Manifold gas screw transformer, Manifold compressor, Manifold expander

Abstract

The present invention provides a branched-confluence gas screw transformer mechanism, a branched-confluence compressor, and a branched-confluence expander. The branched-confluence gas screw transformer mechanism comprises: a shell, in which a rotor cavity is formed; at least two screw rotors, all of which can be rotatably meshed and accept the constraints of the rotor cavity wall in the shell; the branched-confluence gas screw transformer mechanism is not provided with an air inlet plate and an exhaust plate. The branched-confluence gas screw transformer mechanism, the branched-confluence compressor, and the branched-confluence expander of the present invention can realize gas compression or expansion without providing an air inlet plate and an exhaust plate in the prior art by setting the relationship between the branching angle and the number of teeth of each spiral rotor, thereby overcoming the energy losses such as air flow disturbance loss and air flow friction loss caused by the air inlet plate and the exhaust plate in the prior art, and improving the response rate, service life, and energy efficiency of the branched-confluence gas screw transformer mechanism.

Description

Technical Field

[0001] The present invention relates to the technical field of gas compression and expansion, and in particular to a branched gas screw transformer mechanism, a branched compressor, and a branched expander. Background Art

[0002] The counter-meshing rotation of the two screw rotors combined with the fixed constraints of the rotor cavity wall, the air inlet plate and the exhaust orifice plate are the basic characteristics of the current screw compressor technology (especially twin-screw compressors) and screw expanders (especially twin-screw expanders).

[0003] Screw compressors have overcome the defects of piston compressors in mechanical vibration and service life to a considerable extent. Replacing the movable intake valve and exhaust valve with static intake orifice plates and exhaust orifice plates is the structural basis for screw compressors to achieve these beneficial effects. However, despite the different forms of movement, the intake orifice plates and exhaust orifice plates still have the properties of valves in essence, so the energy losses related to valves, such as air flow disturbance losses and air flow friction losses, have not been significantly improved. On the other hand, although the screw compressor is essentially a volumetric compressor, it also has a rotary property, and the use of intake orifice plates and exhaust orifice plates is not conducive to the full play of the rotary advantage, resulting in the current screw compressor technology failing to overcome or significantly reduce the gap between it and centrifugal, axial flow and other speed compressors in terms of air flow continuity, speed, etc.

[0004] Similarly, the intake and exhaust structures of piston expanders are more complex than those of piston compressors, so in terms of mechanical vibration and service life, the advantages of screw expanders over piston expanders are more obvious. However, due to the same valve function nature, valve-related energy losses still exist in screw expanders and piston expanders to varying degrees; and in terms of air flow continuity, rotation speed, etc., the use of intake and exhaust orifice plates also does not help to reduce the gap between screw expanders and turbine expanders. In addition, in terms of the time response of air flow and the proportion of energy loss caused by air flow disturbances, the negative impact of valves on expanders is greater than that on compressors. Therefore, the use of intake and exhaust orifice plates is both the basis for the current screw compressor and expander technology to function, but it is also an obstacle to further improvement of their performance. Summary of the invention

[0005] The present invention provides a manifold gas screw transformer mechanism, a manifold compressor, and a manifold expander that can compress or expand gas by reasonably setting the characteristics of the screw rotor without setting an air inlet orifice plate and an exhaust orifice plate, so as to solve the problems of energy loss and performance degradation of the screw compressor and / or screw expander caused by the air inlet orifice plate and the exhaust orifice plate in the prior art.

[0006] To this end, the present invention provides a branched gas screw pressure transformer mechanism, comprising:

[0007] a housing, wherein a rotor cavity is formed in the housing;

[0008] At least two screw rotors, all of which can mesh and rotate and are constrained by the wall of the rotor cavity in the shell, and among any two of the screw rotors, the product of the divergence angle and the number of teeth of one screw rotor is equal to the product of the divergence angle and the number of teeth of the other screw rotor;

[0009] The said branched gas screw transformer mechanism is not provided with an air inlet plate and an air outlet plate;

[0010] Alternatively, an air inlet plate and an air outlet plate are provided in the shell, but the gas pressure is changed without or mainly with the aid of the air inlet plate and the air outlet plate.

[0011] All the screw rotors include a central rotor and a peripheral rotor, all the peripheral rotors are meshed with the central rotor, and the relationship between the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotor and the number n of the peripheral rotors is: m1 = n*(m2±1).

[0012] The central rotor is a yang rotor, and all the peripheral rotors are yin rotors. The relationship between the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotors, and the number n of peripheral rotors is: m1=n*(m2-1); or, the central rotor is a yin rotor, and all the peripheral rotors are yang rotors. The relationship between the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotors, and the number n of peripheral rotors is: m1=n*(m2+1); or, the number of screw rotors is two, and the two screw rotors include a yang rotor and a yin rotor, and the yin rotor (2) is set as the central rotor. The relationship between the number of teeth m1 of the central rotor and the number of teeth m2 of the peripheral rotor is: m1=m2+1.

[0013] One of the component curves of the end surface profile of the screw rotor is a cycloid; or one of the component curves of the end surface profile of the screw rotor is a modified curve, a derived curve, or a replacement curve based on the cycloid.

[0014] The divergence angle P of the male rotor in the screw rotor is obtained by the following formula:

[0015] When α≤φ / 2, P=(1 / M+1 / N)*360°+φ-α±β;

[0016] When α≥φ / 2, P=(1 / M+1 / N)*360°+α±β;

[0017] Among them, α is the center angle of the tooth top circle of the male rotor end face profile line, φ is the center angle of the part of the male rotor outer circle invading the female rotor outer circle, P is the male rotor divergence angle, M is the number of male rotor teeth, N is the number of female rotor teeth, and β is the theoretical deviation value.

[0018] The screw rotor is formed with two working sections and a non-meshing section between the two working sections, and a radial communication port is provided on a portion of the shell corresponding to the non-meshing section.

[0019] The non-engaging section is provided with a reinforcement structure.

[0020] In the working section of the screw rotor, the helix angle of the screw rotor is a nonlinear function of the axial displacement.

[0021] The difference between the starting helix angle and the ending helix angle of the screw rotor is greater than the divergence angle of the screw rotor.

[0022] A manifold compressor comprises the above-mentioned manifold gas screw pressure transformer mechanism, wherein the process scheduling ratio of the manifold gas screw pressure transformer mechanism is greater than 1.

[0023] A branched expander comprises the above-mentioned branched gas screw pressure transformer, wherein the process scheduling ratio of the branched gas screw pressure transformer is less than 1.

[0024] The manifold gas screw transformer mechanism, manifold compressor, and manifold expander of the present invention can achieve compression or expansion of gas without setting the air inlet and exhaust orifice plates in the prior art by setting the structural characteristics of the rotor group, the relationship between the manifold angle and the number of teeth of each spiral rotor, and the size and change of the helical angle, thereby overcoming the energy losses such as air flow disturbance loss and air flow friction loss caused by the air inlet and exhaust orifice plates in the prior art, and can also overcome the influence of the air inlet and exhaust orifice plates on the continuity of the air flow, give full play to the rotation advantage of the screw rotor, and improve the response rate, service life and energy efficiency of the manifold gas screw transformer mechanism. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Hereinafter, the present invention will be described in more detail based on embodiments and with reference to the accompanying drawings.

[0026] Figure 1 1 is a schematic structural diagram of a manifold gas screw transformer mechanism provided in an embodiment of the present invention;

[0027] Figure 2 is another structural schematic diagram of a branched gas screw transformer mechanism provided in an embodiment of the present invention;

[0028] Figure 3 is another structural schematic diagram of a branched gas screw transformer mechanism provided in an embodiment of the present invention;

[0029] Figure 4 is another structural schematic diagram of a branched gas screw transformer mechanism provided in an embodiment of the present invention;

[0030] Figure 5 is another structural schematic diagram of a branched gas screw transformer mechanism provided in an embodiment of the present invention;

[0031] Figure 6 is another structural schematic diagram of a branched gas screw transformer mechanism provided in an embodiment of the present invention;

[0032] Figure 7 It is another structural schematic diagram of the branched gas screw transformer mechanism provided in an embodiment of the present invention.

[0033] In the drawings, the same reference numerals are used for the same components. The drawings are not drawn to scale.

[0034] 1. Male rotor; 2. Female rotor; 3. Housing; 31. Radial connecting port; 4. Reinforced structure. DETAILED DESCRIPTION

[0035] The present invention will be further described below in conjunction with the accompanying drawings.

[0036] like Figures 1 to 7As shown, the bifurcated gas screw transformer mechanism of the present invention comprises: a shell 3, in which a rotor cavity is formed; at least two screw rotors, all of which can be rotatably meshed and accept the constraint of the rotor cavity wall in the shell 3, and in any two of the screw rotors, the product of the bifurcated angle and the number of teeth of one screw rotor is equal to the product of the bifurcated angle and the number of teeth of the other screw rotor; the bifurcated gas screw transformer mechanism does not have an air inlet plate and an air outlet plate. By setting the structural characteristics of the rotor group, the relationship between the bifurcated angle and the number of teeth of each spiral rotor, the size and change of the spiral angle, the compression or expansion of the gas can be achieved without setting the air inlet plate and the air outlet plate in the prior art, thereby overcoming the energy losses such as the air flow disturbance loss and the air flow friction loss caused by the air inlet plate and the air outlet plate in the prior art, and also overcoming the influence of the air inlet plate and the air outlet plate on the continuity of the air flow, giving full play to the rotation advantage of the screw rotor, and improving the response rate, service life and energy efficiency of the bifurcated gas screw transformer mechanism. Among them, the divergence angle refers to the helix angle of a helix that can form a closed or nearly closed tooth slot space in one of the two intermeshing rotors under the constraint of the other rotor and the rotor cavity. In the intermeshing rotors, a divergence boat can be formed between the two rotors, and the gas can move along the axis of the rotor by riding on the divergence boat. During the movement, the gas is compressed or expanded by the change in the length of the divergence boat. Taking the dual rotor group as an example, the divergence boat is a dynamic tooth slot space of the female rotor and the male rotor that is closed or nearly closed between the front and rear points in the axial direction. The front point is the divergence point and the rear point is the confluence point; the divergence boat is fixed to maintain a helical angle span of a divergence angle, but the boat length of the divergence boat (the axial length of the divergence boat) is dynamically variable. The divergence boat properties of the multi-rotor group are the same as those of the dual rotor group, but the front point of the divergence boat is two or more identical divergence points, and the rear point is two or more identical confluence points. The intake process is the divergence boat formation process, the compression / expansion process is the divergence boat movement process, and the exhaust process is the divergence boat disappearance process. In a manifold screw compressor, there are multiple manifold boats working simultaneously in different phases, and the gas flow of each manifold boat is dynamically complementary, so the total airflow can be kept continuous and constant. Therefore, although the manifold screw compressor is volumetric in nature, it can achieve a pulsation-free airflow effect.

[0037] As another embodiment, an air inlet plate and an exhaust plate are provided in the shell 3, but the gas pressure change (compression or expansion) can be completed without or not mainly with the help of the air inlet plate and the exhaust plate, so that the air inlet plate and the exhaust plate are actually redundant settings and are not repeated here.

[0038] Among them, the branched-confluence gas screw transformer mechanism of the present application can be a compressor or an expander, and the gas inlet and outlet volume flow ratio is theoretically equal to the process scheduling ratio. The process refers to the axial length of the helix angle increasing by one branched-confluence angle within the working length from the starting point of the working section; the scheduling refers to the axial length of the helix angle decreasing by one branched-confluence angle within the working length until the end point of the working section. The processes of the female rotor and the male rotor are equal, and the scheduling is also equal. When the process scheduling ratio of the branched-confluence gas screw transformer mechanism is greater than 1, the branched-confluence gas screw transformer mechanism is a branched-confluence compressor; when the process scheduling ratio of the branched-confluence gas screw transformer mechanism is less than 1, the branched-confluence gas screw transformer mechanism is a branched-confluence expander.

[0039] All the screw rotors include a central rotor and a peripheral rotor, and all the peripheral rotors are meshed with the central rotor, and the relationship between the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotor, and the number n of the peripheral rotors is: m1 = n*(m2±1). On the basis of limiting the divergence angle and the number of teeth of the screw rotor, the quantitative relationship between the central rotor and the peripheral rotor is further limited to ensure that the gas can be reliably compressed or expanded in the structure where the gas equipment is not provided with an air inlet orifice plate and an exhaust orifice plate, and to ensure the working efficiency and reliability of the divergence type gas screw transformer mechanism.

[0040] Specifically, the central rotor is a male rotor 1, and all the peripheral rotors are female rotors 2. The relationship among the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotors, and the number n of the peripheral rotors is: m1=n*(m2-1).

[0041] Alternatively, the number of the screw rotors is two, the two screw rotors include a male rotor 1 and a female rotor 2, the female rotor 2 is used as the central rotor, and the male rotor 1 is used as the peripheral rotor, and the relationship between the number of teeth m1 of the central rotor and the number of teeth m2 of the peripheral rotor is: m1=m2+1.

[0042] Alternatively, the central rotor is a female rotor 2, and all the peripheral rotors are male rotors 1. The relationship between the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotors, and the number n of peripheral rotors is: m1=n*(m2+1).

[0043] One of the component curves of the end profile of the screw rotor is a cycloid, that is, part of the end profile of the screw rotor is in a cycloid shape. The end profile of the screw rotor includes a point, a tooth top circle, a tooth root circle and a cycloid, and can also be adjusted according to the specific requirements of the manifold gas screw transformer mechanism in which the screw rotor is located.

[0044] By taking the point, the tooth top circle, the tooth root circle and the cycloid as the basic components of the end profile of the screw rotor, it is possible to add correction elements on the basis of the basic components, such as forming a correction component by a straight line or curve for correcting an acute angle, that is, one of the component curves of the end profile of the screw rotor is a correction curve, a derivative curve or a replacement curve based on the cycloid;

[0045] The cycloid in the basic composition may also be replaced by its derivative line, such as the equidistant curve of the cycloid, or various curves (circular arc, ellipse, parabola, etc.) and their envelopes to form a derivative composition.

[0046] The divergence angle P of the male rotor 1 in the screw rotor is obtained by the following formula:

[0047] When α≤φ / 2, P=(1 / M+1 / N)*360°+φ-α±β;

[0048] When α≥φ / 2, P=(1 / M+1 / N)*360°+α±β;

[0049] Among them, α is the center angle of the tooth top circle of the end face profile of the male rotor 1, φ is the center angle of the part of the outer circle of the male rotor 1 invading the outer circle of the female rotor 2, P is the divergence angle of the male rotor 1, M is the number of teeth of the male rotor 1, N is the number of teeth of the female rotor 2, β is the theoretical deviation value, and preferably, β is the divergence angle deviation caused by the deviation of the end face profile of the male rotor 1 from the basic structure due to correction, derivation or other processing, reserved clearance, processing error and the like.

[0050] Specifically, the number of the outer rotors is two, and the two outer rotors are respectively arranged on both sides of the central rotor, and the central axes of the two outer rotors are in the same plane as the central axis of the central rotor, and the two outer rotors are symmetrically arranged on both sides of the central rotor.

[0051] Likewise, the number of the peripheral rotors is three, and the three peripheral rotors are distributed around the central rotor in a triangle shape.

[0052] As an embodiment, the screw rotor is formed with two working sections and a non-meshing section between the two working sections, and a radial connecting port 31 is provided on the portion of the shell corresponding to the non-meshing section. By providing the non-meshing section, the connection between the two working sections can be realized, and an air inlet channel or an air exhaust channel can be provided for the two working sections. At this time, the branched gas screw transformer mechanism forms an opposing configuration. When the radial connecting port 31 is used as an air inlet, the screw rotors on both sides of the radial connecting port 31 obtain gas from the radial connecting port 31, and drive the gas in two opposite directions, and finally discharge it through the two ends of the shell 3. In this process, the axial forces on the working sections on both sides are equal in magnitude and opposite in direction, so that they can be completely offset. Therefore, there is no need to provide a thrust bearing, and even a roller bearing is not required. Only a ball bearing can meet the needs, which is conducive to giving full play to the high speed advantage of the screw rotor. When the radial communication port 31 is used as an exhaust port, the screw rotors on both sides of the radial communication port 31 obtain gas from the two ends of the shell 3 respectively, and drive the gas in two opposite directions, and finally discharge it through the radial communication port 31. In this process, the axial forces on the working sections on both sides are equal in magnitude and opposite in direction, so they can be completely offset. There is no need to set up thrust bearings, and even roller bearings are not required. Only ball bearings can meet the needs, which is conducive to giving full play to the high speed advantage of the screw rotor. The axial space where the male rotor 1 and the female rotor 2 are in meshing state and constrained by the shell 3 is the working section. The axial length of each working section is its working length.

[0053] Taking the starting point of the working section as the zero point of the axial displacement and the helical angle, within the working length range, the helical angles of the male rotor 1 and the female rotor 2 are both nonlinear functions of the axial displacement, and the product of the helical angle and the number of teeth of the male rotor 1 and the female rotor 2 is equal at the same axial displacement. The difference between the starting and ending helical angles of the male rotor 1 and the female rotor 2 is respectively greater than the divergence angle of their helical lines, that is, the difference between the starting helical angle and the ending helical angle of the screw rotor is greater than the divergence angle of the screw rotor.

[0054] The gas screw transformer mechanism can be divided into single-suction rotor configuration, opposed double-suction rotor configuration and opposed double-row rotor configuration according to the distribution of working sections on the screw rotor:

[0055] In the single-suction rotor configuration, both ends of the shell 3 are open, and the airflow enters the working section axially or radially from one end of the shell 3 and is discharged from the working section axially or radially from the other end of the shell 3 .

[0056] In the opposed double-suction rotor configuration, both ends of the shell 3 are open, and the airflow enters the two working sections axially from the two ends of the shell 3, and then axially discharges from the two working sections into the internal space of the shell 3 corresponding to the radial communication port 31. In the opposed double-suction rotor configuration, the helical lines of the working sections of the two screw rotors are arranged according to the single-suction rotor configuration, but the helical directions of the helical lines of the two working sections are opposite, and the starting and ending points are axially inverted. The exhaust channel under the opposed double-suction rotor configuration is arranged in the axial space sandwiched by the two working sections (the internal space of the shell 3 corresponding to the radial communication port 31).

[0057] In the opposed double-row rotor configuration, the airflow enters the two working sections axially from the internal space of the shell 3 corresponding to the radial communication port 31, and then axially discharges the two working sections from the two ends of the shell. In the opposed double-row rotor configuration, the helical lines of the working sections of the two screw rotors are arranged according to the single-suction rotor configuration, but the helical directions of the helical lines of the two working sections are opposite, and the starting and ending points are axially inverted. The air intake channel in the opposed double-suction rotor configuration is arranged in the axial space sandwiched between the two working sections (the internal space of the shell 3 corresponding to the radial communication port 31).

[0058] The shell 3 does not cover or restrict the upstream part of the cylinder intersecting the working section of the screw rotor, and the airflow enters the working section radially from this non-covered area; or the shell 3 does not cover or restrict the downstream part of the cylinder intersecting the working section of the screw rotor, and the airflow radially discharges the working section from this non-covered area. The end of the shell 3 corresponding to the non-covered area can also be provided with an axial air intake channel or an axial exhaust channel at the same time, that is, the shell 3 can have both radial air intake channels and axial air intake channels for combined air intake, and can also have both radial exhaust channels and axial exhaust channels for combined exhaust.

[0059] The non-meshing section is provided with a reinforcement structure 4, which is used to improve the structural strength of the screw rotor. The reinforcement structure 4 is connected with the meshing teeth of the working section to further improve the structural reliability of the branched gas screw transformer mechanism.

[0060] In the working section of the screw rotor, the helix angle of the screw rotor is a nonlinear function of the axial displacement.

[0061] Preferably, by adjusting the pitch, the compression or expansion capacity of the manifold gas screw transformer mechanism can be adjusted to improve the reliability of the manifold gas screw transformer mechanism.

[0062] Example 1

[0063] like Figure 1It is a dual-rotor combined gas screw transformer mechanism, which belongs to the opposed double-suction rotor configuration, single axial intake and single axial exhaust, and no reinforcement structure 4 is set on the non-meshing section. The number of teeth of the male rotor 1 and the female rotor 2 are 3 and 2 respectively, and the speed ratio of the male rotor 1 and the female rotor 2 is 2:3. The combined angles of the male rotor 1 and the female rotor 2 are 390° and 585° respectively. A working section consists of two constant pitch sub-sections with unequal pitches. When used as a compressor, the process scheduling ratio is 2.800, and when used as an expander, the process scheduling ratio is 0.357.

[0064] A radial communication port 31 is provided in the middle section of the rotor cavity. When the radial communication port 31 is used as an inlet, the outlets are arranged at both ends of the rotor. Conversely, if the radial communication port 31 is used as an outlet, the inlet is arranged at both ends of the rotor.

[0065] The rotor cavity and the rotor in the present invention are not limited to a specific physical form. The rotor cavity can be one section, or a combination of two or more sections, and the opening can be selected in various ways according to needs. Similarly, the rotor shaft and / or the working section and / or the non-working section can also be composed of two or more sections.

[0066] Example 2

[0067] like Figure 2 It is another dual-rotor group bifurcated gas screw transformer mechanism, which belongs to the opposed double-suction rotor configuration, with a single axial intake and a single axial exhaust setting. No reinforcement structure 4 is set on the non-meshing section, and the radial connecting port 31 is the airflow inlet or outlet. The number of teeth of the male rotor 1 and the female rotor 2 are 4 and 3 respectively, and the speed ratio of the male rotor 1 and the female rotor 2 is 3:4. The bifurcated angles of the male rotor 1 and the female rotor 2 are 399.6° and 532.8° respectively. One working section is a single gradual pitch section. When used as a compressor, the process scheduling ratio is 1.442, and when used as an expander, the process scheduling ratio is 0.693.

[0068] Example 3

[0069] like Figure 3 It is a three-rotor group of gas screw transformer mechanism with a central rotor being a male rotor 1, and the screw rotors are a central male rotor 1 and two peripheral female rotors 2. It belongs to an opposed double-suction rotor configuration, with a single axial intake and a single axial exhaust setting, and no reinforcement structure 4 is set on the non-meshing section. A working section consists of two constant pitch sub-sections with unequal pitches. The number of teeth of the male rotor 1 and the female rotor 2 are both 2, and the speed ratio of the male rotor 1 and the female rotor 2 is 1:1. The divergence angles of the male rotor 1 and the female rotor 2 are both 410°. When used as a compressor, the process scheduling ratio is 2, and when used as an expander, the process scheduling ratio is 0.5. A radial connecting port 31 is provided in the middle section of the rotor cavity.

[0070] Example 4

[0071] like Figure 4 It is a three-rotor group of diverging gas screw transformer mechanism with the central rotor being the female rotor 2. The rotor group includes a central female rotor 2 and two peripheral male rotors 1. It belongs to an opposed double-suction rotor configuration, with a single axial intake and a single axial exhaust. No reinforcement structure 4 is set on the non-meshing section. A working section is composed of two constant pitch sub-sections with unequal pitches on both sides and a gradual pitch sub-section in the middle. The number of teeth of the male rotor 1 and the female rotor 2 are 6 and 2 respectively, and the speed ratio of the male rotor 1 and the female rotor 2 is 1:3. The diverging angles of the male rotor 1 and the female rotor 2 are 205.4° and 616.2° respectively. When used as a compressor, the process scheduling ratio is 2.269, and when used as an expander, the process scheduling ratio is 0.441. A radial connecting port 31 is provided in the middle section of the rotor cavity.

[0072] Example 5

[0073] like Figure 5 It is a four-rotor group bifurcated gas screw transformer mechanism with the central rotor being the male rotor 1. The rotor group includes a central male rotor 1 and three peripheral male rotors 1. It belongs to a single-suction rotor configuration, with a single axial intake and a single axial exhaust setting. The working section is composed of two constant pitch sub-sections with unequal pitches on both sides and a gradual pitch sub-section in the middle. The number of teeth of the male rotor 1 and the female rotor 2 are 2 and 3 respectively, and the speed ratio of the male rotor 1 and the female rotor 2 is 3:2. The bifurcated angles of the male rotor 1 and the female rotor 2 are 402° and 268° respectively. When used as a compressor, the process scheduling ratio is 1.884, and when used as an expander, the process scheduling ratio is 0.531. The inlet and outlet are respectively arranged at the two ends of the rotor, and no radial connecting port 31 is arranged in the middle section of the rotor cavity.

[0074] Example 6

[0075] like Figure 6 It is a four-rotor group of diverging gas screw transformer mechanism with the central rotor being the female rotor 2. The rotor group includes a central female rotor 2 and three peripheral male rotors 1. It belongs to an opposed double-suction rotor configuration, and a working section is a single gradual pitch section. The number of teeth of the male rotor 1 and the female rotor 2 are 9 and 2 respectively, and the speed ratio of the male rotor 1 and the female rotor 2 is 2:9. The diverging angles of the male rotor 1 and the female rotor 2 are 137.0° and 616.5° respectively. When used as a compressor, the process scheduling ratio is 2.831, and when used as an expander, the process scheduling ratio is 0.353. A radial connecting port 31 is provided in the middle section of the rotor cavity.

[0076] Example 7

[0077] like Figure 7 It is an opposed double-suction rotor configuration and an axial radial combined intake and axial radial combined exhaust arrangement. The reinforcement structure between the two working sections is a reinforcement rib, which connects the teeth of the two working sections together. The rotor working section characteristics are the same as those in Example 1.

[0078] Although the present invention has been described with reference to the embodiments, various modifications may be made thereto and parts thereof may be replaced by equivalents without departing from the scope of the present invention. In particular, the various technical features mentioned in the various 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, and the preferred embodiments are not limited to the specific embodiments disclosed herein, but include all technical solutions falling within the scope of the claims.

Claims

1. A branched gas screw transformer mechanism, characterized in that: include: A housing (3), wherein a rotor cavity is formed in the housing (3); At least two screw rotors, all of which are meshed and rotatable and are constrained by the wall of the rotor cavity in the housing (3), and of any two of the screw rotors, the product of the divergence angle and the number of teeth of one screw rotor is equal to the product of the divergence angle and the number of teeth of the other screw rotor; The said branched gas screw transformer mechanism is not provided with an air inlet plate and an air outlet plate; Or, the branched gas screw pressure transformer mechanism is provided with an air inlet plate and an air outlet plate, but the gas pressure transformation is not or not mainly performed with the aid of the air inlet plate and the air outlet plate; All the screw rotors include a central rotor and a peripheral rotor, all the peripheral rotors are meshed with the central rotor, and when the central rotor is a male rotor (1) and all the peripheral rotors are female rotors (2), the relationship between the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotor and the number n of peripheral rotors is: m1=n*(m2-1); or, when the central rotor is a female rotor (2) and all the peripheral rotors are male rotors (1), the relationship between the number of teeth m1 of the central rotor, the number of teeth m2 of the peripheral rotor and the number n of peripheral rotors is: m1=n*(m2+1); or, when the number of the screw rotors is two, the two screw rotors include a male rotor (1) and a female rotor (2), and the female rotor (2) is set as the central rotor, and the relationship between the number of teeth m1 of the central rotor and the number of teeth m2 of the peripheral rotor is: m1=m2+1.

2. The branched gas screw transformer mechanism according to claim 1, characterized in that: One of the component curves of the end surface profile of the screw rotor is a cycloid; or one of the component curves of the end surface profile of the screw rotor is a modified curve, a derived curve, or a replacement curve based on the cycloid.

3. The branched gas screw transformer mechanism according to claim 1, characterized in that: The divergence angle P of the male rotor (1) in the screw rotor is obtained by the following formula: When α≤φ / 2, P=(1 / M+1 / N)*360°+φ-α±β; When α≥φ / 2, P=(1 / M+1 / N)*360°+α±β; Wherein, α is the center angle of the tooth top circle of the end face profile of the male rotor (1), φ is the center angle of the portion of the outer circle of the male rotor (1) intruding into the outer circle of the female rotor (2), P is the divergence angle of the male rotor (1), M is the number of teeth of the male rotor (1), N is the number of teeth of the female rotor (2), and β is the theoretical deviation value.

4. The branched gas screw transformer mechanism according to claim 1, characterized in that: The screw rotor is formed with two working sections and a non-meshing section between the two working sections, and a radial communication port is provided on a portion of the shell corresponding to the non-meshing section.

5. The branched gas screw transformer mechanism according to claim 4, characterized in that: A reinforcement structure (4) is provided on the non-engaging section.

6. The branched gas screw transformer mechanism according to claim 1, characterized in that: In the working section of the screw rotor, the helix angle of the screw rotor is a nonlinear function of the axial displacement.

7. A branched compressor, characterized in that: It comprises the manifold gas screw transformer mechanism according to any one of claims 1 to 6, wherein the process scheduling ratio of the manifold gas screw transformer mechanism is greater than 1.

8. A branched expander, characterized in that: It comprises the manifold gas screw transformer mechanism according to any one of claims 1 to 6, wherein the process scheduling ratio of the manifold gas screw transformer mechanism is less than 1.

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