CN116146487A - Double-screw compressor and refrigeration equipment - Google Patents

Abstract

The invention relates to a double-screw compressor and refrigeration equipment, and relates to the technical field of air compression. The double-screw compressor of the invention comprises a shell, a low pressure part and a high pressure part; the low-pressure part comprises a first low-pressure rotor and a second low-pressure rotor, the spiral directions of the spiral teeth of the first low-pressure rotor and the spiral teeth of the second low-pressure rotor are opposite and meshed with each other to form primary compression; the high-pressure part comprises a first high-pressure rotor and a second high-pressure rotor, the spiral directions of the spiral teeth of the first high-pressure rotor and the spiral teeth of the second high-pressure rotor are opposite and meshed with each other to form two-stage compression; the first low-pressure rotor and the first high-pressure rotor are opposite in spiral direction, and the second low-pressure rotor and the second high-pressure rotor are opposite in spiral direction, so that the primary axial force generated by primary compression on the low-pressure part is opposite to the secondary axial force generated by secondary compression on the high-pressure part. The technical scheme disclosed by the application can solve the problems that the existing double-screw compressor vibrates and has large noise and is extremely easy to fail.

Description

Double-screw compressor and refrigeration equipment

Technical Field

The invention relates to the technical field of air compression, in particular to a double-screw compressor and refrigeration equipment.

Background

The refrigerating equipment is equipment for regulating and controlling parameters such as temperature, humidity, flow rate and the like of air in the environment of a building or a structure by manual means. The compressor is the heart of the refrigeration equipment, which is closely related to the service life and the refrigeration effect of the refrigeration equipment, wherein the twin screw compressor is most widely used.

The double-screw compressor has the advantages of simple structure, high reliability, strong adaptability and the like, and comprises a pair of rotors with spiral teeth which are meshed with each other and have opposite rotation directions, and the purposes of air suction, compression and air discharge are achieved through the rotation movement of the rotors.

However, in the process that the air in the double-screw compressor is compressed from low pressure to high pressure, the air pressure in the direction of the air suction port of the compressor points to the air discharge port is from low to high, so that axial force from the air discharge port to the air suction port is formed on the rotor, the double-screw compressor vibrates and has high noise, and faults are easy to occur.

Disclosure of Invention

The embodiment of the application provides a double-screw compressor and refrigeration equipment, can solve current double-screw compressor vibration and noise great, very easily break down the problem.

In a first aspect, embodiments of the present application provide a twin screw compressor comprising:

a housing;

a low pressure part including a first low pressure rotor and a second low pressure rotor rotatably provided in the housing, the first low pressure rotor and the second low pressure rotor having spiral teeth of opposite directions and being engaged with each other to form a primary compression of a working medium; and

a high-pressure part including a first high-pressure rotor and a second high-pressure rotor rotatably provided in the housing, the first high-pressure rotor and the first low-pressure rotor being coaxially provided and turning the same, the second high-pressure rotor and the second low-pressure rotor being coaxially provided and turning the same, the first high-pressure rotor and the second high-pressure rotor being opposite in rotation direction of helical teeth and intermeshed to form a two-stage compression of a working medium;

the first low-pressure rotor and the first high-pressure rotor are opposite in spiral direction, and the second low-pressure rotor and the second high-pressure rotor are opposite in spiral direction, so that primary axial force generated by primary compression on the first low-pressure rotor and the second low-pressure rotor is opposite to secondary axial force generated by secondary compression on the first high-pressure rotor and the second high-pressure rotor.

In one embodiment, the twin screw compressor includes a partition disposed within the housing and separating the housing into a low pressure chamber and a high pressure chamber isolated from each other;

the low-pressure part is positioned in the low-pressure cavity, and the high-pressure part is positioned in the high-pressure cavity.

In one embodiment, the side wall of the partition is provided with a low-pressure notch and a high-pressure notch;

the low-pressure notch extends to the end face of the partition piece, which is close to the low-pressure part, so that the low-pressure notch is communicated with the low-pressure cavity;

the high-pressure notch extends to the end face, close to the high-pressure part, of the partition piece so that the high-pressure notch is communicated with the high-pressure cavity;

wherein, the low pressure notch is not communicated with the high pressure notch.

In one embodiment, the shell is provided with a primary air suction port, a primary air exhaust port, a secondary air suction port and a secondary air exhaust port;

the primary air suction port is positioned at one end of the shell close to the low-pressure part;

the primary exhaust port is positioned on the side wall of the shell and is communicated with the low-pressure notch;

the secondary air suction port is positioned at one end of the shell close to the high-pressure part;

the secondary exhaust port is positioned on the side wall of the shell and is communicated with the high-pressure notch;

wherein, the first-stage exhaust port is communicated with the second-stage air suction port through a pipeline.

In one embodiment, the shell is provided with a primary air suction port, a primary air exhaust port, a secondary air suction port and a secondary air exhaust port;

the primary air suction port is positioned on the side wall of the shell and is communicated with the low-pressure notch;

the first-stage exhaust port is positioned at one end of the shell close to the low-pressure part;

the secondary air suction port is positioned on the side wall of the shell and is communicated with the high-pressure notch;

the secondary exhaust port is positioned at one end of the shell close to the high-pressure part;

wherein, the first-stage exhaust port is communicated with the second-stage air suction port through a pipeline.

In one embodiment, the twin screw compressor comprises:

the first rotating shaft is rotatably arranged in the shell, and the first rotating shaft, the first low-pressure rotor and the first high-pressure rotor are integrally formed; and

the second rotating shaft is rotatably arranged in the shell, the rotating direction of the second rotating shaft is opposite to that of the first rotating shaft, the second rotating shaft is parallel to the first rotating shaft, and the second rotating shaft, the second low-pressure rotor and the second high-pressure rotor are integrally formed;

the first low-pressure rotor and the first high-pressure rotor are arranged at intervals in the axial direction of the first rotating shaft, and the second low-pressure rotor and the second high-pressure rotor are arranged at intervals in the axial direction of the second rotating shaft.

In one embodiment, the partition member is provided with a first through hole and a second through hole, the first through hole is used for the first rotating shaft to pass through, and the second through hole is used for the second rotating shaft to pass through.

In one embodiment, both ends of the first rotating shaft and the second rotating shaft are connected with the shell through radial bearings.

In one embodiment, the first rotating shaft and the second rotating shaft are provided with axial bearings;

the axial bearing is only positioned at one end of the first rotating shaft and the second rotating shaft, which is close to the high-pressure part.

In a second aspect, embodiments of the present application provide a refrigeration apparatus comprising a twin screw compressor as previously described.

Compared with the prior art, the embodiment of the application has the advantages that the first low-pressure rotor and the first high-pressure rotor are opposite in spiral direction through the arrangement of the spiral teeth of the first low-pressure rotor and the second high-pressure rotor, the spiral directions of the spiral teeth of the second low-pressure rotor and the second high-pressure rotor are opposite, the primary axial force generated by the working medium in primary compression is opposite to the secondary axial force generated by the working medium in secondary compression, the primary axial force and the secondary axial force can at least offset each other to reduce axial resultant force, the problems that the existing double-screw compressor vibrates and has larger noise and is extremely easy to fail are solved, in addition, compared with the existing double-screw compressor, a small quantity of large-model or a plurality of small-model axial bearings are required to be arranged to bear the axial force, and the axial force is reduced due to the fact that only a small quantity of small-model axial bearings are required to be arranged, so that the size of a bearing seat of the compressor is more compact, and the production cost is reduced.

Drawings

The invention will be described in more detail hereinafter on the basis of embodiments and with reference to the accompanying drawings.

FIG. 1 is a schematic view of a twin screw compressor according to an embodiment of the present invention;

FIG. 2 is a cross-sectional view of the separator provided in the embodiment of FIG. 1 taken along the direction A-A;

FIG. 3 is a cross-sectional view of the separator provided in the embodiment of FIG. 1 along the direction B-B;

FIG. 4 is a cross-sectional view of the twin screw compressor provided in the embodiment of FIG. 1 without a partition installed;

fig. 5 is a schematic view showing a structure of a twin screw compressor according to another embodiment of the present invention.

Reference numerals:

10. a housing; 110. a low pressure chamber; 120. a high pressure chamber; 130. a first-stage air suction port; 140. a first-stage exhaust port; 150. a secondary air suction port; 160. a secondary exhaust port; 20. a low pressure section; 210. a first low pressure rotor; 220. a second low pressure rotor; 30. a high pressure section; 310. a first high-pressure rotor; 320. a second high-pressure rotor; 40. a partition; 410. a low pressure notch; 420. a high pressure notch; 430. a first through hole; 440. a second through hole; 50. a first rotating shaft; 60. a second rotating shaft; 70. a radial bearing; 80. an axial bearing.

Detailed Description

The invention will be further described with reference to the accompanying drawings.

The double-screw compressor has the advantages of simple structure, high reliability, strong adaptability and the like, and comprises a shell and a pair of rotors positioned in the shell, wherein the pair of rotors are meshed with each other and provided with spiral teeth with opposite rotation directions, the pair of rotors respectively correspond to a male rotor and a female rotor, the male rotor and the female rotor are respectively provided with an air suction end and an air discharge end, the air suction end is communicated with an air suction port of the shell, the air discharge end is communicated with an air discharge port of the shell, and a working medium achieves the purposes of suction, compression and discharge through the rotary motion of the male rotor and the female rotor.

In the process that the air in the double-screw compressor is compressed into high pressure from low pressure, the air pressure in the direction of the air suction port pointing to the air discharge port is low to high, so that axial force pointing to the air suction port from the air discharge port is formed on the male rotor and the female rotor, the double-screw compressor vibrates and has high noise, and faults are easy to occur.

To solve this problem, the existing twin screw compressor may arrange an axial bearing to carry an axial force, and in order to avoid the axial force exceeding the load range of the axial bearing, it is generally necessary to provide a small number of large-sized or multiple small-sized axial bearings to carry the axial force, but this may increase the radial dimension or axial dimension of the bearing housing of the compressor, thereby increasing the production cost.

In order to solve the above-mentioned technical problems, at least one embodiment of the present application provides a twin-screw compressor, which includes a housing 10, a low pressure part 20, and a high pressure part 30; the low pressure part 20 includes a first low pressure rotor 210 and a second low pressure rotor 220 rotatably provided in the housing 10, the first low pressure rotor 210 and the second low pressure rotor 220 having spiral teeth of opposite directions and being engaged with each other to form a primary compression of the working medium. The high pressure part 30 includes a first high pressure rotor 310 and a second high pressure rotor 320 rotatably disposed in the housing 10, the first high pressure rotor 310 and the first low pressure rotor 210 are coaxially disposed and identically turned, the second high pressure rotor 320 and the second low pressure rotor 220 are coaxially disposed and identically turned, the spiral teeth of the first high pressure rotor 310 and the second high pressure rotor 320 are oppositely turned and intermeshed to form a two-stage compression of the working medium; wherein the first low pressure rotor 210 and the first high pressure rotor 310 have opposite spiral directions of spiral teeth, and the second low pressure rotor 220 and the second high pressure rotor 320 have opposite spiral directions of spiral teeth, so that a primary axial force generated by primary compression on the first low pressure rotor 210 and the second low pressure rotor 220 is opposite to a secondary axial force generated by secondary compression on the first high pressure rotor 310 and the second high pressure rotor 320.

As can be seen from the above, by setting the opposite rotation directions of the helical teeth of the first low pressure rotor 210 and the first high pressure rotor 310, the second low pressure rotor 220 and the second high pressure rotor 320 have opposite rotation directions, so that the primary axial force generated by the working medium in the primary compression is opposite to the secondary axial force generated by the working medium in the secondary compression, and the primary axial force and the secondary axial force can at least offset each other to reduce the axial resultant force, thereby solving the problems of the existing twin-screw compressor that the vibration and the noise are large and the failure is easy to occur.

As shown in fig. 1, the twin screw compressor includes a housing 10, a low pressure part 20, and a high pressure part 30. The housing 10 is matched with the outer shapes of the low-pressure portion 20 and the high-pressure portion 30. It should also be noted that the working medium in the twin screw compressor may be a refrigerant.

The low pressure part 20 includes a first low pressure rotor 210 and a second low pressure rotor 220 rotatably provided in the housing 10, the first low pressure rotor 210 and the second low pressure rotor 220 having spiral teeth of opposite directions and being engaged with each other to form a primary compression of the working medium. It should be noted that the first low-pressure rotor 210 may be a low-pressure stage male rotor and the second low-pressure rotor 220 may be a low-pressure stage female rotor, and of course, the first low-pressure rotor 210 may be a low-pressure stage female rotor and the second low-pressure rotor 220 may be a low-pressure stage male rotor, where the male rotor may be understood to be a driving rotor and the female rotor may be understood to be a driven rotor. It should be further noted that, the meshing gap between the first low pressure rotor 210 and the second low pressure rotor 220 may be 0.01mm.

The high pressure part 30 includes a first high pressure rotor 310 and a second high pressure rotor 320 rotatably disposed in the housing 10, the first high pressure rotor 310 being coaxially disposed and identically turned to the first low pressure rotor 210, the second high pressure rotor 320 being coaxially disposed and identically turned to the second low pressure rotor 220, the spiral teeth of the first high pressure rotor 310 and the second high pressure rotor 320 being oppositely turned and intermeshed to form a two-stage compression of the working medium. It should be noted that the first high-pressure rotor 310 may be a high-pressure stage male rotor and the second high-pressure rotor 320 may be a high-pressure stage female rotor, and of course, the first high-pressure rotor 310 may be a high-pressure stage female rotor and the second high-pressure rotor 320 may be a high-pressure stage male rotor, where the male rotor may be understood to be a driving rotor and the female rotor may be understood to be a driven rotor. It should be noted that, the meshing gap between first high-pressure rotor 310 and second high-pressure rotor 320 may be 0.01mm.

Wherein the first low pressure rotor 210 and the first high pressure rotor 310 have opposite spiral directions of spiral teeth, and the second low pressure rotor 220 and the second high pressure rotor 320 have opposite spiral directions of spiral teeth, so that a primary axial force generated by primary compression on the first low pressure rotor 210 and the second low pressure rotor 220 is opposite to a secondary axial force generated by secondary compression on the first high pressure rotor 310 and the second high pressure rotor 320.

It should be noted that, the direction of the axial force generated by the low pressure portion 20 and the high pressure portion 30 is opposite, so that the axial force can be at least partially offset, and the axial force can be completely offset in the optimal state, so that the axial bearings 80 are not required to be arranged on the low pressure rotor and the high pressure rotor, but the axial force can be fluctuated due to the influence of the working condition change and other external factors during the operation of the twin-screw compressor, and a small number of axial bearings 80 can be still arranged to ensure the reliability.

By arranging the first low-pressure rotor 210 and the first high-pressure rotor 310 with opposite spiral directions of the spiral teeth, the second low-pressure rotor 220 and the second high-pressure rotor 320 with opposite spiral directions of the spiral teeth, the direction of the primary axial force generated by primary compression of the working medium is opposite to that of the secondary axial force generated by secondary compression of the working medium, so that the primary axial force and the secondary axial force can at least offset each other to reduce the axial resultant force on the male rotor and the female rotor, and the problems that the existing double-screw compressor vibrates, has high noise and is extremely easy to fail are solved.

For example, as shown in fig. 1, primary axial forces generated by primary compression of the working medium on the first low pressure rotor 210 and the second low pressure rotor 220 are F _{Low 1} 、F _{Low 2} Secondary axial forces generated by secondary compression of working medium on first high-pressure rotor 310 and second high-pressure rotor 320 are F respectively _{High 1} 、F _{High 2} ，F _{Low 1} And F is equal to _{High 1} Is opposite to the direction of (3);

if first low-pressure rotor 210 and first high-pressure rotor 310 are male rotors, an axial resultant force F is generated on the male rotors _{Yang (Yang)} ＝F _{Low 1} —F _{High 1} ；

If the second low pressure rotor 220, the second high pressure rotor 320 is a male rotor, the resultant force F is the axial force on the female rotor _{Yin type vagina} ＝F _{Low 2} —F _{High 2} 。

In some embodiments, the twin screw compressor includes a partition 40 disposed within the casing 10 and separating the casing 10 into a low pressure chamber 110 and a high pressure chamber 120 isolated from each other; wherein the low pressure portion 20 is located in the low pressure chamber 110 and the high pressure portion 30 is located in the high pressure chamber 120. By arranging the low-pressure cavity 110 and the high-pressure cavity 120 to form independent spaces for primary compression and secondary compression of working media, the primary compression and the secondary compression are relatively independent, and a structural basis is provided for realizing opposite axial force directions of the low-pressure part 20 and the high-pressure part 30 in the double-screw compressor.

As shown in fig. 2 and 3, in some embodiments, a low pressure notch 410 and a high pressure notch 420 are provided on the sidewall of the separator 40; the low pressure notch 410 extends to an end face of the partition 40 near the low pressure portion 20 so that the low pressure notch 410 communicates with the low pressure chamber 110; the high-pressure notch 420 extends to the end face of the partition 40 near the high-pressure portion 30 so that the high-pressure notch 420 communicates with the high-pressure chamber 120; wherein the low pressure notch 410 is not in communication with the high pressure notch 420. The high pressure gap 420 and the low pressure gap 410 are symmetrical with respect to the partition plate in the axial direction of the partition plate, and of course, the high pressure gap 420 and the low pressure gap 410 may be designed according to the pressure ratio distribution of the twin screw compressor between the low pressure portion 20 and the high pressure portion 30.

As shown in fig. 1 and 4, in some embodiments, the housing 10 is provided with a primary air intake 130, a primary air exhaust 140, a secondary air intake 150, and a secondary air exhaust 160; the primary suction port 130 is located at one end of the casing 10 near the low pressure portion 20; the primary exhaust port 140 is located on the side wall of the housing 10, and the primary exhaust port 140 is communicated with the low-pressure notch 410; the secondary air suction port 150 is located at one end of the casing 10 near the high pressure portion 30; the secondary exhaust port 160 is located on the side wall of the casing 10, and the secondary exhaust port 160 is communicated with the high-pressure notch 420; wherein the primary exhaust port 140 is in communication with the secondary intake port 150 via a conduit. The conduit may be a flow passage provided in the housing 10 and isolated from the low pressure chamber 110 and the high pressure chamber 120, or may be an external conduit provided outside the housing 10.

By arranging the first-stage air suction port 130 and the first-stage air discharge port 140 which are communicated with the low-pressure cavity 110 and arranging the second-stage air suction port 150 and the second-stage air discharge port 160 which are communicated with the high-pressure cavity 120 on the shell, the compression work of the low-pressure part 20 and the high-pressure part 30 is respectively matched, and the flowing direction of working medium in the low-pressure cavity 110 is opposite to the flowing direction of working medium in the high-pressure cavity 120, so that axial force with opposite directions is formed in the low-pressure part 20 and the high-pressure part 30; the low-pressure notch 410 and the high-pressure notch 420 on the partition piece 40 are respectively communicated with the first-stage exhaust port 140 and the second-stage exhaust port 160 to form exhaust channels of the low-pressure cavity 110 and the high-pressure cavity 120, so that the structure is simple, the processing is convenient, the replacement is convenient and the cost is low.

For example, as shown in fig. 1, the working medium enters the low pressure chamber 110 from the first stage suction port 130, is discharged from the first stage discharge port 140 after being compressed by the low pressure portion 20 by one stage, generates an axial force directed to the first low pressure rotor 210 by the partition 40 on the first low pressure rotor 210, and generates an axial force directed to the second low pressure rotor 220 by the partition 40 on the second low pressure rotor 220; the working medium after primary compression enters the high-pressure chamber 120 through the secondary air suction port 150 and is discharged from the secondary air discharge port 160 after secondary compression by the high-pressure part 30, the axial force directed to the first high-pressure rotor 310 by the partition 40 is formed on the first high-pressure rotor 310, and the axial force directed to the second high-pressure rotor 320 by the partition 40 is formed on the second high-pressure rotor 320, so that the axial force generated by the rotor of the low-pressure part 20 is opposite to the axial force generated by the high-pressure part 30 in direction, and at least part of the axial forces can be mutually offset.

As shown in fig. 4, in some embodiments, the twin screw compressor includes a first shaft 50 and a second shaft 60; the first rotating shaft 50 is rotatably disposed in the housing 10, and the first rotating shaft 50, the first low-pressure rotor 210 and the first high-pressure rotor 310 are integrally formed. It should be noted that the first shaft 50, the first low-pressure rotor 210, and the first high-pressure rotor 310 may be machined on the same optical axis by machining such as grinding to realize integral molding.

The second rotating shaft 60 is rotatably disposed in the housing 10, the rotating direction of the second rotating shaft 60 is opposite to the rotating direction of the first rotating shaft 50, and the second rotating shaft 60 is parallel to the first rotating shaft 50, and the second rotating shaft 60, the second low-pressure rotor 220 and the second high-pressure rotor 320 are integrally formed. It should be noted that the second rotating shaft 60, the second low-pressure rotor 220, and the second high-pressure rotor 320 may be machined on the same optical axis by a machining method such as grinding to realize integral molding.

Wherein the first low pressure rotor 210 and the first high pressure rotor 310 are spaced apart in the axial direction of the first rotating shaft 50, and the second low pressure rotor 220 and the second high pressure rotor 320 are spaced apart in the axial direction of the second rotating shaft 60.

It should be noted that, the first shaft 50 may be used as a driving shaft and connected to a driving motor, and the second shaft 60 may be used as a driven shaft to rotate, where the rotor on the first shaft 50 is a male rotor and the rotor on the second shaft 60 is a female rotor; of course, the second rotating shaft 60 may be connected to the driving motor as a driving shaft, and the first rotating shaft 50 may be rotated as a driven shaft, and in this case, the rotor on the first rotating shaft 50 may be a female rotor, and the rotor on the second rotating shaft 60 may be a male rotor.

The first low-pressure rotor 210, the first high-pressure rotor 310 and the first rotating shaft 50 are integrally formed, the second low-pressure rotor 220, the second high-pressure rotor 320 and the second rotating shaft 60 are integrally formed, coaxiality is ensured, and deviation of meshing gaps of the rotors caused by eccentricity is avoided. Compared with the existing rotor formed by assembling an optical axis and a screw sleeve through radial positioning and fastening nuts, the rotor is not easy to eccentric, and the meshing gap of the rotor can reach required precision.

As shown in fig. 2 and 3, in some embodiments, the partition 40 has a first through hole 430 and a second through hole 440, the first through hole 430 is used for the first shaft 50 to pass through, and the second through hole 440 is used for the second shaft 60 to pass through. It should be noted that, when the first through hole 430 is sealed with the first rotating shaft 50, the first rotating shaft 50 needs to be guaranteed to rotate normally, and when the second through hole 440 is sealed with the second rotating shaft 60, the second rotating shaft 60 needs to be guaranteed to rotate normally.

In some embodiments, both ends of the first and second shafts 50, 60 are connected to the housing 10 through radial bearings 70. It should be noted that, a bearing seat is disposed on the housing 10, and the radial bearing 70 is connected to the corresponding bearing seat. It should be noted that the radial bearing 70 may be a cylindrical roller bearing.

In some embodiments, the first shaft 50 and the second shaft 60 are each provided with an axial bearing 80; wherein the axial bearing 80 is only located on one end of the first and second rotating shafts 50, 60 near the high pressure portion 30. It should be noted that, the two ends of the first rotating shaft 50 and the second rotating shaft 60 are respectively provided with a shaft shoulder, and the radial bearing 70 and the axial bearing 80 are disposed at the shaft shoulders, so as to realize axial positioning of the radial bearing 70 and the axial bearing 80. It should be noted that the axial bearing 80 may be an angular contact bearing.

By providing the axial bearing 80 only on the end of the rotary shaft near the high pressure portion 30, the axial force which is not completely counteracted, the axial force caused by the factors such as the change of the working condition, etc. are carried, and the reliability of the operation of the twin-screw compressor is improved. Compared with the existing double-screw compressor, the axial bearing 80 is required to be arranged at the low-pressure stage and the high-pressure stage, the axial bearing 80 is also arranged at the middle partition part of the rotor to bear the axial force, and the axial force generated by the low-pressure part 20 and the high-pressure part 30 in the compressor can be balanced independently and is not buffered axially, so that the axial bearing 80 is not required to be arranged at the low-pressure part 20, and the compressor is more compact in structure and lower in cost.

As shown in fig. 5, fig. 5 differs from fig. 1 exemplarily in that: the casing 10 is provided with a primary air inlet 130, a primary air outlet 140, a secondary air inlet 150 and a secondary air outlet 160; the primary air suction port 130 is positioned on the side wall of the shell 10, and the primary air suction port 130 is communicated with the low-pressure notch 410; the primary exhaust port 140 is located at one end of the housing 10 near the low pressure portion 20; the secondary air suction port 150 is positioned on the side wall of the shell 10, and the secondary air suction port 150 is communicated with the high-pressure notch 420; the secondary exhaust port 160 is located at one end of the housing 10 near the high pressure portion 30; wherein the primary exhaust port 140 is in communication with the secondary intake port 150 via a conduit.

By arranging the first-stage air suction port 130 and the first-stage air discharge port 140 which are communicated with the low-pressure cavity 110 and arranging the second-stage air suction port 150 and the second-stage air discharge port 160 which are communicated with the high-pressure cavity 120, the compression work of the low-pressure part 20 and the high-pressure part 30 is respectively matched, and the flowing direction of working medium in the low-pressure cavity 110 is opposite to the flowing direction of working medium in the high-pressure cavity 120, so that axial force with opposite directions is formed in the low-pressure part 20 and the high-pressure part 30; the low-pressure notch 410 and the high-pressure notch 420 on the partition piece 40 are respectively communicated with the primary air suction port 130 and the secondary air suction port 150 to form an air suction channel of the low-pressure cavity 110 and the high-pressure cavity 120, so that the structure is simple, the processing is convenient, the replacement is convenient and the cost is low.

For example, as shown in fig. 5, the working medium enters the low pressure chamber 110 from the first stage suction port 130, is discharged from the first stage discharge port 140 after being compressed by the low pressure portion 20 by one stage, an axial force directed to the partition 40 by the first low pressure rotor 210 is formed on the first low pressure rotor 210, and an axial force directed to the partition 40 by the second low pressure rotor 220 is formed on the second low pressure rotor 220; the working medium after primary compression enters the high-pressure chamber 120 through the pipeline from the secondary air suction port 150, is discharged from the secondary air discharge port 160 after secondary compression by the high-pressure part 30, forms an axial force directed to the partition 40 by the first high-pressure rotor 310 on the first high-pressure rotor 310, forms an axial force directed to the partition 40 by the second high-pressure rotor 320 on the second high-pressure rotor 320, and thus the axial force generated by the rotor of the low-pressure part 20 is opposite to the axial force generated by the high-pressure part 30 in direction, and can offset at least partially.

The application further provides refrigeration equipment, which comprises the double-screw compressor according to any embodiment of the application, and further has all technical effects brought by the technical scheme of the embodiment. It should be noted that the refrigeration apparatus includes, but is not limited to, an air conditioner.

While the invention has been described with reference to a preferred embodiment, various modifications may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In particular, the technical features mentioned in the respective embodiments may be combined in any manner as long as there is no structural conflict. The present invention is not limited to the specific embodiments disclosed herein, but encompasses all technical solutions falling within the scope of the claims.

Claims (10)

1. A twin screw compressor, comprising:

a housing;

a low pressure part including a first low pressure rotor and a second low pressure rotor rotatably provided in the housing, the first low pressure rotor and the second low pressure rotor having spiral teeth of opposite directions and being engaged with each other to form a primary compression of a working medium; and

a high-pressure part including a first high-pressure rotor and a second high-pressure rotor rotatably provided in the housing, the first high-pressure rotor and the first low-pressure rotor being coaxially provided and turning the same, the second high-pressure rotor and the second low-pressure rotor being coaxially provided and turning the same, the first high-pressure rotor and the second high-pressure rotor being opposite in rotation direction of helical teeth and intermeshed to form a two-stage compression of a working medium;

the first low-pressure rotor and the first high-pressure rotor are opposite in spiral direction, and the second low-pressure rotor and the second high-pressure rotor are opposite in spiral direction, so that primary axial force generated by primary compression on the first low-pressure rotor and the second low-pressure rotor is opposite to secondary axial force generated by secondary compression on the first high-pressure rotor and the second high-pressure rotor.

2. The twin screw compressor of claim 1, comprising a divider disposed within the housing and dividing the housing into a low pressure chamber and a high pressure chamber isolated from each other;

the low-pressure part is positioned in the low-pressure cavity, and the high-pressure part is positioned in the high-pressure cavity.

3. The twin screw compressor of claim 2, wherein the divider has low pressure notches and high pressure notches disposed in a sidewall thereof;

the low-pressure notch extends to the end face of the partition piece, which is close to the low-pressure part, so that the low-pressure notch is communicated with the low-pressure cavity;

the high-pressure notch extends to the end face, close to the high-pressure part, of the partition piece so that the high-pressure notch is communicated with the high-pressure cavity;

wherein, the low pressure notch is not communicated with the high pressure notch.

4. The twin-screw compressor according to claim 3, wherein the housing is provided with a primary suction port, a primary discharge port, a secondary suction port, and a secondary discharge port;

the primary air suction port is positioned at one end of the shell close to the low-pressure part;

the primary exhaust port is positioned on the side wall of the shell and is communicated with the low-pressure notch;

the secondary air suction port is positioned at one end of the shell close to the high-pressure part;

the secondary exhaust port is positioned on the side wall of the shell and is communicated with the high-pressure notch;

wherein, the first-stage exhaust port is communicated with the second-stage air suction port through a pipeline.

5. The twin-screw compressor according to claim 3, wherein the housing is provided with a primary suction port, a primary discharge port, a secondary suction port, and a secondary discharge port;

the primary air suction port is positioned on the side wall of the shell and is communicated with the low-pressure notch;

the first-stage exhaust port is positioned at one end of the shell close to the low-pressure part;

the secondary air suction port is positioned on the side wall of the shell and is communicated with the high-pressure notch;

the secondary exhaust port is positioned at one end of the shell close to the high-pressure part;

wherein, the first-stage exhaust port is communicated with the second-stage air suction port through a pipeline.

6. The twin screw compressor of claim 2, wherein the twin screw compressor comprises:

the first rotating shaft is rotatably arranged in the shell, and the first rotating shaft, the first low-pressure rotor and the first high-pressure rotor are integrally formed; and

the second rotating shaft is rotatably arranged in the shell, the rotating direction of the second rotating shaft is opposite to that of the first rotating shaft, the second rotating shaft is parallel to the first rotating shaft, and the second rotating shaft, the second low-pressure rotor and the second high-pressure rotor are integrally formed;

the first low-pressure rotor and the first high-pressure rotor are arranged at intervals in the axial direction of the first rotating shaft, and the second low-pressure rotor and the second high-pressure rotor are arranged at intervals in the axial direction of the second rotating shaft.

7. The twin screw compressor of claim 6, wherein the divider has a first through hole through which the first shaft passes and a second through hole through which the second shaft passes.

8. The twin screw compressor of claim 6, wherein the first and second shafts are connected at both ends to the housing by radial bearings.

9. The twin-screw compressor of claim 6, wherein axial bearings are provided on both the first and second shafts;

the axial bearing is only positioned at one end of the first rotating shaft and the second rotating shaft, which is close to the high-pressure part.

10. A refrigeration apparatus comprising a twin screw compressor as claimed in any one of claims 1 to 9.

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