CN114593053A

CN114593053A - Screw compressor and air conditioning system

Info

Publication number: CN114593053A
Application number: CN202210299535.8A
Authority: CN
Inventors: 董明珠; 谭建明; 刘华; 张治平; 武晓昆
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2020-12-02
Filing date: 2020-12-02
Publication date: 2022-06-07
Also published as: WO2022116566A1; CN114320910B; CN114320910A

Abstract

The invention relates to a screw compressor and an air conditioning system. The screw compressor comprises a shell (3) and a rotor assembly, wherein the rotor assembly is rotatably arranged in the shell (3) to compress a refrigerant in a cavity between the shell (3) and the rotor assembly.

Description

Screw compressor and air conditioning system

Technical Field

The invention relates to the field of compressors, in particular to a screw compressor and an air conditioning system.

Background

Fig. 1 shows a schematic view of a related art screw compressor; fig. 2 shows a schematic view of a structure of another related art screw compressor. As shown in connection with fig. 1 and 2, a screw compressor includes a housing and a rotor assembly disposed within the housing. The rotor assembly comprises a male rotor 3 disposed within the housing and a female rotor 2 meshing with the male rotor 3, the male rotor 3 comprising a male rotor shaft and first and second

male rotor bodies

3a, 3b arranged side by side along the male rotor shaft, the helical directions of the first and second

male rotor bodies

3a, 3b being opposite. The female rotor 2 comprises a female rotor shaft and a first female rotor body 2a and a second female rotor body 2b arranged side by side along the female rotor shaft, the helical directions of the first female rotor body 2a and the second female rotor body 2b being opposite. The first female rotor body 2a meshes with the first male rotor body 3a, and the second female rotor body 2b meshes with the second male rotor body 3 b.

The air inlet of the screw compressor is positioned at the joint of the first male rotor body and the second male rotor body in the axial direction of the screw compressor, a refrigerant to be compressed, which is introduced by the air inlet, flows towards the two axial ends of the screw compressor, and the compressor further comprises two air outlets which are respectively positioned at the two axial ends of the screw compressor. The exhaust port is used for discharging the refrigerant compressed by the male rotor and the female rotor. The first male and female rotor bodies form a first compression section and the second male and female rotor bodies form a second compression section.

The screw compressor also comprises two bearing parts 1, and the two bearing parts 1 are respectively positioned at two ends of the rotor assembly. The screw compressor further comprises two radial bearings 4 mounted on the two carrier parts 1, respectively. The radial bearing 4 is sleeved on the male rotor shaft. The screw compressor further comprises a first thrust bearing 5a and a second thrust bearing 5b mounted on the two bearing parts 1, respectively. The first thrust bearing 5a and the second thrust bearing 5b are for receiving thrust forces in opposite directions.

Fig. 2 shows a schematic view of the structure of another related art screw compressor, which is different from the screw compressor shown in fig. 1 in that a first thrust bearing 5a and a second thrust bearing 5b are mounted on the same carrier member 1.

In the related art, the first male rotor body and the second male rotor body are symmetrically arranged relative to the center of the rotor assembly, and the first female rotor body and the second female rotor body are symmetrically arranged relative to the center of the rotor assembly, so that the axial gas forces of the first compression part and the second compression part on the rotor assembly are equal in value and opposite in direction, and the purpose of balancing the axial force is achieved.

However, in the actual implementation process, due to the influence of manufacturing deviation, the first and second compression parts inevitably have certain deviation to respective axial gas force, so that the resultant force of the axial forces of the first and second compression parts cannot be completely cancelled, that is, a resultant force with random axial direction and random numerical value occurs in the whole rotor assembly, so that the whole shaft system is randomly pushed to one of the two exhaust end surfaces, and the exhaust end surface of the side rotor is in contact with and rubs against the end surface of the housing, thereby causing a fault. Therefore, the thrust bearing is still inevitably required to bear the limit, and due to the randomness of the resultant force direction, the thrust bearing is required to meet the requirement that the two directions can bear the limit, so that the size and the cost of the compressor assembly are increased finally, the mechanical efficiency of shafting operation is reduced to a certain extent, and the requirement of lubricating oil quantity is increased.

Disclosure of Invention

The invention aims to provide a screw compressor and an air conditioning system.

According to an aspect of an embodiment of the present invention, there is provided a screw compressor including:

a housing; and

the rotor assembly is rotatably arranged in the shell to compress the refrigerant in the cavity between the shell and the rotor assembly.

In some embodiments, the rotor assembly is configured such that the sum of forces is invariant in the direction of the components in the axial direction of the rotor assembly.

In some embodiments, the rotor assembly comprises:

a male rotor including a male rotor shaft and a male rotor body disposed on the male rotor shaft; and

and the female rotor comprises a female rotor shaft parallel to the male rotor shaft and a female rotor body arranged on the female rotor shaft, and the female rotor body is meshed with the male rotor body.

In some embodiments of the present invention, the,

the male rotor body comprises a first male rotor body and a second male rotor body which are arranged side by side along the axial direction of the male rotor shaft, and the spiral directions of the first male rotor body and the second male rotor body are opposite;

the female rotor body comprises a first female rotor body and a second female rotor body which are arranged side by side along the axial direction of the female rotor shaft,

the first female rotor body is meshed with the first male rotor body to form a first compression part, the second female rotor body is meshed with the second male rotor body to form a second compression part, and the first compression part is configured in such a way that the difference between the suction pressure and the exhaust pressure of the first compression part is different from the difference between the suction pressure and the exhaust pressure of the second compression part, so that the direction of the force component of the rotor assembly in the axial direction is unchanged.

In some embodiments of the present invention, the,

the first compression part comprises a first air inlet arranged on the shell and a first air outlet arranged on the shell; and

the second compression part comprises a second air inlet arranged on the shell and a second air outlet arranged on the shell.

In some embodiments of the present invention, the,

the distance between the first intake port and the first exhaust port in the axial direction is different from the distance between the second intake port and the second exhaust port in the axial direction.

In some embodiments, the first exhaust port extends a different length in the axial direction of the rotor assembly than the second exhaust port extends in the axial direction of the rotor assembly.

In some embodiments, the first compression section further comprises a first air supplement port provided on the housing; the second compression part also comprises a second air supplement port arranged on the shell,

the distance between the first air supplementing port and the first air inlet in the axial direction of the rotor assembly is different from the distance between the second air supplementing port and the second air inlet in the axial direction of the rotor assembly; and/or

The flow area of the first air supplement port is different from the flow area of the second air supplement port.

In some embodiments of the present invention, the,

the first air inlet is positioned at one end of the first compression part adjacent to the second compression part, and the first air outlet is positioned at one end of the first compression part far away from the second compression part; or

The first air inlet is located at one end of the first compression part far away from the second compression part, and the first air outlet is located at one end of the first compression part near the second compression part.

In some embodiments, the screw compressor further comprises a motor coupled to the rotor assembly, the motor comprising:

a stator; and

and the rotor is rotatably arranged in the inner cavity of the stator and is connected with the male rotor shaft or the female rotor shaft, and the stator and the rotor are arranged in a staggered mode along the axial direction of the motor so that the rotor is subjected to electromagnetic force along the axial direction of the motor.

In some embodiments, the axial direction of the rotor assembly is horizontal.

In some embodiments, the axial direction of the rotor assembly is vertical.

In some embodiments, the first female rotor body and the second female rotor body have a gap therebetween.

In some embodiments, the bearing member comprises a first bearing member provided at one end of the female rotor, the first and second female rotor bodies each having a gap with the first bearing member.

In some embodiments of the present invention, the,

a sliding bearing is sleeved between the first female rotor body and the female rotor shaft; and (c) and (d).

A sliding bearing is sleeved between the second female rotor body and the female rotor shaft.

In some embodiments of the present invention, the,

a bearing between the first female rotor body and the female rotor shaft protruding out of the first female rotor body in an axial direction of the female rotor shaft;

a bearing between the second female rotor body and the female rotor shaft protrudes out of the second female rotor body in the axial direction of the female rotor shaft.

In some embodiments, the female rotor body is rotatably disposed about the female rotor shaft.

In some embodiments of the present invention, the,

the female rotor body is in sliding fit with the female rotor shaft; or

A rolling bearing is sleeved between the female rotor body and the female rotor shaft; or

A sliding bearing is sleeved between the female rotor body and the female rotor shaft.

In some embodiments, the screw compressor further comprises a lubricating oil flow path comprising:

a first port extending in an axial direction of the female rotor shaft; and

and a second hole passage extending from the first hole passage to an outer peripheral surface of the female rotor shaft in a radial direction of the female rotor shaft.

In some embodiments, a sliding bearing is sleeved between the female rotor body and the female rotor shaft, and the lubricating oil flow path further includes a third hole provided in the sliding bearing, and the third hole communicates with the second hole.

In some embodiments, an annular groove communicating with the third bore is provided on the outer peripheral surface of the sliding bearing.

In some embodiments, the female rotor shaft is provided with a recess on its outer circumferential surface, and the outlet end of the second bore is located at the bottom of the recess.

In some embodiments, the female rotor body is provided on an inner peripheral surface thereof with a groove extending in a circumferential direction of the female rotor shaft, the groove communicating with the second port.

In some embodiments, an end of the housing adjacent to an outlet end of the first port passage is provided with a first oil inlet hole, the first oil inlet hole is communicated with the refrigerant chamber between the male rotor body and the female rotor body, and the outlet end of the first port passage is communicated with the first oil inlet hole.

In some embodiments, the screw compressor further comprises a first bearing portion located at the outlet end of the first duct, the first bearing portion being provided with a first bearing cavity for mounting a bearing for bearing the male rotor shaft, the outlet end of the first duct being in communication with the first bearing cavity.

In some embodiments, the first bearing chamber is located downstream of the outlet end of the first port passage and upstream of the first oil inlet hole in the flow direction of the lubricating oil.

In some embodiments, an end of the housing adjacent to the inlet end of the first bore is provided with a second oil inlet port communicating with the refrigerant chamber between the male and female rotor bodies, and an inlet of the lubricant oil flow path communicates with both the second oil inlet port and the inlet end of the first bore.

In some embodiments, the screw compressor further comprises a second bearing portion at the inlet end of the first port, the second bearing portion having a second bearing cavity disposed thereon for mounting a bearing for bearing the male rotor shaft, the second bearing cavity communicating with the inlet of the lubricating oil flow path.

In some embodiments, the second bearing chamber is located downstream of the inlet of the lubricant flow path and upstream of the second oil inlet hole in the flow direction of the lubricant.

In some embodiments, an oil reservoir communicating with the first port and a flow passage communicating the oil reservoir and the tooth grooves of the female rotor are provided on the end surface of the female rotor body.

In some embodiments, the oil reservoir and the flow passage are provided on an end face of the suction end of the female rotor body.

In some embodiments, the female rotor body comprises a first female rotor body and a second female rotor body arranged side by side in an axial direction of the female rotor shaft, an end of the first female rotor body adjacent to the second female rotor body being a suction end.

In some embodiments, the male rotor shaft comprises a connection section for connecting a rotor of an electrical machine, the connection section being provided with a rotation stop plane, the rotation stop plane being parallel to the axis of the male rotor shaft.

In some embodiments, the connecting section is further provided with a limit step surface for limiting the axial movement of the motor rotor relative to the male rotor shaft along the male rotor shaft, the limit step surface intersecting the rotation stop plane.

In some embodiments, the limiting step surfaces are arranged in one-to-one correspondence with the rotation stop planes.

In some embodiments, the limit step face is perpendicular to the axis of the male rotor shaft.

In some embodiments, the rotation stop plane is plural, and the plural rotation stop planes are arranged side by side in a circumferential direction of the male rotor shaft.

In some embodiments, the rotor assembly includes a male rotor and a female rotor engaged with the male rotor, the male rotor including a male rotor shaft and a male rotor body nested about the male rotor shaft, the male rotor body including first teeth extending helically about the male rotor shaft,

wherein, (the diameter D1 of the tooth root of the male rotor-the diameter dc1 of the tooth core of the male rotor)/the center distance A is 18 percent to 50.6 percent, (the diameter D1 of the tooth top of the male rotor-the diameter dt1 of the pitch circle of the male rotor)/the center distance A is 36.4 percent to 50.6 percent,

the male rotor root diameter d1 is the distance of the root of the first tooth of the male rotor from the axis of the male rotor;

the male rotor tooth core diameter dc1 is the diameter of the shaft bore of the male rotor body;

the male rotor addendum diameter D1 is the distance between the tip of the first tooth and the axis of the male rotor;

male rotor pitch diameter dt1 is the distance from the male rotor's contact point with the female rotor to the axis of the male rotor;

the center-to-center distance a is the distance between the axes of the female and male rotors.

In some embodiments, the male rotor body has a length of L1, where L1/D1 is 1.0-1.9.

In some embodiments, the twist angle of the male rotor is 250 deg. -320 deg.

In some embodiments, the female rotor comprises a female rotor shaft and a female rotor body sleeved on the female rotor shaft, the female rotor body comprises a plurality of second teeth spirally extending in the axial direction of the female rotor shaft, the plurality of second teeth are parallel to each other, two adjacent second teeth form a tooth socket matched with the male rotor,

wherein, (the root diameter d 2-the central hole diameter dc2) of the female rotor/the center distance A is 17.4-46%. The center distance A is-3.6% -6.8%,

the female rotor root diameter d1 is the distance of the root of the second tooth from the axis of the female rotor;

the female rotor center bore diameter dc2 is the diameter of the shaft bore of the female rotor shaft;

the female rotor addendum diameter D2 is the distance between the tip of the second tooth and the axis of the female rotor; and

the female rotor pitch diameter dt2 is the distance from the male rotor and female rotor contact point to the axis of the female rotor 8.

In some embodiments, the female rotor body has a length of L2, where L2/D2 is 0.8-1.2.

In some embodiments of the present invention, the,

the male rotor body comprises a first male rotor body and a second male rotor body which are arranged side by side along a male rotor shaft, and the spiral directions of the first male rotor body and the second male rotor body are opposite; and

the female rotor body comprises a first female rotor body and a second female rotor body arranged side by side along the female rotor shaft, the first female rotor body meshing with the first male rotor body, the second male rotor body meshing with the second female rotor body.

In some embodiments, the bearing member comprises a first bearing member provided at one end of the female rotor, a side of the first bearing member adjacent the female rotor being provided with an impact protection member.

In some embodiments, the impact resistant member is copper.

According to another aspect of the invention, an air conditioning system is also provided, which comprises the screw compressor.

By applying the technical scheme of the invention, the screw compressor comprises a shell and a rotor component, wherein the rotor component is rotatably arranged in the shell so as to compress a refrigerant in a cavity between the shell and the rotor component.

Other features of the present invention and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.

Drawings

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

Fig. 1 shows a schematic view of a related art screw compressor;

fig. 2 is a schematic view showing a structure of another related art screw compressor;

fig. 3 shows a schematic structural view of a screw compressor of a first embodiment of the present invention;

fig. 4 shows an operational principle diagram of a screw compressor of a first embodiment of the present invention;

fig. 5 is a schematic structural view showing a rotor assembly of a screw compressor according to a first embodiment of the present invention;

fig. 6 shows a schematic structural view of a male rotor of a screw compressor of a first embodiment of the present invention;

fig. 7 shows a schematic view in longitudinal section of the male rotor of a screw compressor of a first embodiment of the invention;

fig. 8 is a schematic structural view showing a female rotor of a screw compressor according to a first embodiment of the present invention;

fig. 9 shows a schematic view in longitudinal section of the female rotor of the screw compressor of the first embodiment of the invention;

fig. 10 shows a partially enlarged view of a screw compressor of the first embodiment of the present invention;

FIG. 11 shows a partial enlarged view at A in FIG. 10;

FIG. 12 shows a partial enlarged view at B in FIG. 10;

fig. 13 is a schematic structural view showing a bearing shell of a screw compressor according to a first embodiment of the present invention;

fig. 14 is a schematic perspective view showing a female rotor shaft of a screw compressor according to a first embodiment of the present invention;

fig. 15 shows a schematic structural view of a male rotor and a motor of a screw compressor of a first embodiment of the present invention;

fig. 16 shows a schematic structural view of the male rotor of the screw compressor of the first embodiment of the present invention;

fig. 17 shows a schematic structural view of another alternative male rotor of the screw compressor of the first embodiment of the present invention;

fig. 18 is a schematic perspective view showing the male and female rotors of the screw compressor of the first embodiment of the present invention;

fig. 19 is a schematic structural view showing cross sections of a male rotor and a female rotor of the screw compressor of the first embodiment of the present invention;

fig. 20 shows a schematic view of profiles of the male and female rotors of the screw compressor of the first embodiment of the present invention;

fig. 21 is a schematic structural view showing a screw compressor according to a second embodiment of the present invention;

fig. 22 is a schematic structural view showing a female rotor of a screw compressor according to a second embodiment of the present invention;

fig. 23 is a schematic structural view showing a bearing shell of a female rotor of a screw compressor according to a second embodiment of the present invention;

fig. 24 is a schematic structural view showing a female rotor shaft of a screw compressor according to a second embodiment of the present invention;

fig. 25 is a schematic structural view showing an end face of a screw compressor of a second embodiment of the present invention;

fig. 26 is a schematic structural view showing a cross section of a female rotor of a screw compressor according to a second embodiment of the present invention.

Fig. 27 is a schematic structural view showing a screw compressor according to a third embodiment of the present invention;

fig. 28 is a schematic structural view showing a cross section of a male rotor and a female rotor of a screw compressor of a third embodiment of the present invention;

fig. 29 is a schematic structural view showing a screw compressor according to a fourth embodiment of the present invention;

fig. 30 is a schematic structural view showing a screw compressor according to a fifth embodiment of the present invention;

fig. 31 is a schematic structural view showing a screw compressor according to a sixth embodiment of the present invention; and

fig. 32 is a schematic structural view showing a female rotor of a screw compressor according to a seventh embodiment of the present invention;

fig. 33 shows a schematic structural view of a female rotor of a screw compressor of an eighth embodiment of the present invention; and

fig. 34 shows a schematic configuration diagram of a screw compressor according to a ninth embodiment of the present invention.

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 of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

Example one

Fig. 3 is a schematic structural view of the screw compressor of the present embodiment, and fig. 4 is an operational diagram of the screw compressor of the present embodiment. Fig. 5 is a schematic view showing the structure of the rotor assembly of the screw compressor of the present embodiment.

Referring to fig. 3 to 5, the screw compressor of the present embodiment includes a housing 3 and a rotor assembly, and the rotor assembly is rotatably disposed in the housing 3 to compress a refrigerant in a cavity between the housing 3 and the rotor assembly.

In the present embodiment, the rotor assembly is configured such that the direction of the total force applied to the rotor assembly in the axial direction of the rotor assembly is unchanged, so that the screw compressor of the present embodiment may only be provided with the thrust bearing 1 that bears the axial force in one direction, which improves the problem in the related art that two thrust bearings that can bear two axial forces in opposite directions need to be provided because the direction of the axial force applied to the rotor of the compressor is uncertain.

The rotor assembly comprises a male rotor 4 and a female rotor 8. The male rotor 4 includes a male rotor shaft 4c and a male rotor body provided on the male rotor shaft. In some embodiments, the male rotor body comprises a first male rotor body 4a and a second male rotor body 4b arranged side by side in the axial direction of the male rotor shaft 4c, the helical direction of the first male rotor body 4a and the second male rotor body 4b being opposite.

The female rotor 8 includes a female rotor shaft 8c parallel to the male rotor shaft 4c and a female rotor body provided on the female rotor shaft 8 c. The female rotor body comprises a first female rotor body 8a and a second female rotor body 8b arranged side by side in the axial direction of the female rotor shaft 8 c. The first female rotor body 8a and the second female rotor body 8b are helically oppositely directed.

The screw compressor comprises two bearing parts respectively positioned at two ends of the rotor assembly, and the bearing parts comprise a first bearing part 6 arranged at one end of the shell 3 along the axial direction of the rotor assembly. The screw compressor also comprises two radial bearings 2 fitted on the male rotor shaft 4 c. Two radial bearings 2 are mounted on the two first carrier parts 6, respectively.

The screw compressor 6 further comprises a thrust bearing 1 which is fitted over the male rotor shaft 4c, the thrust bearing 1 being mounted on a first bearing member 6.

The first male rotor body 4a and the second male rotor body 4b are arranged symmetrically with respect to the centre line of the rotor assembly. The first female rotor body 8a and the second female rotor body 4b are arranged symmetrically with respect to the centre line of the rotor assembly.

In some embodiments, the first male rotor body 4a and the second male rotor body 4b are in abutment, the interface of the first male rotor body 4a and the second male rotor body 4b is perpendicular to the axial direction of the rotor assembly, the first male rotor body 4a and the second male rotor body 4b are symmetrically arranged on both sides of the interface.

The first female rotor body 8a and the second female rotor body 4b are in abutment, the first female rotor body 8a and the second female rotor body 4b being symmetrically arranged on either side of the aforementioned interface.

In the present embodiment, the first female rotor body 8a meshes with the first male rotor body 4a to form a first compression portion, and the second female rotor body 4b meshes with the second male rotor body 4b to form a second compression portion.

The first compression portion includes a first intake port provided on the casing 3 and a first exhaust port 10a provided on the casing 3; the second compression portion includes a second intake port provided on the housing 3 and a second exhaust port 10b provided on the housing 3.

In the present embodiment, the first intake port is located at an end of the first compression part adjacent to the second compression part, and the first exhaust port 10a is located at an end of the first compression part remote from the second compression part; the second intake port is located at an end of the second compression part adjacent to the first compression part, and the second exhaust port 10b is located at an end of the second compression part remote from the first compression part.

In some embodiments, the first inlet port and the second inlet port are connected to form an integral inlet port, the inlet port is located at the middle of the rotor assembly in the axial direction, and the first exhaust port 10a and the second exhaust port 10b are located at the two ends of the rotor assembly in the axial direction. As shown in fig. 4, the air inlet is disposed at the intersection of the first compression part and the second compression part, the refrigerant enters the interior of the screw compressor from the air inlet and is divided into two parts, and the two parts of the refrigerant respectively flow to the two ends of the rotor assembly.

As shown in fig. 5, the first exhaust port 10a extends in the axial direction by a length L1, the second exhaust port 10b extends in the axial direction by a length L2, and L1 is greater than L2.

The coolant in the tooth space of the female rotor is compressed in the rotating process of the male rotor 4, and when the female rotor 8 rotates to the state that the tooth space is communicated with the exhaust port, the coolant is compressed. Therefore, the larger the size of the discharge port in the axial direction of the rotor assembly, the smaller the distance between the discharge port and the intake port, and the smaller the difference between the suction pressure and the discharge pressure of the corresponding compression portion.

In this embodiment, the axial distance between the first air inlet and the first air outlet 10a is different from the axial distance between the second air inlet and the second air outlet 10b, and the difference between the air suction pressure and the air discharge pressure of the first compression part is different from the difference between the air suction pressure and the air discharge pressure of the second compression part, so that the axial force applied to the rotor assembly by the first compression part is different from the axial force applied to the rotor assembly by the second compression part, the resultant force direction of the axial force applied to the rotor assembly by the first compression part and the resultant force applied to the rotor assembly by the second compression part is fixed, and the direction of the axial force applied to the rotor assembly when the axial force applied to the rotor assembly fluctuates due to machining errors, uneven air suction pressure and the like in the compression parts is ensured to be unchanged.

In other embodiments, the first intake port is located at an end of the first compression section distal from the second compression section, and the first exhaust port is located at an end of the first compression section proximal to the second compression section; the second air inlet is positioned at one end of the second compression part far away from the first compression part, and the second air outlet is positioned at one end of the second compression part near the first compression part.

In some embodiments, the first exhaust port and the second exhaust port are connected to form an integral exhaust port, the exhaust port is located at the middle of the rotor assembly in the axial direction, and the first intake port and the second intake port are located at the two ends of the rotor assembly in the axial direction.

As shown in fig. 5, the first compression part further includes a first air supplement port 11a provided on the housing; the second compression part further includes a second air supplement port 11b provided in the casing 3.

In some embodiments, the first inlet port 11a is spaced axially from the first inlet port by a distance that is different from the second inlet port 11 a. The first compression part supplements air in advance or lags relative to the second compression part, so that the difference value of the axial force applied to the rotor assembly by the refrigerant in the first compression part and the second compression part can offset the fluctuation of the axial force applied to the rotor assembly by the compression part due to processing error, uneven suction pressure and the like, and the direction of the axial force born by the rotor assembly is unchanged.

In some embodiments, the first air supplement port 11a has a different flow area than the second air supplement port 11b, such that the axial forces applied to the rotor assembly by the cooling medium in the first and second compression sections are different, such that the direction of the axial force experienced by the rotor assembly is unchanged.

In this embodiment, the axial direction of the rotor assembly is horizontal.

Fig. 6 shows a schematic structural view of a male rotor of the screw compressor of the present embodiment, and fig. 7 shows a schematic structural view of a longitudinal section of fig. 6.

As shown in fig. 6 and 7 in combination, the male rotor 4 includes a first male rotor body 4a and a male rotor shaft 4c integral with the first male rotor body 4 a. The male rotor 4 comprises a second male rotor body 4b arranged side by side with the first male rotor body 4a along a male rotor shaft 4 c. The first male rotor body 4a and the second male rotor body 4b have opposite helical directions.

The second male rotor body 4b is provided with a central hole adapted to the male rotor shaft 4c, and the second male rotor body 4b is sleeved on the male rotor shaft 4 c. The second male rotor body 4b is fixed relative to the male rotor shaft 4c to rotate with the male rotor shaft 4 c.

Fig. 8 shows a schematic structural view of the female rotor of the screw compressor of the present embodiment, and fig. 9 shows a schematic longitudinal sectional view of the female rotor of the screw compressor of the present embodiment.

As shown in fig. 8 and 9 in conjunction, the female rotor 8 includes a female rotor shaft 8c and a first female rotor body 8a and a second female rotor body 8b arranged side by side in the axial direction of the female rotor shaft 8 c. The first female rotor body 8a and the second female rotor body 8b are helically counter-directed.

The first female rotor body 8a and the second female rotor body 8b each have a central bore, and the first female rotor body 8a and the second female rotor body 8b each rotatably fit over the female rotor shaft 8 c.

As shown in the combination of fig. 3-4 and 6-9, the screw compressor further comprises a motor 5 for driving the male rotor 4 in rotation. The male rotor shaft 4c is coaxially connected with the rotor of the motor 5.

Fig. 10 shows a partial schematic structural view of the screw compressor, and as shown in fig. 3 and 10, the screw compressor further includes a first bearing member A6a provided at a first axial end of the female rotor 8 and a second bearing member B6B provided at a second axial end of the female rotor 8. The first carrier part A6a and the second carrier part B6B are each provided with a radial bearing 2 for carrying the male rotor shaft 4 c. The second bearing part B6B is further provided with a thrust bearing 1, and the thrust bearing 1 is sleeved on the male rotor shaft 4 c. The first carrier part A6a is located at the end of the female rotor 8 adjacent the electric machine 5.

Both ends of the female rotor shaft 8c are mounted on the first bearing member A6a and the second bearing member B6B, respectively, and the female rotor shaft 8c is fixed with respect to the bearing member 6. The first female rotor body 8a and the second female rotor body 8b are rotatably fitted over the female rotor shaft 8 c.

When the male rotor 4 is driven by the motor 5 to rotate, the first male rotor body 4a drives the first female rotor body 8a meshed with the first male rotor body to rotate, and the second male rotor body 4b drives the second female rotor body 8b meshed with the second male rotor body to rotate.

A bearing is sleeved between the first female rotor body 8a and the female rotor shaft 8 c; a bearing is sleeved between the second female rotor body 8b and the female rotor shaft 8 c.

In some embodiments, the bearing comprises a plain bearing 9. The slide bearing 9 comprises a bearing shell. Figure 13 a schematic view of the construction of a bearing shell.

As shown in connection with fig. 10, the bearing comprises a first slide bearing 9a and a second slide bearing 9b, which are nested between the first female rotor body 8a and the female rotor shaft 8 c. The first slide bearing 9a is located at an end of the first female rotor body 8a adjacent the first bearing member A6a and the second slide bearing 9b is located at an end of the first female rotor body 8a adjacent the second female rotor body 8 b.

The bearing comprises a third slide bearing 9c and a fourth slide bearing 9d, which are nested between the second female rotor body 8b and the female rotor shaft 8 c. The third slide bearing 9c is located at an end of the second female rotor body 8B adjacent to the first female rotor body 8a and the fourth slide bearing 9d is located at an end of the second female rotor body 8B adjacent to the second bearing member B6B.

As shown in fig. 11, the second slide bearing 9b projects from the first female rotor body 8a in the axial direction of the female rotor shaft 8c, and the third slide bearing 9c projects from the second female rotor body 8b in the axial direction of the female rotor shaft 8 c. The second and

third slide bearings

9b, 9c abut so that there is a gap between the first and second

female rotor bodies

8a, 8b, thereby avoiding interference between the first and second

female rotor bodies

8a, 8b during operation of the screw compressor.

As shown in fig. 12, the first slide bearing 9a protrudes from one end of the first female rotor body 8a adjacent to the first bearing member A6a in the axial direction of the female rotor shaft 8c, the first slide bearing 9a abuts against the first bearing member A6a, and a gap exists between the first female rotor body 8a and the first bearing member A6 a.

In some embodiments, the fourth slide bearing 9d protrudes from an end of the second female rotor body 8B adjacent to the second carrier part B6B such that there is a gap between the second female rotor body 8B and the second carrier part B6B.

In some embodiments, an end of the first male rotor body 4a adjacent to the second male rotor body 4b protrudes out of the first female rotor body 8a in the axial direction of the female rotor shaft 8 c. The second male rotor body 4b projects axially beyond the second female rotor body adjacent an end of the first male rotor body 4a, the female rotor shaft 8 c.

The end of the first male rotor body 4a remote from the second male rotor body 4b is flush with the first female rotor body 8a and has a clearance with the carrier 6 to avoid interference with the carrier 6 during rotation of the rotor assembly.

The end of the second male rotor body 4b remote from the first male rotor body 4a is flush with the second female rotor body 8b and has a clearance with the carrier 6 to avoid interference with the carrier 6 during rotation of the rotor assembly.

In this embodiment, the sliding bearing 9 is fixed to the first female rotor body 8a or the second female rotor body 8b, and the sliding bearing 9 generates friction as the first female rotor body 8a or the second female rotor body 8b rotates relative to the female rotor shaft 8 c. Therefore, the sliding bearing 9 is made of a wear-resistant material such as tin bronze or the like.

In order to reduce friction of the sliding bearing 9 or heat generated by the friction, the female rotor shaft 8c is provided with a flow path for feeding a cooling liquid or a lubricating liquid between the sliding bearing 9 and the second rotor 8 c.

As shown in fig. 10 and 14, the flow path includes a first port 14 and a second port 15, the first port 14 extending in the axial direction of the female rotor shaft 8 c; the second port passage 15 extends from the first port passage to the outer peripheral surface of the female rotor shaft 8c in the radial direction of the female rotor shaft 8 c.

Fig. 15 shows a schematic structural view of the male rotor of the screw compressor and the rotor of the motor of the present embodiment. Fig. 16 is a schematic perspective view showing the male rotor of the screw compressor of the present embodiment.

As shown in fig. 15 and 16 in conjunction, the male rotor shaft 4c includes a connecting section for connecting the rotor of the motor 5, the connecting section being provided with a rotation stop plane 4e, the rotation stop plane 4e being parallel to the axis of the male rotor shaft 4 c. The motor rotor 5b is provided with a mounting hole matched with the connecting section. After the connecting section of the male rotor 4 is inserted into the mounting hole of the motor rotor 5b, the male rotor 4 is in rotation stopping fit with the motor rotor 5b, so that the male rotor 4 rotates along with the motor.

As shown in fig. 16, the rotation stop plane 4e of the connecting section is formed by removing a part of the cylindrical shaft, and a limit step surface 4d is formed at the boundary between the connecting section and the cylindrical section at the same time as the rotation stop plane 4e is formed. The limit step surface 4d serves to limit the axial movement of the motor rotor 5b relative to the male rotor shaft 4c along the male rotor shaft 4 c.

The limiting step surfaces 4d and the rotation stopping planes 4e are arranged in a one-to-one correspondence mode, and the limiting step surfaces 4d and the rotation stopping planes 4e are crossed.

In some embodiments, the limit step face 4d is perpendicular to the axis of the male rotor shaft 4 c.

As shown in fig. 16, the rotation stop planes 4e of the coupling segments are two, and the two rotation stop planes 4e are arranged side by side in the circumferential direction of the male rotor shaft 4 c. In the embodiment shown in fig. 16, the two rotation stop planes 4e are spaced 180 degrees apart in the circumferential direction of the male rotor shaft 4 c. The two anti-rotation planes 4e are parallel, thereby forming a flat shaft section.

The connecting section of the male rotor 4 is formed by milling an original cylindrical shaft symmetrically, and the distance from a rotation stopping plane 4e of the connecting section to the axis is 75-85% of the diameter of the shaft. The thickness of the connecting section is too large, the male rotor 4 cannot be driven to rotate when the motor 5 rotates, and the male rotor 4 slides relative to the motor rotor 5b easily; the thickness of the connecting section is too small, the strength and the bending resistance of the flat shaft section are poor, and even the structure is poor compared with the structure provided with the positioning key groove.

In order to position the male rotor shaft 4c of the male rotor 4 and the motor rotor 5b in the related art, key grooves are required to be provided on the male rotor shaft 4c and the motor rotor 5b to position the male rotor shaft 4c and the motor rotor 5b in the circumferential direction. In order to achieve axial positioning of the male rotor shaft 4c and the motor rotor 5b, a positioning shoulder needs to be provided on the male rotor shaft 4 c.

In the embodiment, a part of the rotation stopping plane 4e and the limiting step surface 4d are formed by removing a part of the cylindrical shaft, so that the axial positioning and the axial positioning of the male rotor shaft 4c and the motor rotor 5b are realized.

As shown in fig. 17, in some embodiments, the rotation stop plane 4e is plural, and the plural rotation stop planes 4e are arranged side by side in the circumferential direction of the male rotor shaft 4 c.

As shown in fig. 18, in some embodiments, the male rotor 4 includes a male rotor shaft 4c and a male rotor body 4g, the male rotor body 4g is provided with a shaft hole matching with the male rotor shaft 4c, and the male rotor body 4g is sleeved on the male rotor shaft 4 c. The female rotor 8 includes a female rotor shaft 8c and a female rotor body 8g, and the female rotor body 8g is provided with a shaft hole adapted to the female rotor shaft 8 c. The female rotor body 8g is fitted over the female rotor shaft 8 c.

The male rotor body 4g is keyed to the male rotor shaft 4c, or the male rotor body 4g is interference fit with the male rotor shaft 4 c. The female rotor body 8g and the female rotor shaft 8c are connected by a key, or the female rotor body 8g and the female rotor shaft 8c are interference-fitted.

At least one of the male rotor shaft 4c and the female rotor shaft 8c is made of metal, for example, 45 steel.

At least one of the male rotor body 4g and the female rotor body 8g is made of metal or nonmetal, and the male rotor body 4g and the female rotor body 8g can be made of one of No. 45 steel, polyether ether ketone (PEEK), pearlite type nodular cast iron (QT600-3), stainless steel S30408 and No. 25 steel.

The number of the male rotor bodies 4g provided on the male rotor shaft 4c may be 1, 2, or 3. In some embodiments, the male rotor body 4g includes a first male rotor body 4a and a second male rotor body 4b disposed side-by-side on the male rotor shaft 4 c. The helical direction of the first male rotor body 4a is opposite to the helical direction of the second male rotor body 4 b.

The number of female rotor bodies 8g provided on the female rotor shaft 8c may be 1, 2, or 3. The female rotor bodies 8g provided on the female rotor shaft 8c are arranged in one-to-one correspondence with the male rotor bodies 4g provided on the male rotor shaft 4c, the male rotor bodies 4g meshing with the respective female rotor bodies 8 g.

The male rotor body 4g and the male rotor shaft 4c are of a split structure, and the female rotor body 8g and the female rotor shaft 8c are of a split structure. The male rotor body 4g and the female rotor body 8g are provided with shaft holes matched with the corresponding rotating shafts, and the rigidity of the male rotor body 4g and the rigidity of the female rotor body 8g are influenced by the size of the shaft holes, so that the deformation condition of the rotors in the actual operation of the screw compressor is influenced.

As shown in fig. 19, the male rotor 4 includes first teeth that extend spirally in the circumferential direction of the male rotor shaft 4 c. The female rotor 8 includes second teeth that extend spirally in the circumferential direction of the female rotor shaft 8 c. The female rotor 8 comprises a plurality of parallel second teeth, and tooth grooves matched with the first teeth are formed between the adjacent second teeth. In the present embodiment, the male rotor 4 comprises 5 first teeth arranged in parallel and the female rotor 8 comprises 6 second teeth arranged in parallel.

In this embodiment, the parameters of the male rotor 4 and the female rotor 8 are optimized for the problem that the size of the bore affects the stiffness of the male rotor body 4g and the female rotor body 8 g.

As shown in connection with fig. 19 and 20, the parameters of the male rotor 4 include a male rotor root diameter D1, a male rotor tooth core diameter dc1, a male rotor tooth tip diameter D1, and a male rotor pitch diameter dt 1. The male rotor root diameter d1 is the distance of the root of the first tooth from the axis of the male rotor 4. The male rotor tooth core diameter dc1 is the diameter of the shaft hole of the male rotor body 4 g. The male rotor addendum diameter D1 is the distance of the tip of the first tooth from the axis of the male rotor 4. Male rotor pitch diameter dt1 is the distance from the contact point of male rotor 4 and female rotor 8 to the axis of male rotor 4.

The centre distance a refers to the distance between the axes of the female rotor 8 and the male rotor 4.

Wherein, (the diameter d1 of the tooth root of the male rotor-the diameter of the tooth core of the male rotor-the diameter dc 1)/the center distance A is 18 percent to 50.6 percent. (the diameter of the addendum of the male rotor D1-the diameter of the pitch circle of the male rotor dt 1)/the center distance A is 36.4-50.6%.

The parameters of the female rotor 8 include the female rotor root diameter D2, the female rotor center bore diameter dc2, the female rotor tip diameter D2 and the female rotor pitch diameter dt 2. The female rotor root diameter d1 is the distance of the root of the second tooth from the axis of the female rotor 8. The female rotor center hole diameter dc2 is the diameter of the shaft hole of the female rotor body 8 g. The female rotor addendum diameter D2 is the distance of the tip of the second tooth from the axis of the female rotor 8. Female rotor pitch diameter dt2 is the distance from the contact point of male rotor 4 and female rotor 8 to the axis of female rotor 8.

(root diameter d 2-central hole diameter dc 2)/A is 17.4-46%. (the tooth top diameter D2-the pitch circle diameter dt2 of the female rotor)/the center distance A is-3.6% -6.8%.

The axial length of the single male rotor body 4g is L1 and the diameter of the single male rotor body 4g is D1, where L1/D1 is 1.0-1.9.

The axial length L2 of the single female rotor body 8g, the diameter of the single female rotor body 8g is D2, wherein L2/D2 equals 0.8-1.2, preferably L2/D2 equals 1.

In some embodiments, the twist angle range of the male rotor is 250 deg. and 320 deg. The rotor end face profile is twisted in the circumferential direction from the air suction end to the air discharge end by a twisting angle, i.e. a twisting angle, for example, when one profile is twisted by 360 degrees, the end face profile is completely matched with the profile before twisting.

Example two

Fig. 21 shows a schematic sectional structure view of the screw compressor of the present embodiment, and fig. 22 shows a schematic structural view of a female rotor of the screw compressor of the present embodiment.

Referring to fig. 21 and 22, the screw compressor of the present embodiment is a screw compressor in which the lubricant flow path is refined based on the first embodiment in which the female rotor body is rotatably fitted around the female rotor shaft 8 c. A sliding bearing 9 is sleeved between the female rotor body 8g and the female rotor shaft 8 c.

The lubricating oil flow path includes a first port passage 14 and a second port passage 15, the first port passage 14 extending in the axial direction of the female rotor shaft 8 c; the second bore 15 extends from the first bore to the outer circumferential surface of the female rotor shaft 8c in the radial direction of the female rotor shaft 8c to feed the lubricating oil between the sliding bearing 9 and the rotor body.

Fig. 23 shows a schematic structural view of the sliding bearing 9 of the screw compressor of the present embodiment, and as shown in fig. 21 to 23, the lubricating oil flow path further includes a third orifice 92 provided on the sliding bearing 9, and the third orifice 92 communicates with the second orifice 15. The third orifice 92 extends in the thickness direction of the sliding bearing 9.

An annular groove 91 communicating with the third orifice 92 is provided on the outer peripheral surface of the sliding bearing 9. After the sliding bearing 9 is sleeved in the central hole of the female rotor body, the annular groove can store certain lubricating oil required by the sliding bearing 9 during working.

The inner peripheral surface of the female rotor body is provided with a groove 22 extending in the circumferential direction of the female rotor shaft 8c, and the groove 22 communicates with the second port passage 15. In some embodiments, the groove 22 communicates with the annular groove 91. The grooves 22 may also store the lubrication oil required for the sliding bearing.

Fig. 24 shows a schematic structural view of the female rotor shaft of the screw compressor of the present embodiment, and as shown in fig. 22 and 24, a recessed portion 8f is provided on the outer peripheral surface of the female rotor shaft 8c, and the outlet end of the second duct 15 is located at the bottom of the recessed portion 8 f. After the sliding bearing 9 is sleeved on the female rotor shaft 8c, the recessed portion 8f forms a cavity communicated with the third pore passage 92, which is beneficial to improving the problem that the third pore passage 92 and the second pore passage 15 cannot be aligned and communicated due to assembly errors.

As shown in fig. 21 and 25, a first oil inlet hole 23 is formed at an end of the casing 3 adjacent to an outlet end of the first hole 14, the first oil inlet hole 23 is communicated with a refrigerant chamber between the male rotor body and the female rotor body, and the outlet end of the first hole 14 is communicated with the first oil inlet hole 23.

The screw compressor further comprises a first bearing part 6a located at an outlet end of the first duct 14, a first bearing cavity is arranged on the first bearing part 6a, the first bearing cavity is used for installing a bearing for bearing the male rotor shaft 4c, and the outlet end of the first duct 14 is communicated with the first bearing cavity.

The first bearing chamber is located downstream of the outlet end of the first port passage 14 in the flow direction of the lubricating oil, and upstream of the first oil inlet hole 23.

As shown in fig. 25, a part of the lubricating oil introduced from the inlet end of the first port passage 14 is delivered between the sliding bearing 9 and the female rotor body through the second port passage 15 and the third port passage 92, and the other part is delivered to the first bearing chamber, which communicates with the first oil inlet hole 23, to lubricate the bearing in the first bearing chamber, so that the lubricating oil discharged from the first bearing chamber enters the compression chamber between the female rotor and the male rotor.

A second oil inlet hole 20 is formed at one end of the housing 3 adjacent to the inlet end of the first duct 14, the second oil inlet hole 20 is communicated with a refrigerant chamber between the male rotor body and the female rotor body, and an inlet 17 of the lubricating oil flow path is communicated with the second oil inlet hole 20 and the inlet end of the first duct 14.

The screw compressor further comprises a second bearing portion 6b at the inlet end of the first port 14, the second bearing portion 6b being provided with a second bearing cavity for mounting a bearing for bearing the male rotor shaft 4c, the second bearing cavity being in communication with the inlet 17 of the lubricating oil flow path.

The second bearing chamber is located downstream of the inlet 17 of the lubricant flow path and upstream of the second oil inlet hole 20 in the flow direction of the lubricant.

In this embodiment, a part of the lubricating oil introduced from the inlet 17 of the lubricating oil flow path enters the first port 14 of the female rotor 8, and the other part enters the compression chamber between the female rotor and the male rotor through the second oil inlet hole 20 via the second bearing chamber.

In the present embodiment, the female rotor body includes a first female rotor body 8a and a second female rotor body 8b arranged side by side in the axial direction of the female rotor shaft 8c, and an end of the first female rotor body 8a adjacent to the second female rotor body 8b is a suction end.

The male rotor body comprises a first male rotor body 4a and a second male rotor body 4b arranged side by side in the axial direction of the male rotor shaft 4c, the helical directions of the first male rotor body 4a and the second male rotor body 4b being opposite. The first female rotor body 8a meshes with the first male rotor body 4a to form a first compression portion, and the second female rotor body 8b meshes with the second male rotor body 4b to form a second compression portion.

The air suction end of the first compression part is positioned at one end of the first compression part adjacent to the second compression part, and the end of the first compression part far away from the second compression part is an air discharge end. The air suction end of the second compression part is positioned at one end of the second compression part adjacent to the first compression part, and the end of the second compression part far away from the first compression part is an air discharge end.

The first oil inlet hole 23 is provided at the discharge end of the first compression part, and the second oil inlet hole is provided at the discharge end of the second compression part.

As shown in fig. 26, an oil reservoir 26 communicating with the first port passage 14 and a flow passage 24 communicating the oil reservoir 26 with the tooth grooves 25 of the female rotor 8 are provided on the end surface of the female rotor body.

In some embodiments, the oil reservoir 26 communicates with the gap between the slide bearing 9 and the female rotor body to collect lubricating oil between the slide bearing 9 and the female rotor body. The lubricating oil between the sliding bearing 9 and the female rotor body enters the tooth grooves of the female rotor 8 through the oil reservoir 26 and the flow passage 24.

The oil reservoir 26 and the flow passage 24 are provided on the end face of the suction end of the female rotor body. In some embodiments, the oil reservoir 26 and the flow passage 24 are provided on both the end face of the suction end of the first female rotor body and the end face of the suction end of the second female rotor body.

As shown in fig. 21, the lubricating oil flow path of the present embodiment further includes a first throttle plug 18 provided at the inlet of the lubricating oil flow path and a second throttle plug 19 provided at the outlet end of the first port passage 14.

EXAMPLE III

Fig. 27 shows a schematic structural view of a longitudinal section of the screw compressor of the present embodiment, and fig. 28 shows a schematic structural view of cross sections of the female rotor and the male rotor of the screw compressor of the present embodiment.

As shown in fig. 27 and 28, the present embodiment is different from the second embodiment in that the number of the male rotors and the female rotors in the present embodiment is one.

Example four

Fig. 29 is a schematic structural view of the screw compressor of the present embodiment, and in combination with fig. 29, the screw compressor of the present embodiment differs from the first embodiment in that:

the screw compressor is characterized by further comprising a motor 5 connected with the rotor assembly, wherein the motor 5 comprises a stator 5a and a rotor 5 b. The rotor 5b is rotatably disposed in an inner cavity of the stator 5a and connected to the male rotor shaft 4c or the female rotor shaft 8c, and the stator 5a and the rotor 5b are arranged in a staggered manner in the axial direction of the motor so that the rotor 5b is subjected to electromagnetic force in the axial direction of the motor.

After a closed magnetic return circuit is formed between the stator 5a of the motor and the rotor 5b of the motor, the motor rotor 5b can be pulled by electromagnetic force as a current-carrying conductor, because of axial dislocation L, the pulling direction of the electromagnetic force is not only tangential to the excircle of the rotor 5b, but an electromagnetic force is generated to one side opposite to the axial deviation direction of the rotor, namely, the resultant force of the electromagnetic force applied to the rotor can decompose the electromagnetic force in the axial direction, and for the permanent magnet variable frequency motor, the electromagnetic force can exist between the stator 5a of the motor and the rotor 5b all the time. To pair

In a three-phase asynchronous motor, the electromagnetic force is generated between the stator 5a and the rotor 5b after the motor is powered on; for the male rotor 4, an electromagnetic force in the same direction as the axial component of the gas force occurs, so that the rotor shaft system is ensured to be always subjected to the axial force in a fixed direction, only one set of thrust bearing, namely a positive thrust bearing, is required, and no reverse thrust bearing exists in the whole mechanism; the screw compressor mostly adopts the transverse arrangement of rotors, namely the axes of the male rotor 4 and the female rotor 8 are horizontally arranged, so the required electromagnetic force only needs to be slightly larger than the maximum static friction force of a shafting.

EXAMPLE five

Fig. 30 shows a schematic structural view of the screw compressor of the present embodiment, and as shown in fig. 30, the present embodiment is different from embodiment 1 in that:

the screw compressor also comprises an anti-collision component 12 arranged on the inner side of the bearing component 6, and the material of the anti-collision component 12 is copper.

Considering that the first male rotor body and the second male rotor body are not completely identical in structure and the axial force of the male rotor 4 in the conventional compressor is large, the male rotor still adopts the conventional gas force bearing mode, namely, the cylindrical roller bearing and the angular contact bearing are adopted.

The first female rotor body and the second female rotor body are structurally identical, and a sliding bearing 9 is arranged between the female rotor body and the female rotor shaft to balance radial forces. The axial force generated by a single female rotor is relatively small, and theoretically, no axial bearing structure needs to be added on the premise that the axial forces generated by the two female rotors are mutually offset. However, in the actual use process, the two pairs of female rotors are not tightly attached to each other by axial force in opposite directions before starting up, axial shaking can be generated, the shaking distance is the tooth surface meshing gap between the female rotors and the male rotors, and before stopping, the rotors are reversely rotated to cause axial instability. In order to solve the problem of small gap shaking caused by axial instability, a copper ring is embedded into a bearing seat on the motor side and the non-motor side respectively, the thickness of the copper ring is slightly higher than the depth of a copper ring cavity, the copper ring is slightly higher than the end face by 0.03-0.05 mm (rotor meshing gap), and before starting up a compressor and after stopping the compressor, when a female rotor produces unstable axial shaking, the copper ring can prop the female rotor, so that the rotor is not scratched on the end face of the bearing seat. Because the end surface has an oil film and the copper ring is made of soft material, the copper ring and the end surface of the female rotor cannot be scratched.

EXAMPLE six

Fig. 31 is a schematic structural diagram of the screw compressor of the present embodiment, and as shown in fig. 31, the present embodiment is different from the first embodiment in that: a rolling bearing 13 is provided between the female rotor shaft 8c and the female rotor body. The female rotor body comprises a first female rotor body 8a and a second female rotor body 8b arranged side by side in the axial direction of the female rotor shaft 8 c.

A first rolling bearing is arranged between the first female rotor body 8a and the female rotor shaft 8 c. In some embodiments, the first rolling bearings are two. Optionally, two first rolling bearings are located at the two ends of the first female rotor body 8a, respectively.

A second rolling bearing is provided between the second female rotor body 8b and the female rotor shaft 8 c. In some embodiments, the second rolling bearings are two. Alternatively, two second rolling bearings are provided at both ends of the second female rotor body 8b, respectively.

EXAMPLE seven

Fig. 32 is a schematic structural view showing a female rotor of the screw compressor of the present embodiment, and as shown in fig. 32, the screw compressor of the present embodiment is different from the first embodiment in that: a sliding fit between the female rotor body and the female rotor shaft 8 c. The female rotor body comprises a first female rotor body 8a and a second female rotor body 8b arranged side by side in the axial direction of the female rotor shaft 8 c.

The female rotor shaft 8c is made of hard alloy materials, and the first female rotor body 8a and the second female rotor body are made of self-lubricating non-metallic materials.

The screw compressor further comprises a lubricating oil flow path for conveying lubricating oil between the box female rotor shaft 8c and the female rotor body. The lubricating oil flow path includes a first port 14 and a second port 15 provided in the female rotor shaft 8 c. The first port channel 14 extends in the axial direction of the female rotor shaft 8c and the second port channel 15 extends in the radial direction of the female rotor shaft. A second port 15 extends from the first port 14 to the circumferential surface of the female rotor shaft to deliver lubricating oil between the female rotor shaft 8c and the female rotor body.

Example eight

Fig. 33 shows a schematic configuration diagram of the female rotor of the screw compressor of the present embodiment. As shown in fig. 33, the present embodiment is different from the seventh embodiment in that: the number of female rotor bodies is one.

Example nine

Fig. 34 shows a schematic structural view of the screw compressor of the present embodiment. As shown in fig. 34, the present embodiment is different from the first embodiment in that: the axial direction of the rotor assembly of the screw compressor is a vertical direction, so that the direction of the force component of the rotor assembly in the axial direction is unchanged. The sum of the forces applied to the rotor assembly during operation is directed downwards in the direction of the component in the axial direction, so that the screw compressor of the embodiment can be provided with only one thrust bearing.

The present invention is not limited to the above exemplary embodiments, and any modifications, equivalent replacements, improvements, etc. within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A screw compressor, comprising:

a housing (3);

the rotor assembly is rotatably arranged in the shell (3) so as to compress a refrigerant in a cavity between the shell (3) and the rotor assembly; and

and the two bearing parts are respectively positioned at two ends of the rotor assembly.

2. The screw compressor of claim 1, wherein the rotor assembly is configured such that the force sum is invariant in the direction of the component force in the axial direction of the rotor assembly.

3. -screw compressor according to claim 1 or 2, characterised in that the rotor assembly comprises:

a male rotor (4) comprising a male rotor shaft (4c) and a male rotor body provided on the male rotor shaft (4 c); and

a female rotor (8) comprising a female rotor shaft (8c) parallel to said male rotor shaft (4c) and a female rotor body provided on said female rotor shaft (8c), said female rotor body and said male rotor body being in mesh.

4. -screw compressor according to claim 3,

the male rotor body comprises a first male rotor body (4a) and a second male rotor body (4b) arranged side by side in the axial direction of the male rotor shaft (4c), the helical directions of the first male rotor body (4a) and the second male rotor body (4b) being opposite;

the female rotor body comprises a first female rotor body (8a) and a second female rotor body (8b) arranged side by side in the axial direction of the female rotor shaft (8c),

wherein the first female rotor body (8a) meshes with the first male rotor body (4a) to form a first compression section, and the second female rotor body (8b) meshes with the second male rotor body (4b) to form a second compression section, the first compression section being configured such that the difference in suction and discharge pressures is different from the difference in suction and discharge pressures of the second compression section such that the rotor assembly is subjected to a force sum in the direction of the components of the rotor assembly in the axial direction.

5. Screw compressor according to claim 4,

the first compression part comprises a first air inlet arranged on the shell (3) and a first air outlet (10a) arranged on the shell (3); and

the second compression part comprises a second air inlet arranged on the shell (3) and a second air outlet (10b) arranged on the shell (3).

6. Screw compressor according to claim 5,

the distance in the axial direction between the first intake port and the first exhaust port (10a) is different from the distance in the axial direction between the second intake port and the second exhaust port (10 b).

7. -screw compressor according to claim 5, characterised in that the first exhaust port (10a) extends in the axial direction of the rotor assembly for a different length than the second exhaust port (10b) extends in the axial direction of the rotor assembly.

8. -screw compressor according to claim 5, characterised in that the first compression part also comprises a first supplementary gas port (11a) provided on the casing; the second compression part also comprises a second air supplementing opening (11b) arranged on the shell (3),

the distance between the first air supplementing port (11a) and the first air inlet in the axial direction of the rotor assembly is different from the distance between the second air supplementing port (11a) and the second air inlet in the axial direction of the rotor assembly; and/or

The flow area of the first air supplement port (11a) is different from the flow area of the second air supplement port (11 b).

9. Screw compressor according to claim 5,

the first intake port is located at an end of the first compression section adjacent the second compression section, and the first exhaust port (10a) is located at an end of the first compression section remote from the second compression section; or

The first intake port is located at an end of the first compression section remote from the second compression section, and the first exhaust port (10a) is located at an end of the first compression section adjacent to the second compression section.

10. -screw compressor according to claim 3, characterised in that it further comprises an electric motor (5) connected to the rotor assembly, said electric motor (5) comprising:

a stator (5 a); and

a rotor (5b) rotatably disposed in an inner cavity of the stator (5a) and connected to the male rotor shaft (4c) or the female rotor shaft (8c), the stator (5a) and the rotor (5b) being disposed in a staggered manner in an axial direction of the motor so that the rotor (5b) receives an electromagnetic force in the axial direction of the motor.

11. The screw compressor according to any one of claims 1 to 9, wherein the axial direction of the rotor assembly is horizontal.

12. -screw compressor according to any one of the claims 1 to 9, characterised in that the axial direction of the rotor assembly is vertical.

13. -screw compressor according to claim 4, characterised in that there is a gap between the first female rotor body (8a) and the second female rotor body (4 b).

14. -screw compressor according to claim 4, characterised in that the bearing means comprise a first bearing means (6) provided at one end of the female rotor (8), the first female rotor body (8a) and the second female rotor body (4b) each having a clearance from the first bearing means (6).

15. Screw compressor according to claim 4,

a sliding bearing is sleeved between the first female rotor body (8a) and the female rotor shaft (8 c); and (c) and (d).

A sliding bearing is sleeved between the second female rotor body (8b) and the female rotor shaft (8 c).

16. Screw compressor according to claim 15,

the bearing between the first female rotor body (8a) and the female rotor shaft (8c) protrudes beyond the first female rotor body (8a) in the axial direction of the female rotor shaft (8 c);

the bearing between the second female rotor body (8b) and the female rotor shaft (8c) protrudes beyond the second female rotor body (8b) in the axial direction of the female rotor shaft (8 c).

17. -screw compressor according to claim 3, characterised in that the female rotor body is rotatably fitted on the female rotor shaft (8 c).

18. Screw compressor according to claim 17,

said female rotor body (8g) being in sliding fit with said female rotor shaft (8 c); or

A rolling bearing (13) is sleeved between the female rotor body (8g) and the female rotor shaft (8 c); or

A sliding bearing (9) is sleeved between the female rotor body (8g) and the female rotor shaft (8 c).

19. The screw compressor of claim 17, further comprising a lubrication oil flow path, the lubrication oil path comprising:

a first duct (14) extending in the axial direction of the female rotor shaft (8 c); and

a second hole passage (15) extending from the first hole passage to an outer peripheral surface of the female rotor shaft (8c) in a radial direction of the female rotor shaft (8 c).

20. -screw compressor according to claim 19, characterised in that between the female rotor body (8g) and the female rotor shaft (8c) a slide bearing (9) is nested, and that the lubricating oil flow path further comprises a third port channel (92) provided on the slide bearing (9), which third port channel (92) communicates with the second port channel (15).

21. -screw compressor according to claim 20, characterised in that the slide bearing (9) is provided on its outer circumferential surface with an annular groove (91) which communicates with the third duct (92).

22. -screw compressor according to claim 19, characterised in that the female rotor shaft (8c) is provided on its outer circumference with a recess (8f), the outlet end of the second duct (15) being located at the bottom of the recess (8 f).

23. -screw compressor according to claim 19, characterised in that the female rotor body is provided on its inner circumferential surface with a groove (22) extending in the circumferential direction of the female rotor shaft (8c), which groove (22) communicates with the second duct (15).

24. -screw compressor according to claim 19, characterised in that the end of the casing (3) adjacent to the outlet end of the first duct (14) is provided with a first oil inlet hole (23), which first oil inlet hole (23) communicates with the coolant chamber between the male and female rotor bodies, and that the outlet end of the first duct (14) communicates with the first oil inlet hole (23).

25. -screw compressor according to claim 24, characterised in that it also comprises a first bearing (6a) at the outlet end of the first duct (14), said first bearing (6a) being provided with a first bearing cavity for mounting a bearing carrying the male rotor shaft (4c), the outlet end of the first duct (14) communicating with said first bearing cavity.

26. -screw compressor according to claim 25, characterised in that the first bearing chamber is located downstream of the outlet end of the first duct (14) and upstream of the first oil inlet hole (23) in the direction of flow of the lubricating oil.

27. -screw compressor according to claim 19, characterised in that the end of the casing (3) adjacent to the inlet end of the first duct (14) is provided with a second oil inlet, which communicates with the cooling medium chamber between the male and female rotor bodies, the inlet of the lubricating oil flow path communicating with both the second oil inlet and the inlet end of the first duct (14).

28. -screw compressor according to claim 27, characterised in that it further comprises a second bearing portion (6b) at the inlet end of the first duct (14), said second bearing portion (6b) being provided with a second bearing cavity for mounting a bearing carrying the male rotor shaft (4c), said second bearing cavity communicating with the inlet of the lubricating oil flow path.

29. The screw compressor according to claim 28, wherein the second bearing chamber is located downstream of the inlet of the lubricating oil flow path and upstream of the second oil inlet hole in the flow direction of the lubricating oil.

30. -screw compressor according to claim 19, characterised in that the female rotor body is provided on its end face with an oil reservoir (26) communicating with the first duct (14) and with a flow channel (24) communicating the oil reservoir (26) with the tooth grooves (25) of the female rotor (8).

31. -screw compressor according to claim 30, characterised in that the oil reservoir (26) and the flow channel (24) are provided on the end face of the suction end of the female rotor body.

32. -screw compressor according to claim 3, characterised in that it comprises a first female rotor body (8a) and a second female rotor body (8b) arranged side by side in the axial direction of a female rotor shaft (8c), the end of the first female rotor body (8a) adjacent to the second female rotor body (8b) being the suction end.

33. -screw compressor according to claim 3, characterised in that the male rotor shaft (4c) comprises a connection section for connecting the rotor of the electric motor (5), said connection section being provided with a rotation-stop plane (4e), said rotation-stop plane (4e) being parallel to the axis of the male rotor shaft (4 c).

34. -screw compressor according to claim 33, characterised in that the connecting section is also provided with a limit step surface (4d) for limiting the movement of the motor rotor (5b) relative to the male rotor shaft (4c) in the axial direction of the male rotor shaft (4c), said limit step surface (4d) intersecting the rotation stop plane (4 e).

35. The screw compressor according to claim 34, wherein the limit step faces (4d) are provided in one-to-one correspondence with the rotation stop planes (4 e).

36. -screw compressor according to claim 34, characterised in that the limit step surface (4d) is perpendicular to the axis of the male rotor shaft (4 c).

37. -screw compressor according to claim 33, characterised in that the rotation stop planes (4e) are several, the rotation stop planes (4e) being arranged side by side in the circumferential direction of the male rotor shaft (4 c).

38. -screw compressor according to claim 1, characterised in that the rotor assembly comprises a male rotor (4) and a female rotor (8) meshing with the male rotor (4), the male rotor (4) comprising a male rotor shaft (4c) and a male rotor body (4g) fitted over the male rotor shaft (4c), the male rotor body (4g) comprising first teeth extending helically on the male rotor shaft (4c),

the male rotor root diameter d1 is the distance of the root of the first tooth of the male rotor (4) from the axis of the male rotor (4);

the male rotor tooth core diameter dc1 is the diameter of the shaft hole of the male rotor body (4 g);

the male rotor addendum diameter D1 is the distance between the crest of the first tooth and the axis of the male rotor (4);

male rotor pitch diameter dt1 is the distance from the contact point of the male rotor (4) and the female rotor (4) to the axis of the male rotor (4);

the centre distance A is the distance between the axes of the female rotor (8) and the male rotor (4).

39. -screw compressor according to claim 38, characterised in that the male rotor body (4g) has a length L1, where L1/D1 is 1.0-1.9.

40. The screw compressor as claimed in claim 38, wherein the torsion angle of the male rotor is 250 deg-320 deg.

41. -screw compressor according to any one of the claims 38 to 40, characterised in that the female rotor (8) comprises a female rotor shaft (8c) and a female rotor body (8g) fitted over the female rotor shaft (8c), the female rotor body (8g) comprising a plurality of second teeth extending helically in the axial direction of the female rotor shaft (8c), the plurality of second teeth being parallel to each other, two adjacent second teeth forming a tooth slot adapted to the male rotor (4),

wherein, (the root diameter d 2-the central hole diameter dc2) of the female rotor/the center distance A is 17.4-46%. (the diameter D2 of the tooth top of the female rotor-the pitch circle diameter dt2 of the female rotor)/the center distance A is-3.6-6.8%,

the female rotor root diameter d1 is the distance of the root of the second tooth from the axis of the female rotor (8);

the female rotor center hole diameter dc2 is the diameter of the shaft hole of the female rotor shaft (8 c);

the female rotor addendum diameter D2 is the distance between the tip of the second tooth and the axis of the female rotor (8); and

female rotor pitch diameter dt2 is the distance from the contact point of the male rotor (4) and female rotor (8) to the axis of the female rotor (8).

42. -screw compressor according to claim 41, characterised in that the female rotor body (8g) has a length L2, where L2/D2 is 0.8-1.2.

43. Screw compressor according to claim 38,

the male rotor body (4g) comprises a first male rotor body (4a) and a second male rotor body (4b) arranged side by side along the male rotor shaft (4c), the helical direction of the first male rotor body (4a) being opposite to that of the second male rotor body (4 b); and

the female rotor body (8g) comprises a first female rotor body (8a) and a second female rotor body (8b) arranged side by side along the female rotor shaft (8c), the first female rotor body (8a) meshing with the first male rotor body (4a), the second male rotor body (4b) meshing with the second female rotor body (8 b).

44. -screw compressor according to claim 3, characterised in that the carrier also comprises a first carrier (6) provided at one end of the female rotor (8), the side of the first carrier (6) adjacent to the female rotor (8) being provided with an anti-collision part (12).

45. -screw compressor according to claim 44, characterised in that the impact-protection part (12) is made of copper.

46. An air conditioning system comprising a screw compressor according to any one of claims 1 to 45.