CN113482923B - Compression assembly, scroll compressor and air conditioner - Google Patents

Abstract

The invention discloses a compression assembly, a scroll compressor and an air conditioner, and relates to the technical field of compressors. The compression assembly includes a movable scroll and a crankshaft, the movable scroll includes a movable scroll, and the outer profile of the movable scroll has a maximum The outer diameter is De, and the tooth height of the moving spiral tooth is h; the crankshaft includes a long shaft part and an eccentric part, and the eccentric part is provided with a first sectional plane, and the reference plane formed by the central axis of the long shaft part and the central axis of the eccentric part is the same as the first tangential plane. The angle between all faces is

The distance between the central axis of the long shaft part and the central axis of the eccentric part is Ror; the angle characteristic parameter of the first section

Eccentricity characteristic parameter of crankshaft H2=Ror ² /(De*h); 0.10≤H1+αH2≤0.22, 8.5≤α≤11.2. In the present invention, the angle characteristic parameter of the first section and the eccentricity characteristic parameter of the crankshaft are designed within an appropriate range, so that the contact force between the movable scroll and the movable scroll is kept relatively small and the corresponding frictional power consumption is relatively small At the same time, the movable scroll and the stationary scroll are not easy to separate and cause leakage, which improves the energy efficiency and reliability of the scroll compressor.

Description

Compression components, scroll compressors and air conditioners

technical field

The present invention relates to the technical field of compressors, in particular to a compression assembly, a scroll compressor and an air conditioner.

Background technique

In the related art, a scroll compressor includes a stationary scroll, a movable scroll and a crankshaft. When the crankshaft drives the movable scroll to move relative to the stationary scroll, multiple compression chambers are formed between the movable scroll and the stationary scroll, and the compression chamber realizes Inhalation, compression and discharge of refrigerant. There is a contact force between the movable scroll and the stationary scroll. When the contact force is too large, the frictional power consumption of the scroll compressor is larger. The pump body leaks, which affects the energy efficiency of the scroll compressor. Therefore, designing an appropriate contact force range is the key to solving the energy efficiency and reliability of the scroll compressor.

SUMMARY OF THE INVENTION

The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a compression assembly, which can ensure the energy efficiency of the scroll compressor and improve the reliability of the scroll compressor.

The present invention also provides a scroll compressor with the above-mentioned compression assembly.

The present invention also provides an air conditioner with the above scroll compressor.

所述长轴部的中心轴线和所述偏心部的中心轴线的距离为Ror；其中，所述第一切面的角度特征参数

所述曲轴的偏心距特征参数H2＝Ror²/(De*h)；所述H1和所述H2满足关系式：0.10≤H1+αH2≤0.22，8.5≤α≤11.2。The compression assembly according to the embodiment of the first aspect of the present invention includes: a movable scroll including a movable scroll, the maximum outer diameter of the outer profile of the movable scroll is De, and the tooth height of the movable scroll is h; A crankshaft includes a long shaft portion and an eccentric portion, the eccentric portion is provided with at least one first tangential plane, and the reference plane formed by the central axis of the long shaft portion and the central axis of the eccentric portion and the first tangential plane The angle between is

The distance between the central axis of the long shaft portion and the central axis of the eccentric portion is Ror; wherein, the angle characteristic parameter of the first section

The characteristic parameter of the eccentricity of the crankshaft is H2=Ror ² /(De*h); the H1 and the H2 satisfy the relationship: 0.10≤H1+αH2≤0.22, 8.5≤α≤11.2.

The compression assembly according to the embodiment of the present invention has at least the following beneficial effects:

曲轴的偏心部的第一切面的角度特征参数

H1越小，压缩组件压缩过程形成的切向气体力在径向的分量减小，导致动涡盘和静涡盘之间的接触力减小，动涡盘和静涡盘容易发生分离而导致泄漏；H1越大，切向气体力在径向的分量增大，动涡盘和静涡盘之间的接触力增大而导致相应的摩擦损失增大；定义曲轴的长轴部的中心轴线和偏心部的中心轴线的距离为Ror，动涡盘的涡齿的外侧型线的最大外径为De，动涡盘的涡齿齿高为h，曲轴的偏心距特征参数H2＝Ror²/(De*h)，H2越小，动涡盘的涡齿齿高h越大，动涡盘和静涡盘的重心越高，容易在压缩组件压缩过程中形成的气体力的作用下发生倾斜而导致泄漏；H2越小，曲轴的长轴部的中心轴线和偏心部的中心轴线的距离Ror越大，动涡盘的转动半径越大，动涡盘和静涡盘之间的摩擦路径变长，摩擦损失增大；设计0.10≤H1+αH2≤0.22，α为常数且满足8.5≤α≤11.2，使得压缩组件的参数H1+αH2位于上述范围内，从而能够兼顾涡旋压缩机的能效和可靠性的要求。By designing the characteristic parameters of the angle of the first section of the eccentric part of the crankshaft and the characteristic parameters of the eccentricity of the crankshaft within an appropriate range, the contact force between the movable scroll and the movable scroll can be kept relatively small and the corresponding friction work can be maintained. At the same time, the movable scroll and the stationary scroll are not easy to separate and cause leakage, which improves the energy efficiency and reliability of the scroll compressor. Specifically, the angle between the reference plane formed by the central axis of the long shaft portion of the crankshaft and the central axis of the eccentric portion and the first tangential plane of the eccentric portion is defined as

Angle characteristic parameters of the first section of the eccentric part of the crankshaft

The smaller H1 is, the smaller the radial component of the tangential gas force formed during the compression process of the compression assembly, the smaller the contact force between the movable scroll and the stationary scroll, and the easier the separation of the movable scroll and stationary scroll. Leakage; the larger H1, the larger the radial component of the tangential gas force, the larger the contact force between the movable scroll and the stationary scroll, and the larger the corresponding friction loss; defines the central axis of the long shaft portion of the crankshaft The distance from the central axis of the eccentric portion is Ror, the maximum outer diameter of the outer profile of the lap of the movable scroll is De, the height of the lap of the movable scroll is h, and the characteristic parameter of the eccentricity of the crankshaft is H2=Ror ² / (De*h), the smaller H2, the greater the tooth height h of the movable scroll, the higher the center of gravity of the movable scroll and the stationary scroll, and it is easy to tilt under the action of the gas force formed during the compression of the compression assembly. And lead to leakage; the smaller H2, the larger the distance Ror between the central axis of the long shaft portion of the crankshaft and the central axis of the eccentric portion, the larger the turning radius of the movable scroll, and the larger the friction path between the movable scroll and the stationary scroll. long, the friction loss increases; the design is 0.10≤H1+αH2≤0.22, α is a constant and satisfies 8.5≤α≤11.2, so that the parameter H1+αH2 of the compression component is within the above range, so that the energy efficiency and reliability requirements.

According to some embodiments of the present invention, the H2 satisfies: 0.0056≤H2≤0.0069.

According to some embodiments of the present invention, the H1 satisfies: 0.033≤H1≤0.056.

According to some embodiments of the present invention, the Ror satisfies: 0<Ror≤1.2mm.

According to some embodiments of the present invention, the α satisfies: α=10.

According to some embodiments of the present invention, the eccentric portion is provided with two of the first cut surfaces, and the two first cut surfaces are arranged in parallel.

According to some embodiments of the present invention, the areas of the two first cut planes are equal.

According to some embodiments of the present invention, the compression assembly further includes a shaft sleeve sleeved with the eccentric portion, and the inner wall surface of the shaft sleeve is provided with two parallel second cut surfaces, the second cut surfaces and the The first facet is a slip fit.

A scroll compressor according to an embodiment of the second aspect of the present invention includes the compression assembly described in the above embodiments.

The scroll compressor according to the embodiment of the present invention has at least the following beneficial effects:

曲轴的偏心部的第一切面的角度特征参数

H1越小，压缩组件压缩过程形成的切向气体力在径向的分量减小，导致动涡盘和静涡盘之间的接触力减小，动涡盘和静涡盘容易发生分离而导致泄漏；H1越大，切向气体力在径向的分量增大，动涡盘和静涡盘之间的接触力增大而导致相应的摩擦损失增大；定义曲轴的长轴部的中心轴线和偏心部的中心轴线的距离为Ror，动涡盘的涡齿的外侧型线的最大外径为De，动涡盘的涡齿齿高为h，曲轴的偏心距特征参数H2＝Ror²/(De*h)，H2越小，动涡盘的涡齿齿高h越大，动涡盘和静涡盘的重心越高，容易在压缩组件压缩过程中形成的气体力的作用下发生倾斜而导致泄漏；H2越小，曲轴的长轴部的中心轴线和偏心部的中心轴线的距离Ror越大，动涡盘的转动半径越大，动涡盘和静涡盘之间的摩擦路径变长，摩擦损失增大；设计0.10≤H1+αH2≤0.22，α为常数且满足8.5≤α≤11.2，使得压缩组件的参数H1+αH2位于上述范围内，从而能够兼顾涡旋压缩机的能效和可靠性的要求。Using the compression assembly of the embodiment of the first aspect, by designing the angle characteristic parameter of the first section of the eccentric portion of the crankshaft and the characteristic parameter of the eccentric distance of the crankshaft in the compression assembly within a suitable range, the compression assembly makes the difference between the movable scroll and the movable scroll. The contact force between them is small and the corresponding frictional power consumption is small. At the same time, the movable scroll and the stationary scroll are not easy to separate and cause leakage, which improves the energy efficiency and reliability of the scroll compressor. Specifically, the angle between the reference plane formed by the central axis of the long shaft portion of the crankshaft and the central axis of the eccentric portion and the first tangential plane of the eccentric portion is defined as

Angle characteristic parameters of the first section of the eccentric part of the crankshaft

The smaller H1 is, the smaller the radial component of the tangential gas force formed during the compression process of the compression assembly, the smaller the contact force between the movable scroll and the stationary scroll, and the easier the separation of the movable scroll and stationary scroll. Leakage; the larger H1, the larger the radial component of the tangential gas force, the larger the contact force between the movable scroll and the stationary scroll, and the larger the corresponding friction loss; defines the central axis of the long shaft portion of the crankshaft The distance from the central axis of the eccentric portion is Ror, the maximum outer diameter of the outer profile of the lap of the movable scroll is De, the height of the lap of the movable scroll is h, and the characteristic parameter of the eccentricity of the crankshaft is H2=Ror ² / (De*h), the smaller H2, the greater the tooth height h of the movable scroll, the higher the center of gravity of the movable scroll and the stationary scroll, and it is easy to tilt under the action of the gas force formed during the compression of the compression assembly. And lead to leakage; the smaller H2, the larger the distance Ror between the central axis of the long shaft portion of the crankshaft and the central axis of the eccentric portion, the larger the turning radius of the movable scroll, and the larger the friction path between the movable scroll and the stationary scroll. long, the friction loss increases; the design is 0.10≤H1+αH2≤0.22, α is a constant and satisfies 8.5≤α≤11.2, so that the parameter H1+αH2 of the compression component is within the above range, so that the energy efficiency and reliability requirements.

An air conditioner according to an embodiment of the third aspect of the present invention includes the scroll compressor described in the above embodiments.

The air conditioner according to the embodiment of the present invention has at least the following beneficial effects:

曲轴的偏心部的第一切面的角度特征参数

H1越小，压缩组件压缩过程形成的切向气体力在径向的分量减小，导致动涡盘和静涡盘之间的接触力减小，动涡盘和静涡盘容易发生分离而导致泄漏；H1越大，切向气体力在径向的分量增大，动涡盘和静涡盘之间的接触力增大而导致相应的摩擦损失增大；定义曲轴的长轴部的中心轴线和偏心部的中心轴线的距离为Ror，动涡盘的涡齿的外侧型线的最大外径为De，动涡盘的涡齿齿高为h，曲轴的偏心距特征参数H2＝Ror²/(De*h)，H2越小，动涡盘的涡齿齿高h越大，动涡盘和静涡盘的重心越高，容易在压缩组件压缩过程中形成的气体力的作用下发生倾斜而导致泄漏；H2越小，曲轴的长轴部的中心轴线和偏心部的中心轴线的距离Ror越大，动涡盘的转动半径越大，动涡盘和静涡盘之间的摩擦路径变长，摩擦损失增大；设计0.10≤H1+αH2≤0.22，α为常数且满足8.5≤α≤11.2，使得压缩组件的参数H1+αH2位于上述范围内，从而能够兼顾涡旋压缩机的能效和可靠性的要求。Using the scroll compressor of the embodiment of the second aspect, the scroll compressor includes a compression assembly, and the compression assembly is designed by designing the angle characteristic parameter of the first section of the eccentric portion of the crankshaft and the characteristic parameter of the eccentric distance of the crankshaft within a suitable range , so that the contact force between the movable scroll and the movable scroll is kept small and the corresponding frictional power consumption is small, and the movable scroll and the stationary scroll are not easy to separate and cause leakage, which improves the energy efficiency of the scroll compressor. and reliability. Specifically, the angle between the reference plane formed by the central axis of the long shaft portion of the crankshaft and the central axis of the eccentric portion and the first tangential plane of the eccentric portion is defined as

Angle characteristic parameters of the first section of the eccentric part of the crankshaft

The smaller H1 is, the smaller the radial component of the tangential gas force formed during the compression process of the compression assembly, the smaller the contact force between the movable scroll and the stationary scroll, and the easier the separation of the movable scroll and stationary scroll. Leakage; the larger H1, the larger the radial component of the tangential gas force, the larger the contact force between the movable scroll and the stationary scroll, and the larger the corresponding friction loss; defines the central axis of the long shaft portion of the crankshaft The distance from the central axis of the eccentric portion is Ror, the maximum outer diameter of the outer profile of the lap of the movable scroll is De, the height of the lap of the movable scroll is h, and the characteristic parameter of the eccentricity of the crankshaft is H2=Ror ² / (De*h), the smaller H2, the greater the tooth height h of the movable scroll, the higher the center of gravity of the movable scroll and the stationary scroll, and it is easy to tilt under the action of the gas force formed during the compression of the compression assembly. And lead to leakage; the smaller H2, the larger the distance Ror between the central axis of the long shaft portion of the crankshaft and the central axis of the eccentric portion, the larger the turning radius of the movable scroll, and the larger the friction path between the movable scroll and the stationary scroll. long, the friction loss increases; the design is 0.10≤H1+αH2≤0.22, α is a constant and satisfies 8.5≤α≤11.2, so that the parameter H1+αH2 of the compression component is within the above range, so that the energy efficiency and reliability requirements.

Additional aspects and advantages of the present invention will be set forth, in part, from the following description, and in part will be apparent from the following description, or may be learned by practice of the invention.

Description of drawings

The present invention will be further described below in conjunction with the accompanying drawings and embodiments, wherein:

1 is a schematic structural diagram of a scroll compressor according to an embodiment of the present invention;

Fig. 2 is an enlarged cross-sectional view of the movable scroll in Fig. 1;

Fig. 3 is the bottom view enlarged view of the movable scroll in Fig. 1;

Figure 4 is an enlarged plan view of the crankshaft in Figure 1;

Figure 5 is an enlarged cross-sectional view of the crankshaft in Figure 1;

6 is a force analysis diagram of a crankshaft in a compression assembly according to an embodiment of the present invention;

FIG. 7 is a relationship diagram of H1+αH2 and COP in a scroll compressor according to an embodiment of the present invention.

Reference number:

housing 100;

main frame 200;

stator 300;

Compression assembly 400; movable scroll 410; movable disk body 411; movable scroll 412; inner profile 4121; outer profile 4122; eccentric sleeve 413; stationary scroll 420;

Crankshaft 500; long shaft portion 510; eccentric portion 520; first cut surface 521;

rotor 600;

Bushing 700; second cut surface 710.

Detailed ways

The following describes in detail the embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary, only used to explain the present invention, and should not be construed as a limitation of the present invention.

In the description of the present invention, it should be understood that the azimuth description, such as the azimuth or positional relationship indicated by upper and lower, is based on the azimuth or positional relationship shown in the accompanying drawings, which is only for the convenience of describing the present invention and simplifying the description. , rather than indicating or implying that the indicated device or element must have a particular orientation, be constructed and operate in a particular orientation, and therefore should not be construed as limiting the invention.

In the description of the present invention, plural refers to two or more. If it is described that the first and the second are only for the purpose of distinguishing technical features, it cannot be understood as indicating or implying relative importance, or indicating the number of the indicated technical features or the order of the indicated technical features. relation.

In the description of the present invention, unless otherwise clearly defined, words such as setting, installation, connection should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above words in the present invention in combination with the specific content of the technical solution.

Referring to FIG. 1 , a scroll compressor according to an embodiment of the present invention includes a casing 100 , a main frame 200 and a stator 300 fixed inside the casing 100 . A compression assembly 400 , a crankshaft 500 and a rotor 600 are also provided inside the casing 100 . The rotor 600 is fixedly connected with the crankshaft 500 , and the rotor 600 cooperates with the stator 300 to drive the crankshaft 500 to rotate. The compression assembly 400 of the embodiment of the present invention includes a movable scroll 410 and a stationary scroll 420 , the stationary scroll 420 is connected to the main frame 200 , the movable scroll 410 is connected to the crankshaft 500 , and the crankshaft 500 drives the movable scroll 410 relative to the stationary scroll 420 During rotation, a compression chamber is formed between the movable scroll 410 and the stationary scroll 420 to compress the refrigerant.

2, it can be understood that the movable scroll 410 includes a movable scroll body 411, a movable scroll tooth 412 and an eccentric sleeve 413, and the movable scroll tooth 412 is fixedly connected to the side of the movable disc body 411 facing the stationary scroll 420, The eccentric sleeve 413 is fixedly connected to the side of the movable disk body 411 away from the stationary scroll 420 . The tooth height of the movable spiral tooth 412 is defined as h.

3 , it can be understood that the movable scroll 412 has an inner profile 4121 and an outer profile 4122, and the inner profile 4121 is the involute of the side of the movable scroll 412 toward the center of the movable scroll 410, The outer profile 4122 is an involute of the side of the movable scroll 412 away from the center of the movable scroll 410 . The maximum outer diameter of the outer profile 4122 of the movable spiral tooth 412 is defined as De, and De can also be understood as the maximum outer diameter of the movable spiral tooth 412 .

定义长轴部510的中心轴线和偏心部520的中心轴线的距离为Ror，Ror也可以理解为曲轴500的偏心距。4 and 5 , it can be understood that the crankshaft 500 includes a long shaft portion 510 and an eccentric portion 520, the eccentric portion 520 is located at the end of the long shaft portion 510 facing the movable scroll 410, and the central axis of the eccentric portion 520 is connected to the long shaft portion 520. The central axes of the shaft portion 510 do not coincide, and the eccentric portion 520 is connected with the eccentric sleeve 413 through the shaft sleeve 700 , thereby driving the movable scroll 410 to rotate. It should be noted that the eccentric portion 520 is formed with at least one first section 521, and the number of the first section 521 is generally set to one or two. The faces 521 are generally arranged parallel to each other. Correspondingly, the inner wall surface of the shaft sleeve 700 is formed with a second cut surface 710 that cooperates with the first cut surface 521 , and the second cut surface 710 cooperates with the first cut surface 521 to realize the transmission between the crankshaft 500 and the shaft sleeve 700 , so that the crankshaft 500 is drivingly connected to the movable scroll 410 . Define the plane formed by the central axis of the long shaft portion 510 and the central axis of the eccentric portion 520 as the reference plane, and the included angle between the reference plane and the first cut plane 521 is

The distance between the central axis of the long shaft portion 510 and the central axis of the eccentric portion 520 is defined as Ror, and Ror can also be understood as the eccentricity of the crankshaft 500 .

因此，设计合适的

数值能够获得合适的接触力。Referring to FIG. 2 to FIG. 6 , in the compression assembly 400 according to an embodiment of the present invention, during the compression process of the compression assembly 400, the pressure difference formed by the gradual increase of the pressure of the compression chamber will form the tangential gas force Ft and the radial gas force Fr, the radial direction refers to the direction of the straight line where the distance between the central axis of the long shaft portion 510 and the central axis of the eccentric portion 520 is located, and the tangential direction refers to the direction perpendicular to the radial direction and to the axial direction of the crankshaft 500 . Referring to FIG. 6 , there is a radial contact force between the movable scroll 410 and the stationary scroll 420 , and the magnitude of the contact force is a determining factor affecting the energy efficiency and reliability of the scroll compressor. The greater the contact force, the tighter the contact between the movable scroll 410 and the stationary scroll 420, and the greater the frictional power consumption; the smaller the contact force, the easier the movable scroll 410 and the stationary scroll 420 are out of contact, resulting in leakage. It can be understood that contact force = centrifugal force Fc - radial gas force Fr + tangential gas force Ft in the radial component, tangential gas force Ft in the radial component = tangential gas force

Therefore, designing a suitable

value to obtain a suitable contact force.

需要说明的是，当

的单位为角度时，π为180度，举例来说，

为30度，H1为1/6；当

的单位为弧度时，π为数值。可以理解的是，H1越小，切向气体力Ft在径向的分量减小，导致动涡盘410和静涡盘420之间的接触力减小，动涡盘410和静涡盘420容易发生分离而导致泄漏；H1越大，切向气体力Ft在径向的分量增大，动涡盘410和静涡盘420之间的接触力增大而导致相应的摩擦损失增大。定义曲轴500的偏心距特征参数H2＝Ror²/(De*h)，H2越小，动涡盘410的涡齿齿高h越大，动涡盘410和静涡盘420的重心越高，容易在压缩组件400压缩过程中形成的气体力的作用下发生倾斜而导致泄漏；H2越小，曲轴500的长轴部510的中心轴线和偏心部520的中心轴线的距离Ror越大，动涡盘410的转动半径越大，动涡盘410和静涡盘420之间的摩擦路径变长，摩擦损失增大。It should be noted that the angle characteristic parameters of the first section 521 of the eccentric portion 520 of the crankshaft 500 are defined

It should be noted that when

When the unit is in degrees, π is 180 degrees, for example,

is 30 degrees, and H1 is 1/6; when

When the unit is radians, π is a numerical value. It can be understood that the smaller H1 is, the smaller the radial component of the tangential gas force Ft is, resulting in the reduction of the contact force between the movable scroll 410 and the stationary scroll 420, and the easier it is for the movable scroll 410 and the stationary scroll 420 Separation occurs, resulting in leakage; the larger H1, the larger the radial component of the tangential gas force Ft, the larger the contact force between the orbiting scroll 410 and the stationary scroll 420, and the corresponding increase in friction loss. Define the eccentricity characteristic parameter H2=Ror ² /(De*h) of the crankshaft 500 , the smaller H2 is, the higher the spiral tooth height h of the movable scroll 410, the higher the center of gravity of the movable scroll 410 and the stationary scroll 420, It is easy to tilt under the action of the gas force formed during the compression process of the compression assembly 400 and cause leakage; the smaller H2, the greater the distance Ror between the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520, and the moving vortex The larger the turning radius of the disk 410 is, the longer the friction path between the movable scroll 410 and the stationary scroll 420 is, and the friction loss increases.

Therefore, by designing the angle parameter of the first section 521 of the eccentric portion 520 of the crankshaft 500 and the characteristic parameter of the eccentric distance of the crankshaft 500 in the compression assembly 400 within an appropriate range, the space between the movable scroll 410 and the movable scroll 410 is The contact force is kept small and the corresponding frictional power consumption is small. Meanwhile, the movable scroll 410 and the stationary scroll 420 are not easily separated from each other to cause leakage, thereby improving the energy efficiency and reliability of the scroll compressor. Specifically, design H1+αH2 in the range of 0.10 to 0.22, where α is a constant and satisfies 8.5≤α≤11.2, α is the amplification factor, α can be set to 10, or 9.8, 10.5, etc. etc., designing α within the above-mentioned range of values can avoid a large difference between the actual values of H1 and H2, so that the compression assembly 400 can comprehensively consider the values of the two parameters H1 and H2 when designing, so that the parameters of the compression assembly 400 can be H1+αH2 is designed within the above range, so as to take into account the requirements of energy efficiency and reliability of the scroll compressor.

It can be understood that, referring to the curve shown in FIG. 7 , it can be seen that the parameter H1+αH2 of the compression assembly 400 has a larger COP value between 0.10 and 0.22, where the COP refers to the working condition of DOE-B energy efficiency level. When the parameter H1+αH2 is less than 0.10, the value of COP gradually decreases as the parameter H1+αH2 becomes smaller; when the parameter H1+αH2 is greater than 0.22, the value of COP gradually decreases as the parameter H1+αH2 becomes larger.

It can be understood that the eccentricity characteristic parameter H2 of the crankshaft 500 is set in the range of 0.0056 to 0.0069. When H2 is less than 0.0056, the center of gravity of the movable scroll 410 and the stationary scroll 420 is relatively high, and it is easy to tilt under the action of the gas force formed during the compression of the compression assembly 400, resulting in leakage, resulting in reduced energy efficiency of the scroll compressor. When H2 is greater than 0.0069, the rotating radius of the movable scroll 410 is larger, the friction path between the movable scroll 410 and the stationary scroll 420 becomes longer, and the friction loss increases, resulting in reduced reliability of the scroll compressor. Therefore, when H2 is set within the above range, the scroll compressor can ensure the energy efficiency and improve the reliability of the scroll compressor. For example, H2 can also be set in the range of 0.0059 to 0.0067.

It can be understood that the angle characteristic parameter H1 of the first section 521 of the eccentric portion 520 of the crankshaft 500 is set in the range of 0.033 to 0.056. When H1 is less than 0.033, the radial component of the tangential gas force Ft is small, resulting in a small contact force between the movable scroll 410 and the stationary scroll 420, and the movable scroll 410 and the stationary scroll 420 are easily separated, resulting in leakage , resulting in a decrease in the energy efficiency of the scroll compressor. When H1 is greater than 0.056, the radial component of the tangential gas force Ft is larger, and the contact force between the movable scroll 410 and the stationary scroll 420 is larger, resulting in increased friction loss between the movable scroll 410 and the stationary scroll 420 , resulting in reduced reliability of the scroll compressor. Therefore, when H1 is set within the above-mentioned range, the scroll compressor can ensure the energy efficiency while improving the reliability of the scroll compressor.

Referring to FIGS. 4 and 5 , it can be understood that the distance Ror between the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520 is greater than 0 and less than or equal to 1.2 mm, which can prevent the Ror from being too large and causing the moving vortex If the rotation radius of the disk 410 is too large, the friction path between the movable scroll 410 and the stationary scroll 420 is too long, and the wear and loss of the scroll compressor is larger. For example, Ror can also be limited to be greater than 0 and less than or equal to 0.7mm.

Referring to FIG. 4 , it can be understood that there are two first cut surfaces 521 of the eccentric portion 520 , and the two first cut surfaces 521 are parallel to each other. Correspondingly, the shaft sleeve 700 also has two parallel first cut surfaces 521 . The two tangent planes 710, the two first tangent planes 521 and the two second tangent planes 710 are matched respectively, which can further improve the transmission performance of the eccentric portion 520 and the shaft sleeve 700, and improve the running stability and reliability of the scroll compressor.

Referring to FIG. 4 , it can be understood that the areas of the two first sectional surfaces 521 are equal, which can make the force on the eccentric portion 520 and the shaft sleeve 700 more uniform during transmission, and the transmission performance is better, which further improves the scroll compressor. operational stability and reliability.

Referring to FIG. 4 , it can be understood that the shaft sleeve 700 is sleeved on the eccentric portion 520 , and the second cut surface 710 is slidably matched with the first cut surface 521 . Therefore, when the scroll compressor encounters liquid hammer or impurities enter, the first section 521 of the crankshaft 500 and the second section 710 of the shaft sleeve 700 are slidably matched so that the eccentricity of the movable scroll 410 can be adjusted. The separation of the movable scroll 410 and the stationary scroll 420 reduces the impact of the stationary scroll 420 and the movable scroll 410, ensures that the stationary scroll 420 and the movable scroll 410 will not be damaged, and improves the operation stability of the scroll compressor and reliability. It can be understood that the second cut surface 710 has a gap with the first cut surface 521, that is, the distance between the two second cut surfaces 710 is greater than the distance between the two first cut surfaces 521. Therefore, under special conditions, the eccentricity The part 520 and the shaft sleeve 700 can slide and offset along the matching direction of the first cut surface 521 and the second cut surface 710 , so as to protect the compression assembly 400 .

曲轴500的偏心部520的第一切面521的角度特征参数

H1越小，压缩组件400压缩过程形成的切向气体力Ft在径向的分量减小，导致动涡盘410和静涡盘420之间的接触力减小，动涡盘410和静涡盘420容易发生分离而导致泄漏；H1越大，切向气体力Ft在径向的分量增大，动涡盘410和静涡盘420之间的接触力增大而导致相应的摩擦损失增大；定义曲轴500的长轴部510的中心轴线和偏心部520的中心轴线的距离为Ror，动涡盘410的涡齿的外侧型线4122的最大外径为De，动涡盘410的涡齿齿高为h，曲轴500的偏心距特征参数H2＝Ror²/(De*h)，H2越小，动涡盘410的涡齿齿高h越大，动涡盘410和静涡盘420的重心越高，容易在压缩组件400压缩过程中形成的气体力的作用下发生倾斜而导致泄漏；H2越小，曲轴500的长轴部510的中心轴线和偏心部520的中心轴线的距离Ror越大，动涡盘410的转动半径越大，动涡盘410和静涡盘420之间的摩擦路径变长，摩擦损失增大；设计0.10≤H1+αH2≤0.22，α为常数且满足8.5≤α≤11.2，使得压缩组件400的参数H1+αH2位于上述范围内，从而能够兼顾涡旋压缩机的能效和可靠性的要求。Referring to FIG. 1 , a scroll compressor according to an embodiment of the present invention includes the compression assembly 400 of the above embodiment. The scroll compressor of the embodiment of the present invention adopts the compression assembly 400 of the embodiment of the first aspect. H2 is designed in an appropriate range, so that a small contact force is maintained between the movable scroll 410 and the movable scroll 410 and the corresponding frictional power consumption is relatively small, and the movable scroll 410 and the stationary scroll 420 are not easily separated and Causes leakage, which improves the energy efficiency and reliability of the scroll compressor. Specifically, the angle between the reference plane formed by the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520 and the first sectional plane 521 of the eccentric portion 520 is defined as

Angular characteristic parameters of the first section 521 of the eccentric portion 520 of the crankshaft 500

The smaller H1 is, the smaller the radial component of the tangential gas force Ft formed during the compression process of the compression assembly 400 is, resulting in a reduction in the contact force between the movable scroll 410 and the stationary scroll 420, and the movable scroll 410 and the stationary scroll 420. 420 is easy to separate and lead to leakage; the larger H1, the greater the radial component of the tangential gas force Ft, and the greater the contact force between the movable scroll 410 and the stationary scroll 420, resulting in an increase in the corresponding friction loss; The distance between the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520 is defined as Ror, the maximum outer diameter of the outer profile 4122 of the spiral tooth of the movable scroll 410 is De, and the spiral tooth of the movable scroll 410 The height is h, and the characteristic parameter of eccentricity of crankshaft 500 is H2=Ror ² /(De*h). The higher the value, the easier it is to tilt under the action of the gas force formed during the compression process of the compression assembly 400 and cause leakage; the smaller H2 is, the greater the distance Ror between the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520 is. , the larger the turning radius of the movable scroll 410, the longer the friction path between the movable scroll 410 and the stationary scroll 420, and the friction loss increases; the design is 0.10≤H1+αH2≤0.22, α is a constant and satisfies 8.5≤α ≤11.2, so that the parameter H1+αH2 of the compression assembly 400 is within the above range, so that the requirements of energy efficiency and reliability of the scroll compressor can be taken into account.

Since the scroll compressor adopts all the technical solutions of the compression assembly 400 of the above-mentioned embodiments, it has at least all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, which will not be repeated here.

曲轴500的偏心部520的第一切面521的角度特征参数

H1越小，压缩组件400压缩过程形成的切向气体力Ft在径向的分量减小，导致动涡盘410和静涡盘420之间的接触力减小，动涡盘410和静涡盘420容易发生分离而导致泄漏；H1越大，切向气体力Ft在径向的分量增大，动涡盘410和静涡盘420之间的接触力增大而导致相应的摩擦损失增大；定义曲轴500的长轴部510的中心轴线和偏心部520的中心轴线的距离为Ror，动涡盘410的涡齿的外侧型线4122的最大外径为De，动涡盘410的涡齿齿高为h，曲轴500的偏心距特征参数H2＝Ror²/(De*h)，H2越小，动涡盘410的涡齿齿高h越大，动涡盘410和静涡盘420的重心越高，容易在压缩组件400压缩过程中形成的气体力的作用下发生倾斜而导致泄漏；H2越小，曲轴500的长轴部510的中心轴线和偏心部520的中心轴线的距离Ror越大，动涡盘410的转动半径越大，动涡盘410和静涡盘420之间的摩擦路径变长，摩擦损失增大；设计0.10≤H1+αH2≤0.22，α为常数且满足8.5≤α≤11.2，使得压缩组件400的参数H1+αH2位于上述范围内，从而能够兼顾涡旋压缩机的能效和可靠性的要求。An air conditioner according to an embodiment of the present invention includes the scroll compressor of the above embodiment. It can be understood that when the air conditioner is a split type air conditioner, such as a wall-mounted air conditioner, a floor type air conditioner, etc., the scroll compressor is generally installed in the outdoor unit of the air conditioner; when the air conditioner is an integral type air conditioner, such as a mobile Air conditioners, window air conditioners, etc., scroll compressors are generally installed on the chassis of the air conditioner. The air conditioner of the embodiment of the present invention adopts the scroll compressor of the embodiment of the second aspect. The scroll compressor includes a compression assembly 400 . The eccentricity characteristic parameter H2 of the crankshaft 500 and the crankshaft 500 is designed in an appropriate range, so that the contact force between the movable scroll 410 and the movable scroll 410 is kept small and the corresponding frictional power consumption is small, while the movable scroll 410 and the static The scroll 420 is not easily separated to cause leakage, which improves the energy efficiency and reliability of the scroll compressor. Specifically, the angle between the reference plane formed by the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520 and the first sectional plane 521 of the eccentric portion 520 is defined as

Angular characteristic parameters of the first section 521 of the eccentric portion 520 of the crankshaft 500

The smaller H1 is, the smaller the radial component of the tangential gas force Ft formed during the compression process of the compression assembly 400 is, resulting in a reduction in the contact force between the movable scroll 410 and the stationary scroll 420, and the movable scroll 410 and the stationary scroll 420. 420 is easy to separate and lead to leakage; the larger H1, the greater the radial component of the tangential gas force Ft, and the greater the contact force between the movable scroll 410 and the stationary scroll 420, resulting in an increase in the corresponding friction loss; The distance between the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520 is defined as Ror, the maximum outer diameter of the outer profile 4122 of the spiral tooth of the movable scroll 410 is De, and the spiral tooth of the movable scroll 410 The height is h, and the characteristic parameter of eccentricity of crankshaft 500 is H2=Ror ² /(De*h). The higher the value, the easier it is to tilt under the action of the gas force formed during the compression process of the compression assembly 400 and cause leakage; the smaller H2 is, the greater the distance Ror between the central axis of the long shaft portion 510 of the crankshaft 500 and the central axis of the eccentric portion 520 is. , the larger the turning radius of the movable scroll 410, the longer the friction path between the movable scroll 410 and the stationary scroll 420, and the friction loss increases; the design is 0.10≤H1+αH2≤0.22, α is a constant and satisfies 8.5≤α ≤11.2, so that the parameter H1+αH2 of the compression assembly 400 is within the above range, so that the requirements of energy efficiency and reliability of the scroll compressor can be taken into account.

The embodiments of the present invention have been described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above-mentioned embodiments, and within the scope of knowledge possessed by those of ordinary skill in the art, various Variety.

Claims (10)

1. A compression assembly, characterized in that it comprises: The movable scroll includes a movable scroll, the maximum outer diameter of the outer profile of the movable scroll is De, and the tooth height of the movable scroll is h; A crankshaft includes a long shaft portion and an eccentric portion, the eccentric portion is provided with at least one first tangential plane, and the reference plane formed by the central axis of the long shaft portion and the central axis of the eccentric portion and the first tangential plane The angle between is

The distance between the central axis of the long shaft portion and the central axis of the eccentric portion is Ror; Wherein, the angle characteristic parameter of the first section

The characteristic parameter of the eccentricity of the crankshaft is H2=Ror ² /(De*h); the H1 and the H2 satisfy the relationship: 0.10≤H1+αH2≤0.22, 8.5≤α≤11.2. 2 . The compression assembly according to claim 1 , wherein the H2 satisfies: 0.0056≤H2≤0.0069. 3 . 3. The compression assembly according to claim 1, wherein the H1 satisfies: 0.033≤H1≤0.056. 4. The compression assembly according to claim 1, wherein the Ror satisfies: 0<Ror≤1.2mm. 5 . The compression assembly according to claim 1 , wherein the α satisfies: α=10. 6 . 6 . The compression assembly according to claim 1 , wherein the eccentric portion is provided with two first cut surfaces, and the two first cut surfaces are arranged in parallel. 7 . 7. The compression assembly according to claim 6, wherein the areas of the two first cut planes are equal. 8 . The compression assembly according to claim 6 , wherein the compression assembly further comprises a shaft sleeve sleeved with the eccentric portion, and the inner wall surface of the shaft sleeve is provided with two parallel second cut surfaces, 9 . The second cut surface is slidably matched with the first cut surface. 9. A scroll compressor, characterized by comprising the compression assembly of any one of claims 1 to 8. 10. An air conditioner, characterized by comprising the scroll compressor of claim 9.

Images