CN111878397B - Air compressor and expander of variable pitch screw rod - Google Patents

Air compressor and expander of variable pitch screw rod Download PDF

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Publication number
CN111878397B
CN111878397B CN202011039782.1A CN202011039782A CN111878397B CN 111878397 B CN111878397 B CN 111878397B CN 202011039782 A CN202011039782 A CN 202011039782A CN 111878397 B CN111878397 B CN 111878397B
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pitch
screw
variable
variable pitch
rotor
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CN111878397A (en
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张炯焱
卢阳
王立光
周坤
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Ningbo Baosi Energy Equipment Co Ltd
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Ningbo Baosi Energy Equipment Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor

Abstract

The invention relates to the technical field of air compression or expansion, and provides an air compressor and an expander of a variable-pitch screw, which comprise an air cylinder and a double-screw rotor group positioned in the air cylinder, wherein the double-screw rotor group consists of two screw rotors which are mutually meshed, and the screw rotors consist of two sections of variable-pitch screws with opposite rotation directions; the relationship between the axial position of the variable-pitch screw and the rotating angle of the variable-pitch screw can reduce the flow resistance to gas in the operation process of the double-screw rotor set, reduce noise, improve the shaft efficiency of the rotor and improve gas quantity; the screw rotor is formed by connecting two sections of variable-pitch screws with opposite rotation directions, partial radial force can be balanced, the rotor meets dynamic balance, the service life of the rotor is prolonged, the air suction amount is further increased, the volume efficiency of the rotor is improved, and the working efficiency of an air compressor or an expansion machine is further improved.

Description

Air compressor and expander of variable pitch screw rod
Technical Field
The invention relates to the technical field of air compression or expansion, in particular to an air compressor and an expansion machine of a variable-pitch screw.
Background
The screw rotors are also called screw rotors, the tooth surfaces of which are different in shape, and the double-screw rotors are a pair of screw rotors which are mutually meshed and have opposite rotation directions and are core components of an air compressor and an expander. The double-screw air compressor is used for compressing air, converts the mechanical energy of a prime motor into gas pressure energy, has the characteristics of simple and compact structure, stable operation, low mechanical vibration noise, high energy efficiency and the like, is widely applied to the fields of aviation, electronics, petroleum and the like, forms a plurality of compression cavity volumes which are periodically changed between two mutually meshed screw rotors and an inner cavity of a shell, realizes the suction, pressurization and discharge of gas, adopts the screw rotors with variable screw pitches to gradually reduce the volumes of the compression cavities, and can greatly improve the compression efficiency. The double-screw expander is a positive displacement expander, converts internal energy of gas into mechanical energy, is the inverse process of an air compressor, has the characteristics of few components, high reliability and stable torque output, is widely applied to the fields of industrial waste heat power generation, geothermal energy thermal power generation and solar thermal power generation, forms a plurality of working chambers with periodic change between two screw rotors which are mutually meshed and an inner cavity of a shell, realizes the suction, expansion and discharge of the gas, adopts the screw rotors with variable screw pitches to gradually reduce the volume of the working chambers, and can greatly improve the expansion efficiency.
Because the gas pulsates in the shell and is subject to flow resistance through a valve and the like, the gas can also rub with a moving part in the air compressor or the expansion machine, so that the energy is consumed no matter the sucked gas is compressed or expanded, and the working efficiency of the air compressor or the expansion machine is weakened.
Disclosure of Invention
The technical problem to be solved by the invention is to provide the air compressor with the variable-pitch screw, so that when double-screw rotor groups in the air compressor are meshed with each other, the flow resistance to gas can be reduced, the axial efficiency of the rotors is improved, partial radial force can be balanced, the air suction amount is increased, and the gas compression efficiency is improved.
The technical scheme of the invention is that the air compressor with the variable-pitch screw comprises an air cylinder and a double-screw rotor set positioned in the air cylinder, wherein the double-screw rotor set consists of two mutually meshed screw rotors, and the screw rotors consist of two sections of variable-pitch screws with opposite rotation directions which are connected; the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw meets the formula p = (p)e-ps)/L2*z2+psWhere p is the pitch of the variable pitch screw, z is the axial position of the variable pitch screw, psIs the starting pitch, p, of a variable-pitch screweThe end pitch of the variable pitch screw, L is the length of the variable pitch screw; the corresponding relation among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = p/(2 pi) × t, wherein t is the rotating angle of the variable pitch screw; the corresponding relation between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = - (L ((Pi)2*L2 +ps 2* t2-pe*ps*t2)0.5- π*L))/( pe*t -psT); two intermeshing screw rotorsComprises a male rotor and a female rotor, wherein the pitch and the number of teeth of the male rotor are respectively p1And z1The pitch and number of teeth of the female rotor are respectively p2And z2The relationship between the pitch and the number of teeth between the male rotor and the female rotor satisfies the formula p1/p2=z1/z2。
Compared with the prior art, the air compressor with the variable-pitch screw has the following advantages: the corresponding relation among the axial position of the variable-pitch screw, the pitch of the variable-pitch screw and the rotating angle of the variable-pitch screw can reduce the flow resistance to gas, reduce noise, improve the shaft efficiency of the rotor and improve the air suction amount in the running process of the double-screw rotor set; the screw rotor is formed by connecting two sections of variable-pitch screws with opposite rotation directions, partial radial force can be balanced, the rotor meets dynamic balance, the service life of the rotor is prolonged, the air suction amount is further increased, and the volumetric efficiency of the rotor and the working efficiency of the air compressor are improved.
Preferably, the pitch of one end of the variable pitch screw connected with the other variable pitch screw with opposite rotation directions is the initial pitch p of the variable pitch screwsThe pitch of the other end of the variable pitch screw is the ending pitch p of the variable pitch screweThe air suction port of the air compressor is arranged at the connecting part of two sections of variable-pitch screw rods with opposite rotating directions, and 2 air exhaust ports of the air compressor are respectively arranged at two ends of the screw rod rotor. By adopting the structure, the thermal deformation of the screw rotor is uniformly distributed, the service life of the rotor is effectively prolonged, and the displacement of one working cycle of the screw rotor is twice that of a common screw rotor, so that the working efficiency of compressing gas by the air compressor is greatly improved, and the screw rotor is more energy-saving and environment-friendly.
Preferably, the pitch of one end of the variable pitch screw connected with the other variable pitch screw with opposite rotation direction is the ending pitch p of the variable pitch screweThe pitch of the other end of the variable pitch screw is the initial pitch p of the variable pitch screwsThe air suction ports of the air compressor are 2 and are respectively arranged at two ends of the screw rotor, and the air exhaust port of the air compressor is arranged at two sections of variable screws with opposite rotation directionsThe distance from the connecting part of the screw. By adopting the structure, the thermal deformation of the screw rotor is uniformly distributed, the service life of the rotor is effectively prolonged, and the suction capacity of one working cycle of the screw rotor is twice that of a common screw rotor, so that the working efficiency of compressing gas by the air compressor is greatly improved, and the screw rotor is more energy-saving and environment-friendly.
Preferably, the meshed male rotor and female rotor adopt GHH tooth forms, the number of teeth of the male rotor is 3, and the number of teeth of the female rotor is 5; in the male rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the male rotor, and the initial pitch p of the variable-pitch screwss=600mm, end pitch p of a variable-pitch screwe=273mm, the length L of the variable pitch screw is =300mm, and the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p = (273-600)/3002*z2+600, the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw satisfies the formula z = - (30000 = (pi- (pi)2+ (109*t2)/50)0.5) /(109 × t); in the female rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the female rotor, and the initial pitch p of the variable-pitch screwss=1000mm, end pitch p of variable pitch screwe=455mm, the length L of the variable pitch screw is =300mm, and the correspondence between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p =5/3 ((273-2*z2+600), the correspondence between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw satisfies the formula z = - (18000 = (pi- (pi)2+ (109*t2)/18)0.5) /(109 × t). By adopting the structure, the screw rotor can be widely applied to small-sized air compressors.
Another technical problem to be solved by the present invention is to provide an expander with variable pitch screws, which can reduce the flow resistance to gas and improve the axial efficiency of rotors when the twin-screw rotor sets in the expander are engaged with each other, and can balance part of radial force and increase the suction amount, thereby improving the gas expansion efficiency.
Technical solution of the inventionThe expansion machine comprises an air cylinder and a double-screw rotor group positioned in the air cylinder, wherein the double-screw rotor group consists of two mutually meshed screw rotors, and the screw rotors consist of two sections of variable-pitch screws with opposite rotating directions; the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw meets the formula p = (p)e-ps)/L2*z2+psWhere p is the pitch of the variable pitch screw, z is the axial position of the variable pitch screw, psIs the starting pitch, p, of a variable-pitch screweThe end pitch of the variable pitch screw, L is the length of the variable pitch screw; the corresponding relation among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = p/(2 pi) × t, wherein t is the rotating angle of the variable pitch screw; the corresponding relation between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = - (L ((Pi)2*L2 +ps 2* t2-pe*ps*t2)0.5- π*L))/( pe*t -psT); the two screw rotors meshed with each other comprise a male rotor and a female rotor, wherein the screw pitch and the tooth number of the male rotor are respectively p1And z1The pitch and number of teeth of the female rotor are respectively p2And z2The relationship between the pitch and the number of teeth between the male rotor and the female rotor satisfies the formula p1/p2=z1/z2。
Compared with the prior art, the expander of the variable-pitch screw has the following advantages: the corresponding relation among the axial position of the variable-pitch screw, the pitch of the variable-pitch screw and the rotating angle of the variable-pitch screw can reduce the flow resistance to gas in the running process of the double-screw rotor set, reduce noise, improve the shaft efficiency of the rotor and improve the air suction amount; the screw rotor is formed by connecting two sections of variable-pitch screws with opposite rotating directions, partial radial force can be balanced, the rotor meets dynamic balance, the service life of the rotor is prolonged, the air suction volume is further increased, the volumetric efficiency of the rotor and the working efficiency of the expansion machine are improved, and the utilization rate of the internal energy of gas is improved.
Preferably, the pitch of one end of the variable pitch screw connected with the other variable pitch screw with opposite rotation directions is the initial pitch p of the variable pitch screwsThe pitch of the other end of the variable pitch screw is the ending pitch p of the variable pitch screweThe exhaust port of the expander is arranged at the connecting part of two sections of variable-pitch screws with opposite rotation directions, and 2 air suction ports of the expander are respectively arranged at two ends of the screw rotor. By adopting the structure, the thermal deformation of the screw rotor is uniformly distributed, the service life of the rotor is effectively prolonged, and the suction capacity of one working cycle of the screw rotor is twice that of a common screw rotor, so that the working efficiency of the expansion machine is greatly improved, and the expansion machine is more energy-saving and environment-friendly.
Preferably, the pitch of one end of the variable pitch screw connected with the other variable pitch screw with opposite rotation direction is the ending pitch p of the variable pitch screweThe pitch of the other end of the variable pitch screw is the initial pitch p of the variable pitch screwsThe air suction ports of the expanders are arranged at the connecting parts of two sections of variable-pitch screws with opposite rotation directions, and 2 air exhaust ports of the expanders are respectively arranged at two ends of the screw rotor. By adopting the structure, the thermal deformation of the screw rotor is uniformly distributed, the service life of the rotor is effectively prolonged, and the displacement of one working cycle of the screw rotor is twice that of the common screw rotor, so that the working efficiency of the expansion machine is greatly improved, and the expansion machine is more energy-saving and environment-friendly.
Preferably, the meshed male rotor and female rotor adopt GHH tooth forms, the number of teeth of the male rotor is 3, and the number of teeth of the female rotor is 5; in the male rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the male rotor, and the initial pitch p of the variable-pitch screwss=600mm, end pitch p of a variable-pitch screwe=273mm, the length L of the variable pitch screw is =300mm, and the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p = (273-600)/3002*z2+600, the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw is fullZu formula z = - (30000: (pi- (pi))2+ (109*t2)/50)0.5) /(109 × t); in the female rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the female rotor, and the initial pitch p of the variable-pitch screwss=1000mm, end pitch p of variable pitch screwe=455mm, the length L of the variable pitch screw is =300mm, and the correspondence between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p =5/3 ((273-2*z2+600), the correspondence between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw satisfies the formula z = - (18000 = (pi- (pi)2+ (109*t2)/18)0.5) /(109 × t). By adopting the structure, the screw rotor can be widely applied to small-size expansion machines, the loss of the internal energy of gas is reduced, and the conversion efficiency of mechanical energy is improved.
Drawings
FIG. 1 is a schematic structural view of an embodiment of a twin screw rotor set of the present invention within a cylinder.
Fig. 2 is a schematic structural diagram of an embodiment of a twin-screw rotor set in the air compressor with a variable pitch screw according to the present invention.
Fig. 3 is a cross-sectional view of fig. 2.
FIG. 4 is a schematic diagram of the construction of one embodiment of a twin screw rotor set in the variable pitch screw expander of the present invention.
Fig. 5 is a schematic structural view of another embodiment of a twin-screw rotor set in the expander of the variable pitch screw of the present invention.
As shown in the figure: 1. the air compressor comprises a male rotor, a female rotor, a male rotor, a.
Detailed Description
For a better understanding of the present application, various aspects of the present application will be described in more detail with reference to the accompanying drawings. It should be understood that the detailed description is merely illustrative of exemplary embodiments of the present application and does not limit the scope of the present application in any way. Like reference numerals refer to like elements throughout the specification.
In the drawings, the thickness, size, and shape of an object have been slightly exaggerated for convenience of explanation. The figures are purely diagrammatic and not drawn to scale.
It will be further understood that the terms "comprises," "comprising," "includes" and/or "including," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. Further, when a statement such as "… at least one" appears after the list of listed features, the entire listed feature is modified rather than modifying individual elements in the list.
Example 1:
as shown in fig. 1 to 3, the present embodiment discloses an air compressor with a variable pitch screw, comprising an "∞" shaped cylinder with two intersecting circles, a motor and a gear transmission system; the cylinder is provided with a male rotor 1 and a female rotor 2 which are meshed with each other, the male rotor and the female rotor are formed by connecting two sections of variable-pitch screws with opposite rotation directions and adopt GHH tooth forms, and the corresponding relation between the pitch of the variable-pitch screws and the axial position of the variable-pitch screws meets the formula p = (p =)e-ps)/L2*z2+psWhere p is the pitch of the variable pitch screw, z is the axial position of the variable pitch screw, psIs the starting pitch, p, of a variable-pitch screweThe end pitch of the variable pitch screw, L is the length of the variable pitch screw; the corresponding relation among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = p/(2 pi) × t, wherein t is the rotating angle of the variable pitch screw; the corresponding relation between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = - (L ((Pi)2*L2+ps 2* t2-pe*ps*t2)0.5- π*L))/( pe*t -psT); the pitch and number of teeth of the male rotor being p1And z1The pitch of the female rotor andthe number of teeth is p2And z2The relationship between the pitch and the number of teeth between the male rotor and the female rotor satisfies the formula p1/p2=z1/z2。
In this embodiment, the length of the male rotor is the same, the number of teeth of the male rotor is 3, and two sections of variable pitch screws with opposite rotation directions in the male rotor are symmetrical about a midperpendicular of the axis of the male rotor, wherein the initial pitch p of the variable pitch screwss=600mm (length unit: mm, same applies below), end pitch p of a variable pitch screwe=273mm, the length L of the variable pitch screw is =300mm, the numerical value of the parameter is substituted into the corresponding relation formula between the pitch of the variable pitch screw and the axial position of the variable pitch screw, and the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw is obtained and satisfies the formula p = (273-600)/3002*z2+600, and substituting the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw into the corresponding relation formula among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotation angle of the variable pitch screw to obtain the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw, wherein the corresponding relation satisfies the formula z = - (30000 = (pi- (pi)) of the variable pitch screw2+ (109*t2)/50)0.5) /(109 × t); the number of teeth of the female rotor is 5, two sections of variable pitch screws with opposite rotation directions in the female rotor are symmetrical about the perpendicular bisector of the axis of the female rotor, the length L of each variable pitch screw is =300mm, and the relation between the pitch and the number of teeth between the male rotor and the female rotor meets a formula p1/p2=z1/z2Substituting the tooth numbers of the male rotor and the female rotor into the formula to obtain the initial pitch p of the variable pitch screws=1000mm, end pitch p of variable pitch screwe=455mm, the corresponding relation between the screw pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p =5/3 ((273-)/600)/3002*z2+600), and the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw is brought into the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotation angle of the variable pitch screwThe corresponding relation between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw is obtained in a corresponding relation formula between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw, and the corresponding relation satisfies the formula z = - (18000 = (pi- (pi))2+ (109*t2)/18)0.5) /(109 × t). According to the above formula, the numerical values of the pitch of the variable pitch screw and the rotation angle of the variable pitch screw at any axial position of the variable pitch screw can be calculated. For example, at the position where the axial position z =200mm of the variable pitch screw, the pitch p of the variable pitch screw of the male rotor1=454.6667mm, the angle of rotation t =2.7639rad of the variable pitch screw of the male rotor (unit of measurement of angle: radians, the same applies below); pitch p of variable pitch screw of female rotor1=757.7778mm, the angle of rotation t =1.6583rad of the variable pitch screw of the female rotor.
The intermeshing male and female rotors are assembled in an infinity-shaped cylinder as shown in fig. 1, the male rotor is connected with a motor, the male rotor and the female rotor are in gear transmission, the motor drives the male rotor, the male rotor drives the female rotor, and the male rotor and the female rotor are meshed with each other and rotate in the cylinder to form a closed volume. The pitch of one end of the variable pitch screw rod, which is connected with the other section of variable pitch screw rod with opposite rotation direction, is the initial pitch p of the variable pitch screw rodsThe pitch of the other end of the variable pitch screw is the ending pitch p of the variable pitch screweThe air suction port of the air compressor is arranged at the connecting part of two sections of variable-pitch screw rods with opposite rotating directions, and 2 air exhaust ports of the air compressor are respectively arranged at two ends of the screw rod rotor. Air is sucked from an air compressor air suction port 3 at the connecting part of the two sections of variable-pitch screw rods which are oppositely screwed, and is compressed and then discharged from air compressor air exhaust ports 4 at two ends of the screw rotor.
In the embodiment, the design of the screw pitch of the variable-pitch screw in the air compressor can improve the air flow of the double-screw rotor set, reduce the flow resistance to the air and reduce the noise; the two variable-pitch screws form a symmetrical structure, the displacement of one working cycle of the screw rotors is twice that of a common single screw rotor, the working efficiency of the air compressor for compressing air is greatly improved, the energy is saved, the environment is protected, partial radial force can be balanced when the male and female rotors are meshed with each other, the screw rotors meet dynamic balance, the service life of the screw rotors is prolonged, and the volumetric efficiency and the shaft efficiency of the screw rotor set are improved; the middle air suction and the two-end discharge enable the thermal deformation of the screw rotor to be uniformly distributed, and the service life of the screw rotor can be effectively prolonged.
Example 2:
the air compressor with the variable pitch screw in the embodiment is different from the air compressor with the variable pitch screw in the embodiment 1 in that the pitch of one end of the variable pitch screw, which is connected with the other section of the variable pitch screw with the opposite rotation direction, is the ending pitch p of the variable pitch screweThe pitch of the other end of the variable pitch screw is the initial pitch p of the variable pitch screwsThe air suction ports of the air compressor are 2 and are respectively arranged at two ends of the screw rotor, and the air exhaust port of the air compressor is arranged at the connecting part of two sections of variable-pitch screws with opposite rotation directions. The air is sucked from air compressor suction ports at two ends of the screw rotor, and is compressed and then discharged from air compressor exhaust ports at connecting parts of two sections of variable-pitch screws which are opposite in rotating direction, the thermal deformation of the screw rotor is uniformly distributed due to the structure that the air is sucked at two ends and is sucked in the middle, the service life of the screw rotor is effectively prolonged, the suction capacity of one working cycle of the screw rotor is twice of that of a common single screw rotor, and the working efficiency of compressing air by the air compressor is greatly improved.
Example 3:
as shown in fig. 4, the present embodiment discloses an expander for a variable pitch screw, comprising an "∞" shaped cylinder with two circles intersecting, an electric motor and a gear transmission system; the cylinder is provided with a male rotor 1 and a female rotor 2 which are meshed with each other, the male rotor and the female rotor are formed by connecting two sections of variable-pitch screws with opposite rotation directions and adopt GHH tooth forms, and the corresponding relation between the pitch of the variable-pitch screws and the axial position of the variable-pitch screws meets the formula p = (p =)e-ps)/L2*z2+psWhere p is the pitch of the variable pitch screw, z is the axial position of the variable pitch screw, psIs the starting pitch, p, of a variable-pitch screweThe end pitch of the variable pitch screw, L is the length of the variable pitch screw; the axial position of the variable pitch screw and the screw thread of the variable pitch screwThe corresponding relation between the pitch and the rotating angle of the variable pitch screw meets the formula z = p/(2 pi) × t, wherein t is the rotating angle of the variable pitch screw; the corresponding relation between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = - (L ((Pi)2*L2 +ps 2* t2-pe*ps*t2)0.5- π*L))/( pe*t -psT); the pitch and number of teeth of the male rotor being p1And z1The pitch and number of teeth of the female rotor are respectively p2And z2The relationship between the pitch and the number of teeth between the male rotor and the female rotor satisfies the formula p1/p2=z1/z2。
In this embodiment, the length of the male rotor is the same, the number of teeth of the male rotor is 3, and two sections of variable pitch screws with opposite rotation directions in the male rotor are symmetrical about a midperpendicular of the axis of the male rotor, wherein the initial pitch p of the variable pitch screwss=600mm, end pitch p of a variable-pitch screwe=273mm, the length L of the variable pitch screw is =300mm, the numerical value of the parameter is substituted into the corresponding relation formula between the pitch of the variable pitch screw and the axial position of the variable pitch screw, and the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw is obtained and satisfies the formula p = (273-600)/3002*z2+600, and substituting the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw into the corresponding relation formula among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotation angle of the variable pitch screw to obtain the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw, wherein the corresponding relation satisfies the formula z = - (30000 = (pi- (pi)) of the variable pitch screw2+ (109*t2)/50)0.5) /(109 × t); the number of teeth of the female rotor is 5, two sections of variable pitch screws with opposite rotation directions in the female rotor are symmetrical about the perpendicular bisector of the axis of the female rotor, the length L of each variable pitch screw is =300mm, and the relation between the pitch and the number of teeth between the male rotor and the female rotor meets a formula p1/p2=z1/z2Then, the number of teeth of the male rotor and the female rotor is substituted into the formula to obtainTo the starting pitch p of the variable-pitch screws=1000mm, end pitch p of variable pitch screwe=455mm, the corresponding relation between the screw pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p =5/3 ((273-)/600)/3002*z2+600), the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw is brought into the corresponding relation formula among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotation angle of the variable pitch screw, and the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw is obtained and meets the formula z = - (18000 = (pi- (pi)) and the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw are obtained2+ (109*t2)/18)0.5) /(109 × t). According to the above formula, the numerical values of the pitch of the variable pitch screw and the rotation angle of the variable pitch screw at any axial position of the variable pitch screw can be calculated. For example, at the position where the axial position z =200mm of the variable pitch screw, the pitch p of the variable pitch screw of the male rotor1=454.6667mm, the angle of rotation t =2.7639rad of the variable pitch screw of the male rotor; pitch p of variable pitch screw of female rotor1=757.7778mm, the angle of rotation t =1.6583rad of the variable pitch screw of the female rotor.
The male rotor is connected with the motor, the male rotor and the female rotor are in transmission through the gear, the motor drives the male rotor, the male rotor drives the female rotor, and the male rotor and the female rotor are meshed with each other in the cylinder to rotate to form a closed volume. The pitch of one end of the variable pitch screw rod, which is connected with the other section of variable pitch screw rod with opposite rotation direction, is the initial pitch p of the variable pitch screw rodsThe pitch of the other end of the variable pitch screw is the ending pitch p of the variable pitch screweThe exhaust port of the expander is arranged at the connecting part of two sections of variable-pitch screws with opposite rotation directions, and 2 air suction ports of the expander are respectively arranged at two ends of the screw rotor. The direction of rotation of the rotor in the expander is opposite to that of the rotor in the air compressor of example 1, and the gas is sucked in from the expander air inlets 5 at both ends of the rotor, expanded and discharged from the expander air outlet 6 at the connecting portion of the two sections of variable pitch screws with opposite rotation directions.
In the embodiment, the design of the thread pitch of the variable-pitch screw in the expander can improve the gas flow of the double-screw rotor set, reduce the flow resistance to the gas and reduce the noise; the two variable-pitch screws form a symmetrical structure, the air suction amount of one working cycle of the screw rotor is twice that of a common single screw rotor, the working efficiency of the expansion machine is greatly improved, the energy is saved, the environment is protected, partial radial force can be balanced when the male and female rotors are meshed with each other, the screw rotor meets dynamic balance, the service life of the screw rotor is prolonged, and the volumetric efficiency and the shaft efficiency of the screw rotor set are improved; the two ends suck air and the middle part discharges air, so that the thermal deformation of the screw rotor is uniformly distributed, and the service life of the screw rotor can be effectively prolonged.
Example 4:
as shown in fig. 5, the expander of the variable pitch screw of the present embodiment is different from embodiment 3 in that the pitch of one end of the variable pitch screw connected to the other variable pitch screw having the opposite rotation direction is the end pitch p of the variable pitch screweThe pitch of the other end of the variable pitch screw is the initial pitch p of the variable pitch screwsThe air suction ports of the expanders are arranged at the connecting parts of two sections of variable-pitch screws with opposite rotation directions, and 2 air exhaust ports of the expanders are respectively arranged at two ends of the screw rotor. The direction of rotation of the rotor in the expander is opposite to that of the rotor in the air compressor of example 2, and the gas is sucked in from the expander inlet 7 located at the connection portion of the two stages of variable pitch screws with opposite rotation directions, expanded and then discharged from the expander outlet 8 at both ends of the rotor. The middle air suction and the two-end discharge enable the thermal deformation of the screw rotor to be uniformly distributed, the service life of the screw rotor can be effectively prolonged, the loss of the internal energy of the gas can be reduced, and the conversion efficiency of the mechanical energy is improved.
The above are merely specific examples of the present invention, and are not intended to limit the scope of the invention; it is intended that the following claims be interpreted as including all such alterations, modifications, and equivalents as fall within the true spirit and scope of the invention.

Claims (8)

1. Air compressor of variable-pitch screwThe machine comprises an air cylinder and a double-screw rotor group positioned in the air cylinder, wherein the double-screw rotor group consists of two screw rotors which are mutually meshed; the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw meets the formula p = (p)e-ps)/L2*z2+psWhere p is the pitch of the variable pitch screw, z is the axial position of the variable pitch screw, psIs the starting pitch, p, of a variable-pitch screweThe end pitch of the variable pitch screw, L is the length of the variable pitch screw; the corresponding relation among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = p/(2 pi) × t, wherein t is the rotating angle of the variable pitch screw; the corresponding relation between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = - (L ((Pi)2*L2 +ps 2* t2-pe*ps*t2)0.5- π*L))/( pe*t -psT); the two screw rotors meshed with each other comprise a male rotor and a female rotor, wherein the screw pitch and the tooth number of the male rotor are respectively p1And z1The pitch and number of teeth of the female rotor are respectively p2And z2The corresponding relation between the screw pitch and the tooth number between the male rotor and the female rotor satisfies the formula p1/p2=z1/z2。
2. The variable pitch screw air compressor of claim 1, wherein the pitch of the end of the variable pitch screw connected to the other variable pitch screw having the opposite direction of rotation is the initial pitch p of the variable pitch screwsThe pitch of the other end of the variable pitch screw is the ending pitch p of the variable pitch screweThe air suction port of the air compressor is arranged at the connecting part of two sections of variable-pitch screw rods with opposite rotating directions, and 2 air exhaust ports of the air compressor are respectively arranged at two ends of the screw rod rotor.
3. The air compressor of variable pitch screw of claim 1, wherein the pitch of one end of the variable pitch screw connected to the other variable pitch screw having the opposite direction of rotation is the final pitch p of the variable pitch screweThe pitch of the other end of the variable pitch screw is the initial pitch p of the variable pitch screwsThe air suction ports of the air compressor are 2 and are respectively arranged at two ends of the screw rotor, and the air exhaust port of the air compressor is arranged at the connecting part of two sections of variable-pitch screws with opposite rotation directions.
4. The air compressor of variable pitch screw as claimed in claim 2 or 3, wherein the male rotor and the female rotor engaged with each other have GHH tooth forms, the number of teeth of the male rotor is 3, and the number of teeth of the female rotor is 5; in the male rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the male rotor, and the initial pitch p of the variable-pitch screwss=600mm, end pitch p of a variable-pitch screwe=273mm, the length L of the variable pitch screw is =300mm, and the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p = (273-600)/3002*z2+600, the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw satisfies the formula z = - (30000 = (pi- (pi)2+ (109*t2)/50)0.5) /(109 × t); in the female rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the female rotor, and the initial pitch p of the variable-pitch screwss=1000mm, end pitch p of variable pitch screwe=455mm, the length L of the variable pitch screw is =300mm, and the correspondence between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p =5/3 ((273-2*z2+600), the correspondence between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw satisfies the formula z = - (18000 = (pi- (pi)2+ (109*t2)/18)0.5))/(109*t)。
5. An expander of a variable pitch screw comprises a cylinder and double screws arranged in the cylinderThe double-screw rotor group consists of two screw rotors which are mutually meshed, and is characterized in that the screw rotors are formed by connecting two sections of variable-pitch screws with opposite rotating directions; the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw meets the formula p = (p)e-ps)/L2*z2+psWhere p is the pitch of the variable pitch screw, z is the axial position of the variable pitch screw, psIs the starting pitch, p, of a variable-pitch screweThe end pitch of the variable pitch screw, L is the length of the variable pitch screw; the corresponding relation among the axial position of the variable pitch screw, the pitch of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = p/(2 pi) × t, wherein t is the rotating angle of the variable pitch screw; the corresponding relation between the axial position of the variable pitch screw and the rotating angle of the variable pitch screw meets the formula z = - (L ((Pi)2*L2 +ps 2* t2-pe*ps*t2)0.5- π*L))/( pe*t -psT); the two screw rotors meshed with each other comprise a male rotor and a female rotor, wherein the screw pitch and the tooth number of the male rotor are respectively p1And z1The pitch and number of teeth of the female rotor are respectively p2And z2The relationship between the pitch and the number of teeth between the male rotor and the female rotor satisfies the formula p1/p2=z1/z2。
6. The expander of a variable pitch screw as claimed in claim 5, wherein the pitch of the end of said variable pitch screw connected to the other variable pitch screw of opposite direction is the starting pitch p of the variable pitch screwsThe pitch of the other end of the variable pitch screw is the ending pitch p of the variable pitch screweThe exhaust port of the expander is arranged at the connecting part of two sections of variable-pitch screws with opposite rotation directions, and 2 air suction ports of the expander are respectively arranged at two ends of the screw rotor.
7. A variable pitch screw as defined in claim 5The expander of (1), wherein the pitch of one end of the variable pitch screw connected to the other variable pitch screw having the opposite rotation direction is an end pitch p of the variable pitch screweThe pitch of the other end of the variable pitch screw is the initial pitch p of the variable pitch screwsThe air suction ports of the expanders are arranged at the connecting parts of two sections of variable-pitch screws with opposite rotation directions, and 2 air exhaust ports of the expanders are respectively arranged at two ends of the screw rotor.
8. The variable pitch screw expander of claim 6 or 7 wherein the intermeshing male and female rotors are GHH tooth form, the number of teeth on the male rotor being 3 and the number of teeth on the female rotor being 5; in the male rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the male rotor, and the initial pitch p of the variable-pitch screwss=600mm, end pitch p of a variable-pitch screwe=273mm, the length L of the variable pitch screw is =300mm, and the corresponding relation between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p = (273-600)/3002*z2+600, the corresponding relation between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw satisfies the formula z = - (30000 = (pi- (pi)2+ (109*t2)/50)0.5) /(109 × t); in the female rotor, two sections of variable-pitch screws with opposite rotation directions are symmetrical about the midperpendicular of the axis of the female rotor, and the initial pitch p of the variable-pitch screwss=1000mm, end pitch p of variable pitch screwe=455mm, the length L of the variable pitch screw is =300mm, and the correspondence between the pitch of the variable pitch screw and the axial position of the variable pitch screw satisfies the formula p =5/3 ((273-2*z2+600), the correspondence between the axial position of the variable pitch screw and the rotation angle of the variable pitch screw satisfies the formula z = - (18000 = (pi- (pi)2+ (109*t2)/18)0.5))/(109*t)。
CN202011039782.1A 2020-09-28 2020-09-28 Air compressor and expander of variable pitch screw rod Active CN111878397B (en)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5667370A (en) * 1994-08-22 1997-09-16 Kowel Precision Co., Ltd. Screw vacuum pump having a decreasing pitch for the screw members
CN202140315U (en) * 2011-06-13 2012-02-08 浙江佳力科技股份有限公司 Sectional type varying-pitch rotor structure
CN102808771A (en) * 2012-08-14 2012-12-05 东北大学 Single-head varying-pitch screw rotor with equal tooth top width
CN209761717U (en) * 2019-03-15 2019-12-10 杭州久益机械股份有限公司 Variable-pitch double-screw air compressor
CN111350664A (en) * 2020-02-18 2020-06-30 宁波鲍斯能源装备股份有限公司 Screw rotor set and hydrogen circulating pump with same
CN111734632A (en) * 2020-08-10 2020-10-02 宁波鲍斯能源装备股份有限公司 Double-screw rotor set and vacuum pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5667370A (en) * 1994-08-22 1997-09-16 Kowel Precision Co., Ltd. Screw vacuum pump having a decreasing pitch for the screw members
CN202140315U (en) * 2011-06-13 2012-02-08 浙江佳力科技股份有限公司 Sectional type varying-pitch rotor structure
CN102808771A (en) * 2012-08-14 2012-12-05 东北大学 Single-head varying-pitch screw rotor with equal tooth top width
CN209761717U (en) * 2019-03-15 2019-12-10 杭州久益机械股份有限公司 Variable-pitch double-screw air compressor
CN111350664A (en) * 2020-02-18 2020-06-30 宁波鲍斯能源装备股份有限公司 Screw rotor set and hydrogen circulating pump with same
CN111734632A (en) * 2020-08-10 2020-10-02 宁波鲍斯能源装备股份有限公司 Double-screw rotor set and vacuum pump

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