Double-screw compressor shell and double-screw compressor

Abstract

The invention provides a double-screw compressor shell and a double-screw compressor, the double-screw compressor shell comprises a shell outer cylinder and a shell inner cylinder, the shell inner cylinder forms a rotor cavity for accommodating double screws, the shell inner cylinder is detachably assembled in the shell outer cylinder, and the shell inner cylinder is detachably assembled in the shell outer cylinder. Air suction ports of the double-screw compressor comprise the axial air suction port and the radial air suction port, and the axial air suction port and the radial air suction port are formed in the machine shell inner cylinder. According to the double-screw compressor, the research and development and manufacturing cost can be remarkably reduced, the product iteration efficiency is improved, the cylinder in the machine shell can be flexibly adjusted according to the positions and shapes of the air suction port and the air exhaust port of the double-screw compressor, the matching performance of double screws and orifices is improved, and the efficiency of the compressor is improved.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of compressor design, and particularly relates to a double-screw compressor shell and a double-screw compressor. BACKGROUND

[0002] The body of an existing screw compressor is usually of an integral casting structure, and key flow channel features such as suction orifices, exhaust orifices and rotor cavities are formed at one time in the casting process. Although this structure has high structural rigidity and sealing performance, it has significant technical limitations. For example, the one-time cast shell in the prior art has the defect of irreconfigurability, that is, once the casting is fixed, the internal orifice position, size and geometric shape are fixed, and it cannot adapt to different length, tooth number or profile parameter rotor configurations, resulting in the need to re-open the mold when the product is iterated or the working condition is adjusted, long development cycle and high cost. SUMMARY

[0003] Therefore, the present application provides a double-screw compressor shell and a double-screw compressor, which can overcome the shortcomings of the one-time cast shell in the prior art, that is, once the casting is fixed, the internal orifice position, size and geometric shape are fixed, and it cannot adapt to different length, tooth number or profile parameter rotor configurations, resulting in the need to re-open the mold when the product is iterated or the working condition is adjusted, long development cycle and high cost.

[0004] To solve the above problems, the present application provides a double-screw compressor shell, which comprises a shell outer cylinder and a shell inner cylinder, the shell inner cylinder forms a rotor cavity for accommodating the double screw, the shell inner cylinder is detachably assembled in the shell outer cylinder, and the suction port of the double-screw compressor comprises an axial suction port and a radial suction port, both of which are formed on the shell inner cylinder.

[0005] In some embodiments, a bearing seat is formed on the first end port of the shell outer cylinder, a fixing seat is formed on the first end of the shell inner cylinder, and the shell inner cylinder is detachably connected to the bearing seat through the fixing seat; and / or, the thermal expansion coefficient of the shell inner cylinder is lower than that of the shell outer cylinder.

[0006] In some embodiments, the first end port of the shell outer cylinder is the intake end of the compressor, the bearing seat has an assembly surface facing one side of the exhaust end of the shell outer cylinder, and the fixing seat is assembled on the assembly surface.

[0007] In some embodiments, a first positioning pin is arranged between the assembly and fitting surface of the fixing seat and the bearing seat; and / or, the fixing seat and the bearing seat are bolted.

[0008] In some embodiments, a second locating pin is provided between the exhaust end of the outer cylinder of the housing and the assembly mating surface of the second end of the inner cylinder of the housing.

[0009] In some embodiments, a cooling channel is constructed within the inner cylinder of the housing, and the cooling channel is located on the outer periphery of the twin screw.

[0010] In some embodiments, the cooling channel includes an input main pipe, an output main pipe, and multiple branch pipes connecting the input main pipe and the output main pipe. The inlet of the input main pipe is located on one side of the second end of the inner cylinder of the housing, and the outlet of the output main pipe is located on one side of the first end of the inner cylinder of the housing.

[0011] In some embodiments, the outlet of the output manifold is located on the fixed base and the bearing housing has a communication hole that mates with the outlet; and / or, each of the branch pipes extends along the screw helix direction of the twin screw; and / or, when the twin screw compressor housing is in use, the position of the input manifold is higher than the position of the output manifold.

[0012] In some embodiments, the rotor cavity wall of the inner cylinder of the housing has a wear-resistant self-lubricating layer.

[0013] The present invention also provides a twin-screw compressor, including the twin-screw compressor housing described above.

[0014] The twin-screw compressor housing and twin-screw compressor provided by this invention have the following beneficial effects: The existing technology improves the compressor housing, which is a single-piece cast structure, into two parts: an outer housing and an inner housing. These two parts are assembled into one unit in a detachable manner. This allows for matching and improvement of the structure of the inner housing only, which is located on the inside, according to the actual operating requirements of the twin-screw compressor, without the need to match and improve the structure of the outer housing. In particular, when the outer housing is made as a single casting, there is no need to re-mold it, which significantly reduces R&D and manufacturing costs and improves product iteration efficiency. The inner housing can be flexibly adjusted to suit the position and shape of the twin-screw compressor's intake and exhaust ports, improving the compatibility between the twin screw (i.e., the rotor) and the orifice, which is beneficial to improving compressor efficiency. By setting a fixed seat on the inner cylinder of the housing and a bearing seat on the outer cylinder of the housing, the bearing seat can not only provide rotational support for the shaft ends of the aforementioned male rotor and female rotor, but also serve as a fixed carrier for the inner cylinder of the housing, thus simplifying the structural design of the inner cylinder of the housing and improving the positional stability and reliability of the inner cylinder of the housing. By placing the bearing housing at the air inlet end of the outer cylinder of the housing and assembling the fixing seat of the inner cylinder of the housing onto the mounting surface of the bearing housing near the exhaust end of the compressor, it is possible to achieve a detachable connection between the fixing seat and the bearing housing, while also enabling the bearing housing to axially position the inner cylinder of the housing. This effectively avoids the axial displacement caused by the axial force exerted on the inner cylinder of the housing by the compressed airflow due to the compressor's exhaust pressure being much higher than its intake pressure. The thermal expansion coefficient of the inner cylinder of the casing is lower than that of the outer cylinder of the casing. In other words, the thermal expansion coefficient of the material used to make the inner cylinder of the casing is higher than that of the material used to make the outer cylinder of the casing. This makes the expansion of the inner wall surface of the inner cylinder of the casing, which mates with the male and female rotors at high temperatures, smaller than that of conventional castings. This actively reduces the tooth tip clearance, achieves a "thermal compensation" effect, and effectively improves volumetric efficiency and thermal insulation efficiency. The rotor cavity wall of the inner cylinder of the housing, that is, the inner cylinder wall of the housing, has a wear-resistant self-lubricating layer. When the tooth tip clearance is too small and the twin screws come into contact with the inner cylinder of the housing, self-lubrication is achieved, ensuring operational reliability. Even when the clearance is close to zero under high temperature conditions, the rotor can still be prevented from scratching and jamming due to the excellent wear resistance and self-lubricating properties of the coating. By forming a cooling channel within the inner cylinder of the casing and introducing a cooling medium into the cooling channel, the cooling of the casing, rotor, and heat source inside the rotor cavity can be achieved more efficiently, effectively reducing exhaust temperature and the risk of thermal stress and oil carbonization. In this case, the material of the inner cylinder of the casing is, for example, the aforementioned copper alloy, which has a higher thermal conductivity than cast iron, further improving the cooling effect on the compressor. At the same time, since the inner cylinder of the casing is independent of the outer cylinder of the casing, the flow direction of the cooling channel can be designed more rationally, further improving the cooling effect and cooling efficiency. The outlet of the main output pipe is located on the fixed base, and the bearing housing has a connecting hole that connects to the outlet. That is, the cooling medium in the cooling channel can be introduced into the bearing housing, thereby further efficiently cooling the bearing assembled on the bearing housing, reducing the bearing temperature rise, and ensuring the high-speed and reliable operation of the rotor. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the accompanying drawings used in the description of the embodiments or related technologies will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0016] Figure 1 This is a cross-sectional view of the housing of the twin-screw compressor in an embodiment of the present invention (in the state of assembling the twin-screw compressor). Figure 2 yes Figure 1 A bottom view of the casing of a twin-screw compressor. Figure 3 yes Figure 1 A cross-sectional view of the casing of the twin-screw compressor at another location, showing a schematic diagram of the assembly state of the bearing housing and the fixed base; Figure 4 yes Figure 1 A three-dimensional structural diagram of the inner cylinder of the casing from one perspective; Figure 5 yes Figure 1 A three-dimensional structural diagram of the inner cylinder of the casing from another perspective; Figure 6 yes Figure 1 The figure shows a cross-sectional view of the casing of a twin-screw compressor at another location, and also shows a schematic diagram of the cooling flow channel structure arranged inside the inner cylinder of the casing. Figure 7 yes Figure 1 A three-dimensional structural diagram of the inner cylinder of the casing in another embodiment; Figure 8 A three-dimensional structural diagram of the inner cylinder of the casing before processing in an embodiment of the present invention.

[0017] The attached figures are labeled as follows: 1. Outer casing; 11. Bearing housing; 110. Assembly surface; 111. Connecting hole; 12. First end mounting flange; 13. Second end mounting flange; 2. Inner casing; 21. Fixing seat; 211. Pin hole; 212. Threaded hole; 22. First locating pin; 23. Bolt; 24. Second locating pin; 25. Keyway; 3. Cooling channel; 31. Input main pipe; 311. Inlet; 32. Output main pipe; 321. Outlet; 33. Branch pipe; 4. Bearing; 101. Radial intake port; 201. Male rotor; 202. Female rotor. Detailed Implementation

[0018] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0019] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0020] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90° or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0021] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0022] See also Figures 1 to 8As shown in the figure, according to an embodiment of the present invention, a twin-screw compressor housing is provided, including an outer housing body 1 and an inner housing body 2. The inner housing body 2 forms a rotor cavity (not indicated in the figure) for accommodating the twin screws. Specifically, the aforementioned twin screws include a male rotor 201 and a female rotor 202, which are paired and cooperate to form an inter-tooth compression space. The inner housing body 2 is detachably assembled inside the outer housing body 1, and the suction port of the twin-screw compressor includes an axial suction port. Both the axial and radial air intake ports 101 are formed on the inner cylinder 2 of the housing. That is, the outer cylinder 1 of the housing does not objectively have a structure to mate with the axial and radial air intake ports 101. The outer cylinder 1 of the housing has a first end flange 12 and a second end flange 13 formed at both ends. The first end flange 12 is used to mate with the intake end cap (not shown in the figure), and the second end flange 13 is used to mate with the exhaust end cap (not shown in the figure). It is understood that the outer cylinder wall of the inner cylinder 2 should be able to fit tightly with the inner cylinder wall of the outer cylinder 1 of the housing. That is, objectively, at the mating position, the shapes of the mating surfaces of the two cylinders are matched.

[0023] In this technical solution, the compressor housing, which is integrally cast in the prior art, is improved to consist of two parts: an outer housing 1 and an inner housing 2. The two parts are assembled into one unit in a detachable manner. In this way, only the structure of the inner housing 2 needs to be matched and improved according to the actual working conditions of the twin-screw compressor, without having to match and improve the structure of the outer housing 1. Especially when the outer housing 1 is made as an integral casting, there is no need to re-mold it, which significantly reduces R&D and manufacturing costs and improves product iteration efficiency. The inner housing 2 can be flexibly adjusted to suit the position and shape of the intake and exhaust ports of the twin-screw compressor, improving the matching between the twin screw (i.e., the rotor) and the orifice, which is beneficial to improving compressor efficiency.

[0024] It is understood that the outer cylinder 1 of the housing in this invention objectively only retains the external structural outline of the housing, and has no internal openings or rotor cavity features. All intake ports, exhaust ports, rotor cavities and oil passages are integrated on the inner cylinder 2 of the housing, realizing functional modularization and structural decoupling.

[0025] In some embodiments, a bearing seat 11 is formed on the first end port of the outer cylinder 1 of the housing. It is understood that the bearing seat 11 is provided with bearing chambers that correspond one-to-one with the shaft ends of the male rotor 201 and the female rotor 202, so that the male rotor 201 and the female rotor 202 are respectively rotated and supported by the bearing seat 11 through the bearing 4. A fixed seat 21 is formed on the first end of the inner cylinder 2 of the housing, and the inner cylinder 2 of the housing is detachably connected to the bearing seat 11 via the fixed seat 21.

[0026] In this technical solution, a fixed seat 21 is provided on the inner cylinder 2 of the housing, and a bearing seat 11 is provided on the outer cylinder 1 of the housing. The bearing seat 11 not only provides rotational support for the shaft ends of the aforementioned male rotor 201 and female rotor 202, but also serves as a fixed carrier for the inner cylinder 2 of the housing. This simplifies the structural design of the inner cylinder 2 of the housing and improves the positional stability and reliability of the inner cylinder 2 of the housing.

[0027] In some embodiments, the first end port of the outer cylinder 1 of the housing (i.e. Figure 1 The upper port shown in the diagram is the air inlet of the compressor. The bearing seat 11 has a mounting surface 110 facing the exhaust end of the outer cylinder 1 of the housing. The fixed seat 21 is assembled on the mounting surface 110.

[0028] In this technical solution, the bearing housing 11 is set at the air inlet end of the outer cylinder 1 of the housing, and the fixing seat 21 of the inner cylinder 2 of the housing is assembled on the mounting surface 110 of the bearing housing 11 on the side near the exhaust end of the compressor. This enables the fixing seat 21 and the bearing housing 11 to be detachably connected, while also enabling the bearing housing 11 to axially position the inner cylinder 2 of the housing. This effectively avoids the phenomenon of axial displacement caused by the axial force exerted on the inner cylinder 2 of the housing by the compressed airflow due to the compressor's exhaust end pressure being much higher than its intake end pressure.

[0029] In some embodiments, a first positioning pin 22 is provided between the assembly mating surfaces of the fixed base 21 and the bearing seat 11. The first positioning pin 22 enables pre-positioning of the inner cylinder 2 and the outer cylinder 1 of the housing, facilitating the assembly process. In one specific embodiment, two first positioning pins 22 are provided, spaced apart to ensure a more reliable relative position between the fixed base 21 and the bearing seat 11. It is understood that corresponding pin holes 211 are provided on the mating surfaces of the fixed base 21 and the bearing seat 11.

[0030] In one specific embodiment, the fixed seat 21 and the bearing seat 11 are bolted together by bolts 23. Bolts 23 can work with the aforementioned first positioning pin 22 to reliably connect and limit the first end of the inner cylinder 2 of the housing and the outer cylinder 1 of the housing.

[0031] In some embodiments, a second locating pin 24 is provided between the exhaust end of the outer casing 1 and the second end of the inner casing 2, as detailed below. Figure 2 As shown, keyways 25 extending axially along the outer cylinder 1 and the inner cylinder 2 are formed on the second end faces of the outer cylinder 1. A second locating pin 24 is inserted into the keyway 25, thereby locking the outer cylinder 1 and the inner cylinder 2 circumferentially and preventing circumferential displacement of the inner cylinder 2. Figure 2 In the embodiment shown, there are two second positioning pins 24, which are spaced apart along the circumferential direction of the outer cylinder 1 of the housing.

[0032] In some embodiments, the coefficient of thermal expansion of the inner cylinder 2 is lower than that of the outer cylinder 1. That is, the coefficient of thermal expansion of the material of the inner cylinder 2 is lower than that of the material of the outer cylinder 1. Specifically, the material of the inner cylinder 2 can be a copper alloy, stainless steel, etc., which have a lower coefficient of thermal expansion than cast iron. This makes the expansion of the inner wall surface of the inner cylinder 2 that mates with the male rotor 201 and female rotor 202 at high temperatures less than that of conventional castings, thereby actively reducing the tooth tip clearance, realizing the "thermal compensation" effect, and effectively improving volumetric efficiency and insulation efficiency.

[0033] In some embodiments, the rotor cavity wall of the inner cylinder 2, i.e., the inner cylinder wall of the inner cylinder 2, has a wear-resistant self-lubricating layer. Specifically, this wear-resistant self-lubricating layer can be a coating on the inner cylinder wall of the inner cylinder 2, such as a polyetheretherketone (PEEK) or polytetrafluoroethylene (PTFE) coating. This self-lubricating layer provides self-lubrication when the tooth tip clearance is too small and the twin screws come into contact with the inner cylinder 2, ensuring operational reliability. Even under high-temperature conditions where the clearance approaches zero, the excellent wear resistance and self-lubricating properties of the coating still prevent rotor scratches and jamming. In a feasible embodiment, the aforementioned wear-resistant self-lubricating layer is also provided on the outer surface of the teeth of the aforementioned male rotor 201 and female rotor 202.

[0034] When the compressor is used in heat pump operation, the compressor discharge temperature is very high. At this time, the viscosity of the refrigeration oil decreases, making it difficult to form an oil film, increasing leakage and affecting compressor efficiency. Furthermore, when the discharge temperature exceeds the limit operating temperature of the refrigeration oil, the refrigeration oil may even turn black and lose its function, affecting the reliability of the compressor. At the same time, the rotor undergoes significant thermal deformation under heat pump operation. To avoid friction between the rotor and the rotor cavity wall of the housing, the design value of the clearance between the rotor and the rotor cavity wall of the housing is increased, which further increases leakage and affects compressor efficiency. To solve the aforementioned problems of compressor use under heat pump operation, a cooling channel 3 is constructed inside the inner cylinder 2 of the housing, and the cooling channel 3 is located on the outer periphery of the twin screw.

[0035] In this technical solution, by forming a cooling channel 3 inside the inner cylinder 2 of the casing and introducing a cooling medium into the cooling channel 3, the cooling of the casing, rotor, and heat source inside the rotor cavity can be achieved more efficiently, effectively reducing the exhaust temperature and reducing the risk of thermal stress and oil carbonization. At this time, the material of the inner cylinder 2 of the casing is, for example, the aforementioned copper alloy, which has a higher thermal conductivity than cast iron, which can further improve the cooling effect on the compressor. At the same time, since the inner cylinder 2 of the casing is independent of the outer cylinder 1 of the casing, the flow direction of the cooling channel 3 can be designed more rationally, further improving the cooling effect and cooling efficiency.

[0036] In some embodiments, the cooling channel 3 includes an input main pipe 31, an output main pipe 32, and multiple branch pipes 33 connecting the input main pipe 31 and the output main pipe 32. The inlet 311 of the input main pipe 31 is located on one side of the second end of the inner cylinder 2 of the housing, and the outlet 321 of the output main pipe 32 is located on one side of the first end of the inner cylinder 2 of the housing.

[0037] In this technical solution, the inlet 311 of the cooling channel 3 is set at the exhaust end of the compressor and the outlet 321 is set at the suction end of the compressor, thereby forming a counter-flow of the cooling medium and the compressed air flow, which can improve the cooling efficiency by utilizing the high temperature difference.

[0038] In some embodiments, when the twin-screw compressor housing is in use, the position of the input manifold 31 is higher than the position of the output manifold 32, so that the weight of the cooling medium can be used to assist its flow, thereby reducing the operating power of the driving pumping components of the cooling medium.

[0039] See Figure 7 As shown, each of the branch pipes 33 extends along the screw helix direction of the twin screw. Ideally, each branch pipe 33 corresponds one-to-one with the position of the helical teeth on the male rotor 201 and female rotor 202, thus achieving comprehensive and balanced cooling of the compressed gas inside the compressor.

[0040] In some embodiments, the outlet 321 of the output manifold 32 is located on the fixed base 21 and the bearing housing 11 has a connecting hole 111 that mates with the outlet 321. That is, the cooling medium in the cooling channel 3 can be introduced into the bearing housing 11, thereby further efficiently cooling the bearing 4 assembled on the bearing housing 11, reducing the temperature rise of the bearing 4, and ensuring the high-speed and reliable operation of the rotor.

[0041] In summary, see Figure 1 As shown, the outer casing 1 (hereinafter referred to as the outer casting) includes two flange faces (i.e., the aforementioned first end mounting flange 12 and second end mounting flange 13) that are respectively connected to the intake end cover and the exhaust bearing seat, as well as the bearing seat 11 for mounting the bearing 4. However, the radial intake and exhaust ports of the conventional machine body are not provided at the rotor cavity. That is, the outer casing 1 does not have a structure that matches the rotor (i.e., the aforementioned twin screw, i.e., the male rotor 201 and the female rotor 202). Instead, an inner casing 2 (hereinafter referred to as the inner casting) is added as a part specifically for matching different rotor parameters. Under this design, no matter whether the rotor changes in length, diameter, or torsion angle, as long as the center distance between the male and female rotors is not changed, the outer casting does not need to be adjusted. Only the inner casting needs to be machined or the mold modified to fully match the rotor, thereby improving the compressor's operating efficiency. For example, under the conventional machine body structure, the rotor needs to... To match the cooling capacity requirements of customers, the rotor is shortened. In this case, the radial suction port spiral on the compressor body is cast in place, and there is no space for machining, making it impossible to match the shortened rotor. This causes the rotor's suction process to end prematurely, resulting in a decrease in the compressor's volumetric efficiency and adiabatic efficiency. Furthermore, after the rotor is shortened, the radial exhaust port becomes smaller. If the area of ​​the radial exhaust port cast in the compressor body is larger than the area of ​​the radial exhaust port that the shortened rotor can match, the compressor body cannot be machined to match the radial exhaust port of the shortened rotor (only mold modification is possible). This mismatch in the exhaust port leads to undercompression, reducing the compressor's adiabatic efficiency (shortening the rotor causes undercompression, and other modifications may lead to overcompression, but both reduce the compressor's adiabatic efficiency). Simultaneously, when optimizing the rotor design, only the inner casting needs to be machined or the mold modified, significantly reducing the cost and time of updates and iterations. The aforementioned inner casting can also be manufactured using 3D printing.

[0042] To demonstrate the convenience of the inner cylinder 2 of the housing of the present invention, Figure 8 The diagram shows the inner cylinder 2 of the housing before processing. It can be seen that the rotor cavity is actually two large cylinders. The radial air intake port, radial air exhaust port and axial air intake port can be processed to match rotors with different parameters. The plate of the assembly part, i.e. the fixed seat 21, can be thicker and wider to leave space for screws and pins.

[0043] According to an embodiment of the present invention, a twin-screw compressor is also provided, comprising the twin-screw compressor housing described above.

[0044] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0045] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A twin screw compressor housing, characterized in that, The double screw compressor comprises an outer casing cylinder (1) and an inner casing cylinder (2), the inner casing cylinder (2) is formed with a rotor cavity for accommodating the double screw, the inner casing cylinder (2) is detachably assembled in the outer casing cylinder (1), and the suction port of the double screw compressor comprises an axial suction port and a radial suction port (101), both of which are formed on the inner casing cylinder (2).

2. Double screw compressor housing according to claim 1, characterized in that A bearing seat (11) is formed on the first end port of the outer casing cylinder (1), a fixing seat (21) is formed on the first end of the inner casing cylinder (2), and the inner casing cylinder (2) is detachably connected to the bearing seat (11) through the fixing seat (21); and / or the thermal expansion coefficient of the inner casing cylinder (2) is lower than that of the outer casing cylinder (1).

3. Double screw compressor housing according to claim 2, characterized in that The first end port of the outer casing cylinder (1) is the air inlet end of the compressor, the bearing seat (11) has an assembly surface (110) facing the exhaust end side of the outer casing cylinder (1), and the fixing seat (21) is assembled on the assembly surface (110).

4. Double screw compressor housing according to claim 3, characterized in that A first positioning pin (22) is arranged between the assembly surface of the fixing seat (21) and the bearing seat (11); and / or the fixing seat (21) and the bearing seat (11) are bolted by bolts (23).

5. The twin screw compressor housing of claim 3, wherein, A second positioning pin (24) is arranged between the assembly surface of the exhaust end of the outer casing cylinder (1) and the second end of the inner casing cylinder (2).

6. The twin screw compressor housing of claim 2, wherein, A cooling flow channel (3) is arranged in the inner casing cylinder (2), and the cooling flow channel (3) is located on the outer circumferential side of the double screw.

7. Double screw compressor housing according to claim 6, characterized in that The cooling flow channel (3) comprises an input main pipe (31), an output main pipe (32), and a plurality of branch pipes (33) connected between the input main pipe (31) and the output main pipe (32), the inlet (311) of the input main pipe (31) is located on the second end side of the inner casing cylinder (2), and the outlet (321) of the output main pipe (32) is located on the first end side of the inner casing cylinder (2).

8. Double screw compressor housing according to claim 7, characterized in that The outlet (321) of the output main pipe (32) is located on the fixing seat (21), and the bearing seat (11) has a communication hole (111) which is in communication with the outlet (321); and / or each branch pipe (33) extends along the screw spiral direction of the double screw; and / or in the use state of the double screw compressor casing, the position of the input main pipe (31) is higher than that of the output main pipe (32).

9. The twin screw compressor housing of claim 1, wherein, The rotor cavity wall of the inner casing cylinder (2) is provided with a wear-resistant self-lubricating layer.

10. A twin screw compressor characterized by, The double screw compressor casing comprises the double screw compressor casing according to any one of claims 1 to 9.

Images