WO2021088482A1 - Rotor à vis sans jeu et procédé de préparation associé - Google Patents

Rotor à vis sans jeu et procédé de préparation associé Download PDF

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Publication number
WO2021088482A1
WO2021088482A1 PCT/CN2020/112023 CN2020112023W WO2021088482A1 WO 2021088482 A1 WO2021088482 A1 WO 2021088482A1 CN 2020112023 W CN2020112023 W CN 2020112023W WO 2021088482 A1 WO2021088482 A1 WO 2021088482A1
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WO
WIPO (PCT)
Prior art keywords
rotor body
female
male
gap
male rotor
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Application number
PCT/CN2020/112023
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English (en)
Chinese (zh)
Inventor
刘华
武晓昆
龙忠铿
李日华
毕雨时
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珠海格力电器股份有限公司
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Publication of WO2021088482A1 publication Critical patent/WO2021088482A1/fr

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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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P9/00—Treating or finishing surfaces mechanically, with or without calibrating, primarily to resist wear or impact, e.g. smoothing or roughening turbine blades or bearings; Features of such surfaces not otherwise provided for, their treatment being unspecified
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B1/00—Processes of grinding or polishing; Use of auxiliary equipment in connection with such processes
    • 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
    • F04C18/20—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 dissimilar tooth forms
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the present disclosure relates to the technical field of screw compressor mainframes, in particular to a zero-clearance screw rotor and a preparation method thereof.
  • the screw compressor is a two-shaft rotary compressor that works on the principle of volume change. Its working principle is that the gas to be compressed is sucked into one of the working chambers, and the working chamber is then closed and reduced. The compressed gas undergoes a variable compression process in it. When the gas in the working chamber reaches the expected final pressure, the working chamber is immediately connected to the extrusion pipe, and when the working chamber continues to shrink, the compressed gas is discharged into the exhaust pipe.
  • the above process is mainly realized by the meshing of the male and female rotors. Specifically, the screw compressor realizes volume change through the periodic meshing and rotation of a pair of male and female rotors arranged in parallel, thereby completing the suction, compression and discharge processes.
  • leakage channels of different shapes and sizes between the female and male rotors, and between the rotor and the casing.
  • the main reasons include: 1) the inherent geometric characteristics of the rotor profile; 2) the lack of machining accuracy causes the rotor to deviate from the theory Dimensions; 3) The rotor deforms under the influence of gas force during operation; 4) The rotor deforms due to thermal expansion; 5) During the meshing process, the rotors contact each other to transmit torque, resulting in extrusion deformation and wear; 6) The rotor and the stationary parts Wear out due to abnormal contact.
  • These leakage passages cause leakage losses during the operation of the screw compressor, causing the actual operation process to deviate from the theoretical adiabatic compression, and the efficiency cannot reach the best.
  • the gap between the female and male rotors is called the meshing gap.
  • the low-pressure side of the leakage channel is always the suction pressure, and the other side is the compression process pressure and the exhaust pressure.
  • the pressure difference between the two sides of the leakage channel is relatively large during operation. Leakage losses have the most significant impact on the efficiency of the compressor. Therefore, it is necessary to reduce the area of the leakage passage, reduce the leakage loss, and improve the operating efficiency of the screw compressor.
  • the first objective of the present disclosure is to provide a zero-clearance screw rotor.
  • the second objective of the present disclosure is to provide a method for preparing the zero-clearance screw rotor.
  • the present disclosure relates to a zero-gap screw rotor, comprising a female rotor and a male rotor meshing with each other.
  • the female rotor includes a female rotor body
  • the male rotor includes a male rotor body.
  • Non-equidistant gap bands are arranged between them, the gap value A is 0.01-0.05 mm, and a non-metallic coating is arranged on the surface of the female rotor body and/or the male rotor body.
  • the non-metallic coating is only provided on the surface of the male rotor body, and the thickness of the coating is greater than or equal to A; or, the non-metallic coating is only provided on the surface of the female rotor body, so The thickness of the coating is greater than or equal to A; or, the non-metallic coating is provided on the surface of the male rotor body and the surface of the female rotor at the same time, and the thickness of the coating is greater than or equal to A/2.
  • the non-metallic coating is provided on the surface of the male rotor body and the surface of the female rotor body at the same time;
  • Equidistant gap bands are set on the surface of the male rotor body, the gap value is set to 0.01mm, and the coating thickness is ⁇ 0.01mm;
  • the non-metallic coating is provided on the surface of the male rotor body and the surface of the female rotor body at the same time;
  • Equidistant gap bands are set on the surface of the female rotor body, the gap value is set to 0.01mm, and the coating thickness is ⁇ 0.01mm;
  • the non-metallic coating is only provided on the surface of the male rotor body; non-equidistant gap bands are provided on the surface of the male rotor body, and the pitch circle on both sides of the driving side of the male rotor body is 1mm wide.
  • the gap value in the area is set to 0, the gap value in the 1mm width area on both sides of the non-driving side pitch circle of the male rotor body is set to 0.01mm, and the gap value of the rest of the surface of the male rotor body is set to 0.02mm , Coating thickness ⁇ 0.02mm.
  • the non-metallic coating is only provided on the surface of the female rotor body; non-equidistant gap bands are provided on the surface of the female rotor body, and a width of 1 mm on both sides of the pitch circle on the driving side of the female rotor body is provided.
  • the gap value in the area is set to 0, the gap value in the 1mm width area on both sides of the non-driving side pitch circle of the female rotor body is set to 0.01mm, and the gap value of the rest of the surface of the female rotor body is set to 0.02mm , Coating thickness ⁇ 0.02mm.
  • the material of the female rotor body and the male rotor body are both metal, selected from at least one of carbon structural steel, alloy structural steel, and ductile iron.
  • the non-metallic coating contains polytetrafluoroethylene and epoxy resin.
  • the present disclosure also relates to a preparation method of the zero-clearance screw rotor, which includes the following steps:
  • step (3) the female rotor and the male rotor are assembled on the meshing instrument, and the male rotor is driven by an external motor or manually for static dry grinding.
  • step (3) the static dry milling treatment includes the following steps:
  • Figure 1 is a schematic diagram of the structure of the male and female rotors.
  • Figure 2 is a related art design drawing of the male rotor gap.
  • Figure 3 is a design diagram of the female rotor gap in the related art.
  • Fig. 4 is a design diagram of equidistant gap bands on the surface of the male rotor body of the present disclosure.
  • Figure 5 is a design diagram of the non-equidistant gap zone on the surface of the female rotor body of the present disclosure.
  • the embodiment of the present disclosure relates to a zero-gap screw rotor, as shown in FIG. 1, which includes a female rotor 1 and a male rotor 2 that mesh with each other.
  • the female rotor 1 includes a female rotor body
  • the male rotor 2 includes a male rotor body. It can be seen from the figure that the female rotor body and the male rotor body are not completely meshed, and a non-equidistant gap is set between the two.
  • a non-metallic coating is provided on the surface of the female rotor body and/or the male rotor body.
  • a non-equidistant gap zone is preset on the surface of the female rotor body and/or the male rotor body, and a non-metallic coating is applied to the gap position to achieve zero gap between the female and male rotors.
  • the material of the female rotor body and the male rotor body is selected from at least one of carbon structural steel, alloy structural steel, and ductile iron.
  • the carbon structural steel can be No. 45 steel
  • the alloy structural steel can be 40Cr
  • the ductile cast iron can be ductile iron QT600-3.
  • the role of non-metallic coating is to reduce the serious wear between the female and male rotors and between the rotor and the casing due to friction.
  • the non-metallic coating of the embodiment of the present disclosure contains polytetrafluoroethylene and epoxy resin. Refer to the polytetrafluorovinyl bonded solid lubricant described in the patent 201410221946.0, which uses polyimide resin and epoxy resin as the binder, and polytetrafluoroethylene, melamine cyanurate and molybdenum disulfide as solids Lubricant, mixed solvent as diluent. After it is coated on the surface of mechanical parts and heated and cured, it can form a PTFE-based solid lubricating coating. It has good adhesion to metal substrates, good impact resistance, good corrosion resistance, low friction coefficient and long wear life.
  • the coating thickness needs to be slightly larger than the gap value. Further, 1) when the non-metallic coating is only provided on the surface of the male rotor body, reserve non-equidistant gaps on the surface of the male rotor body, and the thickness of the non-metallic coating is greater than or equal to A; 2) when the non-metallic coating is only provided On the surface of the female rotor body, reserve non-equidistant gaps on the surface of the female rotor body, and the thickness of the non-metallic coating is ⁇ A; 3) When the non-metallic coating is provided on the surface of the male rotor body and the surface of the female rotor body at the same time, That is, equidistant gap bands can be reserved on the surface of the male rotor body, non-equidistant gap bands can be reserved on
  • the screw compressor drives the female rotor 1 to rotate through the male rotor 2, and the gap-free area between the male and female rotors is also the area where the two are in partial contact. Since the relative speed of the female and male rotors at the pitch circle is relatively small, the drive area, that is, the area where the female and male rotors directly contact each other, is located on both sides of the pitch circle.
  • Pitch circle is a concept related to meshing motion. Seen from the axial direction when the two teeth are meshing, the contact point is called the meshing node. The linear velocity at this point is the same as the node, and the circle determined by the position of the node is called the pitch circle.
  • the rotation direction of the male rotor 2 is counterclockwise, and on one tooth of the male rotor 2, the surface driving the female rotor 1 to rotate is the male rotor driving side 21, and the other side is the male rotor non-driving side 22.
  • one side of the female rotor 1 in contact with the male rotor driving side 21 is the female rotor driving side 11, and the other side is the female rotor non-driving side 12.
  • the pitch circle of the female rotor 1 coplanar with the female rotor driving side 11 is the female rotor body driving side pitch circle 111
  • the pitch circle coplanar with the female rotor non-driving side 12 is the female rotor body non-driving side pitch circle 121.
  • the way of defining the pitch circle on the driving side and the pitch circle on the non-driving side of the male rotor body is similar to that of the female rotor 1. Compared with other areas, a smaller gap is required on both sides of the pitch circle. Therefore, at least one non-uniform gap is provided between the female and male rotors, that is, the gap on both sides of the pitch circle is small, and the rest is provided with a normal gap.
  • the screw rotor of the related art is usually made of metal, and the gap is designed on the surface of the female rotor 1. Specifically, no gaps are provided on both sides of the female rotor pitch circle, and equidistant gaps are provided for the remaining parts. No gap is provided on the surface of the male rotor 2, so power is transmitted through the pitch circle during meshing. If the surface is not provided with a non-metallic coating, the gap between the female and male rotors will cause leakage losses and reduce the efficiency of the compressor.
  • Figure 2 is a related art male rotor clearance design drawing.
  • the two ends of the curve are the non-drive side pitch circle and the drive side pitch circle.
  • the single curve in the figure shows that there is no gap on the surface.
  • Fig. 3 is a design diagram of the female rotor gap in the related art.
  • the protrusion on the left side of the curve represents the non-driving side pitch circle, and the protrusion on the right side represents the driving side pitch circle.
  • multiple short straight lines perpendicular to the curve represent the gaps at different positions, and the length of the straight line is the gap value.
  • the female rotor gap design method of the related technology is: no gap near the driving side pitch circle (within the 1mm width area on both sides of the driving side pitch circle), and near the non-driving side pitch circle (within the 1mm width area on both sides of the non-driving side pitch circle)
  • the gap is set to 0.02mm, and the gap value of the rest of the female rotor surface is set to 0.04mm.
  • the body of the female and male rotors needs to be provided with gaps to ensure the thickness of the coating.
  • Equidistant gaps can be provided on the surface of the male rotor body and non-equidistant gaps can be provided on the surface of the female rotor body; it is also possible to provide equidistant gaps on the surface of the female rotor body and non-equidistant gaps on the surface of the male rotor body. The following takes the first case as an example:
  • Fig. 4 is a design drawing of the equidistant gap zone on the surface of the male rotor body of the present disclosure.
  • the two ends of the curve are respectively the non-driving side pitch circle and the driving side pitch circle.
  • the lengths of the short straight lines perpendicular to the curve in the figure are equal, indicating that equidistant gap bands are set on the surface of the male rotor body, and the gap value is set to 0.01 mm for coating.
  • the coating thickness is ⁇ 0.01mm.
  • Figure 5 is a design diagram of the non-equidistant gap zone on the surface of the female rotor body of the present disclosure.
  • the length of the short straight line perpendicular to the curve changes near the pitch circles on both sides, indicating that a non-equidistant gap is set on the surface of the female rotor body.
  • the gap value in the 1mm width area on both sides of the drive side pitch circle of the female rotor body (right side protrusion) is set to 0, and the female rotor body is set to the 1mm width area on both sides of the non-driving side pitch circle (left side protrusion).
  • Set the gap value of 0.01mm the gap value of the rest of the female rotor body surface is set to 0.02mm, which is used to coat the coating.
  • the coating thickness is ⁇ 0.02mm.
  • equidistant gap bands are set on the surface of the female rotor body, the gap value is set to 0.01mm, and the coating thickness is ⁇ 0.01mm; Set the gap value in the 1mm width area on both sides of the drive side pitch circle of the main body to 0, set the gap value in the 1mm width area on both sides of the non-drive side pitch circle of the male rotor body to 0.01mm, and set the gap between the rest of the surface of the male rotor body The value is set to 0.02mm, and the coating thickness is ⁇ 0.02mm.
  • non-metallic coating when the non-metallic coating is only provided on the surface of the male rotor body, non-equidistant gap bands are provided on the surface of the male rotor body, and the drive side pitch circle of the male rotor body is within a 1mm width area on both sides of the pitch circle.
  • Set the gap value of the male rotor body to 0, set the gap value in the 1mm width area on both sides of the non-driving side pitch circle of the male rotor body to 0.01mm, set the gap value of the rest of the surface of the male rotor body to 0.02mm, and the coating thickness ⁇ 0.02 mm.
  • a non-equidistant gap is provided on the surface of the female rotor body, and the female rotor body is driven within a 1mm width area on both sides of the pitch circle.
  • the gap value of the female rotor body is set to 0, the gap value in the 1mm width area on both sides of the non-driving side pitch circle of the female rotor body is set to 0.01mm, the gap value of the rest of the female rotor body surface is set to 0.02mm, and the coating thickness is ⁇ 0.02 mm.
  • the present disclosure also relates to a preparation method of the zero-clearance screw rotor, which includes the following steps:
  • the female rotor 1 and the male rotor 2 need to be subjected to static dry grinding treatment.
  • the female rotor 1 and the male rotor 2 are assembled on the meshing instrument.
  • the male rotor 2 is driven by an external motor or manually driven to rotate.
  • the female rotor 1 is driven by the male rotor 2 for meshing motion.
  • the coating thickness is too large. Part of it will fall off due to the meshing of the rotor, and eventually the male and female rotors will run in to a zero gap state.
  • step (3) the rotational speed of the male rotor 2 is not easy to be set too high.
  • multiple dry grinding needs to be set, and the rotation speed is gradually increased to prevent direct high-speed dry grinding from causing the coating to fall off.
  • the static dry grinding treatment includes the following steps:
  • the first stage of running-in limit the rotation speed of the male rotor 2 to 30-35 rpm/min, and the time is 3 to 4 minutes. At this time, the coating is thicker, and low-speed running-in is required;
  • the present disclosure provides a zero-clearance screw rotor and a preparation method thereof.
  • a non-metallic coating is prepared on the basis of setting non-equidistant gaps on the surface of the male and female rotor bodies, and the female and male rotors are run-in to a zero gap state through static dry grinding treatment to obtain a zero gap screw rotor.
  • This treatment method can greatly reduce the leakage channel area, reduce the leakage loss, and improve the operating efficiency of the screw compressor.
  • Equidistant gap bands are set on the surface of the male rotor body, and the gap value is set to 0.01mm;
  • the material of the yin and yang rotors is 45 steel, and the yin and yang rotor gap design shown in Fig. 2 and Fig. 3 is adopted: that is, there is no gap on the surface of the male rotor 2;
  • the gap in the 1mm width area on both sides of the side pitch circle is set to 0.02mm, the gap value of the rest of the female rotor surface is set to 0.04mm, and the non-metallic coating is not coated on the surface of the female rotor.
  • the suction pressure, suction temperature and discharge pressure in Table 1 are the test conditions. In the actual test process, the above parameters cannot be adjusted to be completely equal, but the difference is within the allowable range.
  • the suction and discharge temperature, pressure and the control fluctuation range of the compressor motor are selected according to the specified values of GB/T 5773-2004 Positive Displacement Compressor Test Method.
  • the volumetric efficiency is a physical quantity that reflects the internal leakage of the compressor (theoretical value is 100%). It can be seen from Table 1 that comparing the example with the comparative example, the volumetric efficiency is increased by 4.97%, indicating that the leakage through the gap is greatly reduced.
  • COP is a physical quantity that describes the performance of the compressor. Due to the reduction in leakage, the leakage loss is reduced, and the compressor performance is increased by 5.5%;

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention divulgue un rotor à vis sans jeu et un procédé de préparation associé. Le rotor à vis sans jeu comprend un rotor femelle (1) et un rotor mâle (2) qui sont en prise l'un avec l'autre ; le rotor femelle (1) comprend un corps de rotor femelle ; le rotor mâle (2) comprend un corps de rotor mâle ; une zone de dégagement non équidistante est disposée entre le corps de rotor femelle et le corps de rotor mâle ; une valeur de dégagement A est de 0,01 mm à 0,05 mm et une couche de revêtement non métallique est disposée sur une surface du corps de rotor femelle et/ou du corps de rotor mâle.
PCT/CN2020/112023 2019-11-06 2020-08-28 Rotor à vis sans jeu et procédé de préparation associé WO2021088482A1 (fr)

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CN201911076028.2A CN110848137B (zh) 2019-11-06 2019-11-06 一种零间隙螺杆转子及其制备方法
CN201911076028.2 2019-11-06

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Publication number Priority date Publication date Assignee Title
CN110848137B (zh) * 2019-11-06 2023-11-10 珠海格力电器股份有限公司 一种零间隙螺杆转子及其制备方法
CN113953934B (zh) * 2021-11-11 2024-05-24 格力电器（武汉）有限公司 一种转子涂层预磨装置和预磨方法

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JP2009264307A (ja) * 2008-04-28 2009-11-12 Hitachi Industrial Equipment Systems Co Ltd スクリュー圧縮機
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JP2016079877A (ja) * 2014-10-16 2016-05-16 株式会社日立産機システム スクリュー圧縮機
CN110848137A (zh) * 2019-11-06 2020-02-28 珠海格力电器股份有限公司 一种零间隙螺杆转子及其制备方法

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WO2003061852A1 (fr) * 2002-01-23 2003-07-31 Carrier Corporation Procede d'application d'un enduit grossier sur des composants pour faciliter leur assemblage
CN1328513C (zh) * 2005-11-21 2007-07-25 西安交通大学 一种螺杆压缩机转子型线设计方法
CN105132086B (zh) * 2014-05-26 2018-02-27 中国科学院兰州化学物理研究所 聚四氟乙烯基粘结固体润滑剂
EP3399191B1 (fr) * 2017-05-03 2020-05-27 Kaeser Kompressoren SE Compresseur à vis avec revêtement multi-couche des vis de rotor
CN109630412A (zh) * 2018-12-12 2019-04-16 珠海格力电器股份有限公司 螺杆转子及压缩机
CN211314549U (zh) * 2019-11-06 2020-08-21 珠海格力电器股份有限公司 一种零间隙螺杆转子

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Publication number Priority date Publication date Assignee Title
CN1786476A (zh) * 2005-12-08 2006-06-14 无锡压缩机股份有限公司 干螺杆压缩机转子喷涂防腐层工艺
JP2009264307A (ja) * 2008-04-28 2009-11-12 Hitachi Industrial Equipment Systems Co Ltd スクリュー圧縮機
CN201377429Y (zh) * 2009-03-02 2010-01-06 上海维尔泰克螺杆机械有限公司 一种冷媒螺杆压缩机转子
JP2016079877A (ja) * 2014-10-16 2016-05-16 株式会社日立産機システム スクリュー圧縮機
CN110848137A (zh) * 2019-11-06 2020-02-28 珠海格力电器股份有限公司 一种零间隙螺杆转子及其制备方法

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