WO2019153873A1 - 螺杆压缩机转子结构及具有其的变频螺杆压缩机 - Google Patents

螺杆压缩机转子结构及具有其的变频螺杆压缩机 Download PDF

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Publication number
WO2019153873A1
WO2019153873A1 PCT/CN2018/120371 CN2018120371W WO2019153873A1 WO 2019153873 A1 WO2019153873 A1 WO 2019153873A1 CN 2018120371 W CN2018120371 W CN 2018120371W WO 2019153873 A1 WO2019153873 A1 WO 2019153873A1
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Prior art keywords
rotor
arc segment
female
screw compressor
geometric center
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PCT/CN2018/120371
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English (en)
French (fr)
Inventor
刘华
张天翼
李日华
龙忠铿
许云功
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Priority to US16/967,630 priority Critical patent/US11629711B2/en
Priority to EP18905002.4A priority patent/EP3719321B1/en
Publication of WO2019153873A1 publication Critical patent/WO2019153873A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to the field of compressor equipment, and in particular to a screw compressor rotor structure and a variable frequency screw compressor having the same.
  • the compression performance of the fixed-frequency screw compressor is limited, resulting in a narrow application range of the fixed-frequency screw compressor.
  • an optimized profile has been obtained, but corresponding
  • the rotor tooth profile of the fixed-frequency screw compressor is directly used, which tends to cause a problem that the compression performance of the fixed-frequency compressor is lowered.
  • the main object of the present invention is to provide a screw compressor rotor structure and a variable frequency screw compressor having the same, to solve the problem of large leakage of the screw compressor in the prior art.
  • a screw compressor rotor structure comprising: a female rotor including a female rotor body, a plurality of female tooth portions provided on the female rotor body, and an end surface of the female rotor body
  • a tooth-shaped profile is formed between the crests of the adjacent two female tooth portions, and the tooth profile line is sequentially followed by the arc segment a 1 b, the envelope bc, the arc segment cd, the arc segment de in the counterclockwise direction
  • the arc segment ea 2 and the arc segment a 2 a 3 are connected end to end, wherein the arc segment cd and the center of the arc segment de are located on both sides of the tooth profile line.
  • the parametric equation of the arc segment cd is: Where R 2t is the pitch radius of the female rotor; ⁇ R is the adjustment parameter of the distance between the center of the arc segment cd and the root of the male rotor; R 3 is the height of the tooth portion; t is a partial tooth profile line The angle formed by the point and the line connecting the geometric center of the female rotor body and the geometric center of the male rotor; t 1 is the central angle of the arc segment cd.
  • the parametric equation of the arc segment de is: Where R 8 is the arc center parameter of the arc segment de; R 4 is the radius of the arc segment de; t 2 is the line connecting the point on the end of the arc segment cd to the center of the arc segment cd, and the yin The angle formed by the line connecting the geometric center of the rotor body and the geometric center of the male rotor; t 5 is the central angle of the arc segment de; t 8 is the central angle of the arc segment cd.
  • R 5 is the radius of the arc segment ea 2
  • t 3 is the line connecting the point on the end of the arc segment ea 2 to the geometric center of the female rotor body, and the geometric center of the female rotor body and the geometric center of the male rotor
  • the angle formed by the line connecting; t 9 is the central angle of the arc segment ea 2 .
  • the parametric equation of the arc segment a 2 a 3 is: Where t 0 is the line connecting the end of the arc segment ea 2 with the geometric center of the female rotor body, and the line connecting the geometric center of the female rotor body with the geometric center of the male rotor.
  • the parametric equation of the arc segment a 1 b is: Where R 7 is the radius of the arc segment a 1 b; t 4 is the line connecting the point on the head end of the arc segment a 1 b with the geometric center of the cathode rotor body, and the geometric center and the anode rotor of the female rotor body The angle between the lines of the geometric center is formed.
  • R 1t is the radius of the anode pitch of the anode
  • R 6 is the radius of the arc segment forming the envelope bc
  • It is the rotation angle of the anode rotor
  • A is the center distance between the cathode rotor and the anode rotor.
  • the screw compressor rotor structure further includes: a male rotor, the teeth of the male rotor meshing with the teeth of the female rotor.
  • the center of the arc segment cd of the female tooth portion is located on the line connecting the geometric center of the female rotor and the geometric center of the male rotor.
  • the distance from the center of the arc segment cd to the line connecting the geometric center of the rotor body and the geometric center of the male rotor is smaller than the center of the arc segment de to the rotor body. The distance between the geometric center and the geometric center of the male rotor.
  • the area utilization coefficient of the male rotor and the female rotor is Q, where 0.429 ⁇ Q.
  • variable frequency screw compressor comprising a screw compressor rotor structure, the screw compressor rotor structure being the screw compressor rotor structure described above.
  • a toothed profile line is formed between the tooth tips of two adjacent female tooth portions on the end surface of the female rotor body, and the tooth profile line is sequentially followed by the arc segment a 1 b and the envelope in the counterclockwise direction.
  • the line bc, the arc segment cd, the arc segment de, the arc segment ea 2 , and the arc segment a 2 a 3 are connected end to end, wherein the arc segment cd and the center of the arc segment de are set to be in the tooth shape On both sides of the line.
  • Such an arrangement can effectively optimize the profile line such that the opening of the tooth profile is larger than the opening of the tooth profile of the rotor structure of the prior art, which in turn reduces the pressure difference between the internal environment of the rotor structure and the external environment.
  • the profile of the tooth is more rationally set, so that the rotational speed of the rotor structure is reduced at the same flow rate.
  • the variable frequency screw compressor having the rotor structure enables the profile of the rotor structure to be applied to a variable frequency screw compressor, thereby effectively reducing the leakage amount of the compressor, thereby improving the compression energy efficiency and application of the variable frequency screw compressor. Sex.
  • Figure 1 shows a schematic structural view of an embodiment of a rotor structure embodiment in accordance with the present invention
  • Figure 2 is a schematic view showing the structure of the first embodiment of the toothed profile of the rotor structure according to the present invention
  • Fig. 3 is a view showing the structure of a second embodiment of a toothed profile of a rotor structure according to the present invention.
  • the female rotor body 11, the female tooth portion; 20, the male rotor; 21, the male tooth portion.
  • spatially relative terms such as “above”, “above”, “on top”, “above”, etc., may be used herein to describe as in the drawings.
  • the exemplary term “above” can include both “over” and "under”.
  • the device can also be positioned in other different ways (rotated 90 degrees or at other orientations) and the corresponding description of the space used herein is interpreted accordingly.
  • a screw compressor rotor structure is provided.
  • the screw compressor rotor structure includes a female rotor.
  • the female rotor includes a female rotor body 10.
  • a plurality of female tooth portions 11 are disposed on the female rotor body 10, and a tooth profile line is formed between the tooth tips of adjacent two female tooth portions 11 on the end surface of the female rotor body 10, and the tooth profile line is sequentially arced in the counterclockwise direction.
  • the line segment a 1 b, the envelope line bc, the arc segment cd, the arc segment de, the arc segment ea 2 , and the arc segment a 2 a 3 are connected end to end.
  • the arc segment cd and the center of the arc segment de are located on both sides of the tooth profile line.
  • such an arrangement can effectively optimize the profile line such that the opening of the tooth profile is larger than the opening of the tooth profile of the rotor structure of the prior art, which in turn reduces the internal environment of the rotor structure and The amount of pressure difference in the external environment is changed to reduce the leakage of refrigerant from the inside of the rotor structure.
  • the profile of the tooth is more rationally set, so that the rotational speed of the rotor structure is reduced at the same flow rate.
  • the variable frequency screw compressor having the rotor structure enables the profile of the rotor structure to be applied to a variable frequency screw compressor, thereby effectively reducing the leakage amount of the compressor, thereby improving the compression energy efficiency and application of the variable frequency screw compressor. Sex.
  • the rotor structure includes a female rotor and a male rotor.
  • the profile of the female rotor is given in the present application.
  • the profile of the male rotor can be uniquely determined according to the female rotor, and the design of the rotor is generally given first.
  • the profile of the female rotor or the male rotor is taken out, and then the profile of the other rotor is obtained according to the envelope principle of the profile.
  • the geometric center of the female rotor body 10 is taken as the origin, and the line connecting the geometric center of the female rotor body 10 and the geometric center of the male rotor is the horizontal axis to be perpendicular to the geometry of the female rotor body 10.
  • the line connecting the center and the geometric center of the male rotor establishes a Cartesian coordinate system for the vertical axis.
  • the parametric equation of the arc segment cd is:
  • R 2t is the pitch radius of the female rotor
  • ⁇ R is the adjustment parameter of the distance between the center of the arc segment cd and the root of the male rotor
  • R 3 is the height of the tooth portion 11
  • t is a partial tooth profile line The angle formed by the point and the line connecting the geometric center of the female rotor body 10 and the geometric center of the male rotor
  • t 1 is the central angle of the arc segment cd.
  • R 8 is the arc center parameter of the arc segment de
  • R 4 is the radius of the arc segment de
  • t 2 is the line connecting the point on the end of the arc segment cd to the center of the arc segment cd
  • yin The angle formed by the line connecting the geometric center of the rotor body 10 and the geometric center of the male rotor
  • t 5 is the central angle of the arc segment de
  • t 8 is the central angle of the arc segment cd.
  • R 5 is the radius of the arc segment ea 2 and t 3 is the line connecting the point on the end of the arc segment ea 2 to the geometric center of the female rotor body 10, and the geometric center of the female rotor body 10 and the male rotor
  • the angle formed by the line connecting the geometric centers, t 9 is the central angle of the arc segment ea 2 .
  • the parametric equation for the arc segment a 2 a 3 is: Where t 0 is the line connecting the end of the arc segment ea 2 with the geometric center of the female rotor body 10, and the line connecting the geometric center of the female rotor body 10 with the geometric center of the male rotor.
  • the parametric equation for the arc segment a 1 b is: Where R 7 is the radius of the arc segment a 1 b, and t 4 is the line connecting the point on the leading end of the arc segment a 1 b with the geometric center of the female rotor body 10, and the geometric center of the female rotor body 10 The angle formed by the line connecting the geometric centers of the male rotor.
  • R 1t is the radius of the anode radius of the anode
  • R 6 is the radius of the arc segment forming the envelope bc
  • A is the center distance between the female rotor and the male rotor.
  • the center of the arc segment cd of the female tooth portion 11 is located on the line connecting the geometric center of the female rotor and the geometric center of the male rotor.
  • the distance from the center of the arc segment cd to the line connecting the geometric center of the rotor body 10 to the geometric center of the male rotor is less than the distance from the center of the arc segment de to the line connecting the geometric center of the rotor body 10 to the geometric center of the male rotor.
  • the arc segment cd does not intersect the projection line of the arc segment de on the vertical axis.
  • the female tooth portions on the female rotor can be set to six, that is, the female rotor has six tooth profile lines, and the parameter equations of each curve are the same, that is, as shown in FIG.
  • the point a3 on the start end of the second profile line in the hour hand direction corresponds to the point a1 on the start end of the first profile line below it, and the joints of the respective arc segments are smooth and excessive.
  • the rotor structure can effectively improve the area utilization coefficient of the anode rotor and the cathode rotor, thereby effectively improving the utility and reliability of the rotor structure.
  • the screw compressor rotor structure in the above embodiment can also be used in the technical field of variable frequency compression equipment, that is, according to another aspect of the present invention, an inverter screw compressor is provided.
  • the variable frequency screw compressor comprises a screw compressor rotor structure, and the screw compressor rotor structure is the screw compressor rotor structure described above.
  • the rotor speed of the tooth profile line in the present application can be reduced.
  • the reduced speed helps to reduce the friction loss between the rotor and the loss of the suction and exhaust oil, thereby improving energy efficiency.
  • the exhaust flow of the compressor is relatively large.
  • the size of the exhaust orifice has a great influence on the pressure loss of the exhaust gas (for a fixed-frequency screw compressor, the pressure loss caused by the size of the exhaust orifice is not due to the small exhaust flow rate. The main factors affecting energy efficiency).
  • the exhaust orifice area of the rotor structure is large, which helps to reduce the exhaust pressure loss of the compressor, thereby improving the energy efficiency of the compressor.

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

Abstract

一种螺杆压缩机转子结构及具有其的变频螺杆压缩机。螺杆压缩机转子结构包括阴转子，阴转子包括阴转子本体（10），阴转子本体（10）上设置有多个阴齿部（11），阴转子本体（10）的端面上的相邻两个阴齿部（11）的齿顶之间形成齿形型线，齿形型线沿逆时针方向依次由弧线段a1b、包络线bc、弧线段cd、弧线段de、弧线段ea2、弧线段a2a3首尾连接形成，弧线段cd和弧线段de的圆心位于齿形型线两侧。

Description

螺杆压缩机转子结构及具有其的变频螺杆压缩机 技术领域
本发明涉及压缩机设备技术领域，具体而言，涉及一种螺杆压缩机转子结构及具有其的变频螺杆压缩机。
背景技术
现有技术中，定频螺杆压缩机的压缩性能有限，造成定频螺杆压缩机适用范围窄的问题，对于现有的定频螺杆压缩机，已经有了一套优化过的型线，但是对应变频压缩机而言，由于转速是改变的，使得直接使用该定频螺杆压缩机的转子齿部型线，容易造成定频压缩机的压缩性能下降的问题。
进一步地，由于现有技术中的不论是定频螺杆压缩机还是变频螺杆压缩机的转子结构的型线设置不合理，造成压缩机在压缩过程中冷媒泄漏量大的问题。
发明内容
本发明的主要目的在于提供一种螺杆压缩机转子结构及具有其的变频螺杆压缩机，以解决现有技术中螺杆压缩机泄漏量大的问题。
为了实现上述目的，根据本发明的一个方面，提供了一种螺杆压缩机转子结构，包括：阴转子，阴转子包括阴转子本体，阴转子本体上设置有多个阴齿部，阴转子本体的端面上的相邻两个阴齿部的齿顶之间形成齿形型线，齿形型线沿逆时针方向依次由弧线段a 1b、包络线bc、弧线段cd、弧线段de、弧线段ea 2、弧线段a 2a 3首尾连接形成，其中，弧线段cd和弧线段de的圆心位于齿形型线的两侧。
进一步地，弧线段cd的参数方程为：
Figure PCTCN2018120371-appb-000001
其中，R 2t为阴转子节圆半径；ΔR为弧线段cd的圆心与阳转子的齿根之间距离的调整参数；R 3为齿部的高度；t为部分的齿形型线上的点与阴转子本体的几何中心与阳转子的几何中心的连线形成的夹角；t 1为弧线段cd的圆心角。
进一步地，弧线段de的参数方程为：
Figure PCTCN2018120371-appb-000002
其中，R 8为弧线段de的圆弧中心参数；R 4为弧线段de的半径；t 2为弧线段cd的末端上的点至弧线段cd的圆心的连线，与阴转子本体的几何中心与阳转子的几何中心的连线形成的夹角；t 5为弧线段de的圆心角；t 8为弧线段cd的圆心角。
进一步地，弧线段ea 2的参数方程为：
Figure PCTCN2018120371-appb-000003
其中，R 5为弧线段ea 2的半径；t 3为弧线段ea 2的末端上的点至阴转子本体的几何中心的连线，与阴转子本体的几何中心与阳转子的几何中心的连线形成的夹角；t 9为弧线段ea 2的圆心角。
进一步地，弧线段a 2a 3的参数方程为：
Figure PCTCN2018120371-appb-000004
其中，t 0为弧线段ea 2的末端与阴转子本体的几何中心的连线，与阴转子本体的几何中心与阳转子的几何中心的连线形成的夹角。
进一步地，弧线段a 1b的参数方程为：
Figure PCTCN2018120371-appb-000005
其中，R 7为弧线段a 1b的半径；t 4为弧线段a 1b的首端上的点与阴转子本体的几何中心的连线，与阴转子本体的几何中心与阳转子的几何中心的连线形成的夹角。
进一步地，包络线bc的参数方程为：
Figure PCTCN2018120371-appb-000006
其中，R 1t为阳转子节圆半径；R 6为形成包络线bc的弧线段的半径；k＝i+1，i为阴转子的齿数与阳转子的齿数比；
Figure PCTCN2018120371-appb-000007
为阳转子的转角；A为阴转子与阳转子的中心距。
进一步地，螺杆压缩机转子结构还包括：阳转子，阳转子的齿部与阴转子的齿部相啮合。
进一步地，当阴齿部与阳转子的齿部啮合时，该阴齿部的弧线段cd的圆心位于阴转子的几何中心与阳转子的几何中心的连线上。
进一步地，当阴齿部与阳转子的齿部啮合时，弧线段cd的圆心至转子本体的几何中心与阳转子的几何中心的连线的距离，小于弧线段de的圆心至转子本体的几何中心与阳转子的几何中心的连线的距离。
进一步地，阳转子和阴转子的面积利用系数为Q，其中，0.429≤Q。
根据本发明的另一方面，提供了一种变频螺杆压缩机，包括螺杆压缩机转子结构，螺杆压缩机转子结构为上述的螺杆压缩机转子结构。
应用本发明的技术方案，阴转子本体的端面上的相邻两个阴齿部的齿顶之间形成齿形型线，齿形型线沿逆时针方向依次由弧线段a 1b、包络线bc、弧线段cd、弧线段de、弧线段ea 2、弧线段a 2a 3首尾连接形成，其中，将弧线段cd和弧线段de的圆心设置成位于齿形型线的两侧。 这样设置能够有效地优化了该齿形型线，使得齿部型线的开口大于现有技术中转子结构的齿部型线的开口，继而降低了转子结构的内部环境与外部环境的压差变化量，从而达到降低冷媒从转子结构内部泄漏的问题。采用该转子结构，使得齿部的型线设置更加合理，使得在相同的流量下降低了该转子结构的转速。尤其是具有该转子结构变频螺杆压缩机，使得该转子结构的型线能够适用于变频螺杆压缩机，有效地降低了该压缩机的泄漏量，从而提高了该变频螺杆压缩机的压缩能效和适用性。
附图说明
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示出了根据本发明的转子结构实施例的实施例的结构示意图；
图2示出了根据本发明的转子结构的齿形型线的实施例一的结构示意图；
图3示出了根据本发明的转子结构的齿形型线的实施例二的结构示意图。
其中，上述附图包括以下附图标记：
10、阴转子本体；11、阴齿部；20、阳转子；21、阳齿部。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、操作、器件、组件和/或它们的组合。
需要说明的是，本申请的说明书和权利要求书及附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的术语在适当情况下可以互换，以便这里描述的本申请的实施方式例如能够以除了在这里图示或描述的那些以外的顺序实施。此外，术语“包括”和“具有”以及他们的任何变形，意图在于覆盖不排他的包含，例如，包含了一系列步骤或单元的过程、方法、系统、产品或设备不必限于清楚地列出的那些步骤或单元，而是可包括没有清楚地列出的或对于这些过程、方法、产品或设备固有的其它步骤或单元。
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用 或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。
现在，将参照附图更详细地描述根据本申请的示例性实施方式。然而，这些示例性实施方式可以由多种不同的形式来实施，并且不应当被解释为只限于这里所阐述的实施方式。应当理解的是，提供这些实施方式是为了使得本申请的公开彻底且完整，并且将这些示例性实施方式的构思充分传达给本领域普通技术人员，在附图中，为了清楚起见，有可能扩大了层和区域的厚度，并且使用相同的附图标记表示相同的器件，因而将省略对它们的描述。
根据本发明的实施例，提供了一种螺杆压缩机转子结构。
具体地，如图1和图2所示，该螺杆压缩机转子结构包括阴转子。阴转子包括阴转子本体10。阴转子本体10上设置有多个阴齿部11，阴转子本体10的端面上的相邻两个阴齿部11的齿顶之间形成齿形型线，齿形型线沿逆时针方向依次由弧线段a 1b、包络线bc、弧线段cd、弧线段de、弧线段ea 2、弧线段a 2a 3首尾连接形成。其中，弧线段cd和弧线段de的圆心位于齿形型线的两侧。
在本实施例中，这样设置能够有效地优化了该齿形型线，使得齿部型线的开口大于现有技术中转子结构的齿部型线的开口，继而降低了转子结构的内部环境与外部环境的压差变化量，从而达到降低冷媒从转子结构内部泄漏的问题。采用该转子结构，使得齿部的型线设置更加合理，使得在相同的流量下降低了该转子结构的转速。尤其是具有该转子结构变频螺杆压缩机，使得该转子结构的型线能够适用于变频螺杆压缩机，有效地降低了该压缩机的泄漏量，从而提高了该变频螺杆压缩机的压缩能效和适用性。
在本实施例中，转子结构包括阴转子和阳转子，本申请中给出阴转子的型线特征，阳转子的型线特征可以根据阴转子唯一求出，转子的型线设计一般是先给出阴转子或者阳转子的型线，然后根据型线的包络原理,求出另外一个转子的型线。
如图1所示，以阴转子本体10的几何中心作为原点，以阴转子本体10的几何中心与阳转子的几何中心的连线所在的直线为横轴，以垂直于阴转子本体10的几何中心与阳转子的几何中心的连线为纵轴建立直角坐标系，其中，弧线段cd的参数方程为：
Figure PCTCN2018120371-appb-000008
其中，R 2t为阴转子节圆半径；ΔR为弧线段cd的圆心与阳转子的齿根之间距离的调整参数，R 3为齿部11的高度，t为部分的齿形型线上的点与阴转子本体10的几何中心与阳转子的几何中心的连线形成的夹角，t 1为弧线段cd的圆心角。
弧线段de的参数方程为：
Figure PCTCN2018120371-appb-000009
其中，R 8为弧线段de的圆弧中心参数，R 4为弧线段de的半径，t 2为弧线段cd的末端上的点至弧线段cd的圆心的连线，与阴转子本体10的几何中心与阳转子的几何中心的连线形成的夹角，t 5为弧线段de的圆心角，t 8为弧线段cd的圆心角。
进一步地，弧线段ea 2的参数方程为：
Figure PCTCN2018120371-appb-000010
其中，R 5为弧线段ea 2的半径，t 3为弧线段ea 2的末端上的点至阴转子本体10的几何中心的连线，与阴转子本体10的几何中心与阳转子的几何中心的连线形成的夹角，t 9为弧线段ea 2的圆心角。
弧线段a 2a 3的参数方程为：
Figure PCTCN2018120371-appb-000011
其中，t 0为弧线段ea 2的末端与阴转子本体10的几何中心的连线，与阴转子本体10的几何中心与阳转子的几何中心的连线形成的夹角。
弧线段a 1b的参数方程为：
Figure PCTCN2018120371-appb-000012
其中，R 7为弧线段a 1b的半径，t 4为弧线段a 1b的首端上的点与阴转子本体10的几何中心的连线，与阴转子本体10的几何中心与阳转子的几何中心的连线形成的夹角。
包络线bc的参数方程为：
Figure PCTCN2018120371-appb-000013
其中，R 1t为阳转子节圆半径，R 6为形成包络线bc的弧线段的半径，k＝i+1，i为阴转子的齿数与阳转子的齿数比，
Figure PCTCN2018120371-appb-000014
为阳转子的转角，A为阴转子与阳转子的中心距。该转子结构的阴转子与阳转子相互啮合配合实现压缩作业。
具体地，当阴齿部11与阳转子的齿部啮合时，该阴齿部11的弧线段cd的圆心位于阴转子的几何中心与阳转子的几何中心的连线上。弧线段cd的圆心至转子本体10的几何中心与阳转子的几何中心的连线的距离，小于弧线段de的圆心至转子本体10的几何中心与阳转子的几何中心的连线的距离。其中，弧线段cd与弧线段de在纵轴上的投影线不相交。采用该结构的转子结构，使得阳转子和阴转子的面积利用系数Q为：0.429≤Q。
如图3所示，在本实施例中，阴转子上的阴齿部可以设置成六个，即该阴转子具有六条齿部型线，每一条曲线的参数方程均相同，即如图3中逆时针方向的第二条型线的起始端上的点a3相当于位于其下方第一条型线的起始端上的点a1，各弧线段的连接处均为光滑过度。
采用该转子结构能够有效地提高了阳转子和阴转子的面积利用系数，从而有效地提高了该转子结构的实用性和可靠性。
上述实施例中的螺杆压缩机转子结构还可以用于变频压缩设备技术领域，即根据本发明的另一方面，提供了一种变频螺杆压缩机。该变频螺杆压缩机包括螺杆压缩机转子结构，螺杆压缩机转子结构为上述的螺杆压缩机转子结构。
采用该结构的转子压缩机能够取得如下的技术效果：
  阳转子面积/mm 2 阴转子面积/mm 2 面积利用系数 排气孔口面积/m 2
现有技术 1562.33 1450.88 0.429 0.0025
本申请 1672.75 1594.94 0.4874 0.0027
在相同转子尺寸下，由于该型线的面积利用系数较大，所以其每转一次，其排出的理论容积较大。所以为达到相同的排气量，本申请中的齿形型线的转子转速可以降低。转速降低有助于减少转子间的摩擦损失和吸排气击油损失，从而提高能效。
另外一方面，在变频高转速下，压缩机的排气流量比较大。这个时候，排气孔口的大小，对排气的压力损失的影响就很大(对定频螺杆压缩机而言，由于排气流量较小，排气孔口的大小造成的压力损失并不是影响能效的主要因素)。采用该齿形型线转子结构，使得该转子结构的排气孔口面积较大，有助于降低压缩机的排气压力损失，从而可以提高压缩机能效。
除上述以外，还需要说明的是在本说明书中所谈到的“一个实施例”、“另一个实施例”、“实施例”等，指的是结合该实施例描述的具体特征、结构或者特点包括在本申请概括性描述的至少一个实施例中。在说明书中多个地方出现同种表述不是一定指的是同一个实施例。进一步来说，结合任一实施例描述一个具体特征、结构或者特点时，所要主张的是结合其他实施例来实现这种特征、结构或者特点也落在本发明的范围内。
在上述实施例中，对各个实施例的描述都各有侧重，某个实施例中没有详述的部分，可以参见其他实施例的相关描述。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (12)

  1. 一种螺杆压缩机转子结构，其特征在于，包括：
    阴转子，阴转子包括阴转子本体(10)，所述阴转子本体(10)上设置有多个阴齿部(11)，所述阴转子本体(10)的端面上的相邻两个所述阴齿部(11)的齿顶之间形成齿形型线，所述齿形型线沿逆时针方向依次由弧线段a 1b、包络线bc、弧线段cd、弧线段de、弧线段ea 2、弧线段a 2a 3首尾连接形成，其中，弧线段cd和弧线段de的圆心位于所述齿形型线的两侧。
  2. 根据权利要求1所述的螺杆压缩机转子结构，其特征在于，弧线段cd的参数方程为：
    Figure PCTCN2018120371-appb-100001
    其中，R 2t为阴转子节圆半径；
    ΔR为弧线段cd的圆心与阳转子的齿根之间距离的调整参数；
    R 3为所述齿部(11)的高度；
    t为部分的所述齿形型线上的点与所述阴转子本体(10)的几何中心与所述阳转子的几何中心的连线形成的夹角；
    t 1为弧线段cd的圆心角。
  3. 根据权利要求2所述的螺杆压缩机转子结构，其特征在于，弧线段de的参数方程为：
    Figure PCTCN2018120371-appb-100002
    其中，R 8为弧线段de的圆弧中心参数；
    R 4为弧线段de的半径；
    t 2为弧线段cd的末端上的点至弧线段cd的圆心的连线，与所述阴转子本体(10)的几何中心与所述阳转子的几何中心的连线形成的夹角；
    t 5为弧线段de的圆心角；
    t 8为弧线段cd的圆心角。
  4. 根据权利要求3所述的螺杆压缩机转子结构，其特征在于，弧线段ea 2的参数方程为：
    Figure PCTCN2018120371-appb-100003
    其中，R 5为弧线段ea 2的半径；
    t 3为弧线段ea 2的末端上的点至所述阴转子本体(10)的几何中心的连线，与所述阴转子本体(10)的几何中心与所述阳转子的几何中心的连线形成的夹角；
    t 9为弧线段ea 2的圆心角。
  5. 根据权利要求4所述的螺杆压缩机转子结构，其特征在于，弧线段a 2a 3的参数方程为：
    Figure PCTCN2018120371-appb-100004
    其中，t 0为弧线段ea 2的末端与所述阴转子本体(10)的几何中心的连线，与所述阴转子本体(10)的几何中心与所述阳转子的几何中心的连线形成的夹角。
  6. 根据权利要求5所述的螺杆压缩机转子结构，其特征在于，弧线段a 1b的参数方程为：
    Figure PCTCN2018120371-appb-100005
    其中，R 7为弧线段a 1b的半径；
    t 4为弧线段a 1b的首端上的点与所述阴转子本体(10)的几何中心的连线，与所述阴转子本体(10)的几何中心与所述阳转子的几何中心的连线形成的夹角。
  7. 根据权利要求6所述的螺杆压缩机转子结构，其特征在于，包络线bc的参数方程为：
    Figure PCTCN2018120371-appb-100006
    其中，R 1t为阳转子节圆半径；
    R 6为形成包络线bc的弧线段的半径；
    k＝i+1，i为阴转子的齿数与阳转子的齿数比；
    Figure PCTCN2018120371-appb-100007
    为阳转子的转角；
    A为阴转子与阳转子的中心距。
  8. 根据权利要求1所述的螺杆压缩机转子结构，其特征在于，所述螺杆压缩机转子结构还包括：
    阳转子，所述阳转子的齿部与所述阴转子的齿部相啮合。
  9. 根据权利要求8所述的螺杆压缩机转子结构，其特征在于，当所述阴齿部(11)与所述阳转子的齿部啮合时，该所述阴齿部(11)的弧线段cd的圆心位于所述阴转子的几何中心与所述阳转子的几何中心的连线上。
  10. 根据权利要求8或9所述的螺杆压缩机转子结构，其特征在于，当所述阴齿部(11)与所述阳转子的齿部啮合时，弧线段cd的圆心至所述转子本体(10)的几何中心与所述阳转子的几何中心的连线的距离，小于弧线段de的圆心至所述转子本体(10)的几何中心与所述阳转子的几何中心的连线的距离。
  11. 根据权利要求8所述的螺杆压缩机转子结构，其特征在于，所述阳转子和所述阴转子的面积利用系数为Q，其中，0.429≤Q。
  12. 一种变频螺杆压缩机，包括螺杆压缩机转子结构，其特征在于，螺杆压缩机转子结构为权利要求1至11中任一项所述的螺杆压缩机转子结构。
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