KR20180126301A - Rotary compressor - Google Patents

Abstract

The present invention relates to a rotary compressor which comprises: a driving motor installed in a case; a rotating shaft coupled to the driving motor to transmit a rotating force; a cylinder installed in the case, and having a compression space in which refrigerant is accommodated in a central portion that is circular; a roller coupled to the rotating shaft to compress the sucked refrigerant while turning in the compression space; a main bearing and a sub-bearing individually coupled to upper and lower portions of the cylinder; and a vein dividing the compression space into a suction chamber and a compression chamber while coming in contact with the roller. Moreover, a ratio between a central internal diameter (Da) of the cylinder and a height (Ha) of the cylinder satisfies an equation 1 that is 3.8< Da/Ha < 5.0.

Description

ROTARY COMPRESSOR

The present invention relates to a structure of a rotary compressor capable of increasing the efficiency of a compressor.

The compressor is applied to a vapor compression refrigerating cycle apparatus such as a refrigerator or an air conditioner and can be classified into an indirect suction system and a direct suction system according to a method of sucking refrigerant into a compression chamber.

The indirect suction method is a method in which the refrigerant circulating in the refrigeration cycle is introduced into the compression chamber after being introduced into the inner space of the compressor case. The direct suction type is a method in which the refrigerant is directly sucked into the compression chamber unlike the indirect suction type. The indirect suction system can be called a low pressure compressor and the direct suction system can be called a high pressure compressor.

The low pressure type compressor does not have a separate accumulator since the liquid refrigerant or oil is filtered in the inner space of the compressor case as the refrigerant first flows into the inner space of the case of the compressor. On the contrary, in order to prevent the liquid refrigerant or the oil from flowing into the compression chamber, the high pressure type compressor is usually provided on the suction side rather than the compression chamber.

In addition, the compressor can be divided into a rotary type and a reciprocating type according to a method of compressing a refrigerant.

In a rotary compressor, a volume of a compression space is changed while a rolling piston (hereinafter, referred to as a roller) rotates or revolves in a cylinder, and a reciprocating compressor is a system in which a volume of a compression space is varied while a roller reciprocates in a cylinder Method.

As the rotary compressor, there is a rotary compressor which compresses the refrigerant by using the rotational force of the driving portion.

In recent years, the main goal of the technology development is to gradually miniaturize the rotary compressor and increase its efficiency. Further, studies for obtaining a larger cooling capacity by increasing the variable range of the operation speed of the miniaturized rotary compressor have been continuously carried out.

In the rotary compressor, a drive motor and a compression unit are provided in a case for forming an appearance, and the refrigerant sucked and discharged is discharged. The driving motor compresses the refrigerant sucked through the compression unit while rotating the rotary shaft.

The compression unit includes a cylinder defining a compression space, a roller coupled to the rotary shaft, and a vane for partitioning the compression space into a suction chamber and a compression chamber, respectively.

Inside the cylinder, there is provided a roller which rotates about a rotation axis and forms a plurality of compression spaces together with a vane. The roller forms a compression space while concentrically rotating together with the rotation axis.

The rotary compressor compresses the refrigerant flowing into the space of the cylinder to a certain pressure by the relative movement of the roller and the vane to the suction chamber, and then discharges the refrigerant through the discharge pipe to the refrigeration cycle apparatus.

In a series of operations of the rotary compressor, the friction loss necessarily occurs, and in particular, the efficiency of the compressor is lowered due to the friction loss generated in the compression unit.

In order to reduce the friction loss, it may be considered to reduce the friction area generated between the eccentric portion of the rotary shaft, the cylinder, the roller and the vane through a method of reducing the size of each constitution of the compression unit. However, .

Therefore, it is necessary to study the structure of a rotary compressor capable of securing the compression capacity of the refrigerant while reducing the friction loss generated in the compression process of the refrigerant.

An object of the present invention is to improve the efficiency of a rotary compressor by reducing frictional loss occurring in an eccentric portion.

It is an object of the present invention to provide a structure of a rotary compressor capable of reducing the efficiency of a compressor by reducing a compression capacity of a refrigerant accommodated in a cylinder and securing a compression space.

Another object of the present invention is to provide a structure of a rotary compressor that increases the durability of the cylinder and can reduce the deformation of the cylinder even when driven by the compressor.

According to another aspect of the present invention, there is provided a rotary compressor including: a drive motor installed inside a case; A rotating shaft coupled to the driving motor to transmit rotational force; A cylinder provided inside the case and having a compression space in which a refrigerant is received in a central portion of a circular shape; A roller coupled to the rotary shaft for compressing the refrigerant sucked while rotating in the compression space; A main bearing and a sub bearing coupled to the upper and lower portions of the cylinder, respectively; And a vane for separating the compression space into a suction chamber and a compression chamber while being in contact with the roller, wherein a relation between 3.8 <Da / Ha <5.0 is provided between the inner diameter Da of the center of the cylinder and the height Ha of the cylinder. Is satisfied.

According to another example of the present invention, the height Ha of the cylinder may be 10 mm or more and 12 mm or less.

According to another embodiment of the present invention, the inner diameter Da of the cylinder may be 38 mm or more and 60 mm or less.

According to another embodiment of the present invention, the roller is coupled to the eccentric portion formed on the rotary shaft, and the height of the eccentric portion may be equal to the height of the cylinder.

According to another embodiment of the present invention, the value obtained by dividing the height Ha of the eccentric portion by the length Da 'of the eccentric portion may be 0.4 or less.

According to another embodiment of the present invention, a circular groove is formed on one side of the outer circumferential surface of the roller, and one end of the vane is configured to be movable in a predetermined range by the pivotal movement of the roller, Lt; / RTI &gt;

According to another aspect of the present invention, there is provided a driving apparatus comprising: a driving motor installed inside a case; A rotating shaft coupled to the driving motor to transmit rotational force; A first cylinder and a second cylinder which are provided at different positions along the rotation axis inside the case and form a compression space in which a coolant is received in a central portion of the circular shape; A first roller and a second roller coupled to the rotary shaft for compressing the refrigerant sucked while rotating the compression space formed in each of the cylinders; A main bearing coupled to an upper portion of the first cylinder; a sub bearing coupled to a lower portion of the second cylinder; An intermediate plate installed between the main bearing and the sub-bearing, the intermediate plate separating the first cylinder and the second cylinder; And a vane that divides the compression space into a suction chamber and a compression chamber, respectively, while being in contact with the rollers, wherein a ratio between a center inner diameter (Da) of the first cylinder and a height (Ha) The ratio between the height (Db) and the height (Hb) satisfies a relationship of 3.8 <Da / Ha <5.0.

In the rotary compressor having the above-described structure, by limiting the height of the cylinder within a predetermined range, the efficiency of the rotary compressor can be increased by reducing the friction loss occurring in the eccentric portion.

Further, the ratio of the inner diameter to the height of the cylinder can be set within a predetermined range, so that even if the height of the cylinder is limited, the compression capacity of the refrigerant can be secured and the efficiency of the compressor can be optimized.

Further, since the roller and the vane are integrally formed, and a separate structure for positioning the vane in the cylinder is unnecessary, deformation of the cylinder can be reduced even by driving the compressor.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing an inside view of a rotary compressor. FIG.
Fig. 2 is a perspective view showing a rotation shaft and a compression unit located inside the rotary compressor; Fig.
Fig. 3 is a side view of the cylinder of Fig. 2; Fig.
Figure 4 is a perspective view of the cylinder of Figure 2;
5 is a graph showing the efficiency of the compressor.
6 is a graph showing the relationship between the value obtained by dividing the height of the cylinder by the length of the eccentric portion and the friction loss occurring in the eccentric portion of the rotary shaft.
7 is a perspective view showing a state in which the vane 135 'is integrally coupled to one side of the roller 134'.
8 is a sectional view showing the structure of a rotary compressor showing another embodiment of the present invention.
9 is a view showing a state of a first cylinder and a second cylinder formed in the rotary compressor of Fig. 8;

Hereinafter, a rotary compressor according to the present invention will be described in detail with reference to the drawings.

As used herein, the singular forms "a", "an" and "the" include plural referents unless the context clearly dictates otherwise.

In the following description of the embodiments of the present invention, a detailed description of related arts will be omitted when it is determined that the gist of the embodiments disclosed herein may be obscured.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory and are intended to provide further explanation of the invention as claimed. It should be understood that it includes water and alternatives.

1 is a sectional view showing an inside view of a rotary compressor.

The rotary compressor 100 includes a case 110, a driving motor 120, and a compression unit 130.

The case 110 forms an outer shape and is formed in a cylindrical shape extending along one direction and can be formed along the extending direction of the rotation shaft 123. [

The case 110 is composed of an upper shell 110a, an intermediate shell 110b and a lower shell 110c. The driving motor 120 and the compression unit 130 may be fixedly installed on the inner surface of the middle shell 110b and the upper shell 110a and the lower shell 110c may be respectively installed on the upper and lower portions of the middle shell 110b, Thereby limiting the external exposure of components located and located therein.

A compression unit 130 is installed inside the case 110. The compression unit 130 compresses and discharges the refrigerant and includes a roller 134, a vane 135, a cylinder 133, (131) and a sub-bearing (132).

In addition, a drive motor 120 is installed inside the case 110. The drive motor 120 is located above the compression unit 130 and serves to provide power for compressing the refrigerant. The driving motor 120 includes a stator 121, a rotor 122, and a rotating shaft 123.

The stator 121 is fixed to the inside of the case 110 and may be mounted on the inner circumferential surface of the cylindrical case 110 by a method of heat shrinking. For example, the stator 121 may be fixedly installed on the inner peripheral surface of the intermediate shell 110b.

The rotor 122 is spaced apart from the stator 121 and may be disposed inside the stator 121. When power is applied to the stator 121, the rotor 122 is rotated by a force generated in accordance with the magnetic field formed between the stator 121 and the rotor 122, The rotational force is transmitted to the rotating shaft 123.

A suction port 133a is provided on one side of the intermediate shell 110b and a discharge pipe 114 is provided on one side of the upper shell 110a so that refrigerant can flow out from the inside of the case 110. [

The suction port 133a communicates the suction pipe 113 and the case 110 from an evaporator (not shown) forming a refrigeration cycle, and a discharge port (not shown) is connected to the discharge pipe 114 and the case 110 from a condenser (110).

The compressed refrigerant is compressed from the compression chamber V2 into the first discharge space 137 and the second discharge space 138 respectively by the compression unit 130 installed inside the case 110 And then moves along the discharge pipe 114 after being collected in the upper discharge space part 115 of the case 110. [ Suction and discharge of the refrigerant can be performed inside the cylinder 133 forming the compression space V. [

The refrigerant flowing into the cylinder 133 along the suction flow path 133a is circulated by the roller 134 coupled to the eccentric portion 123a of the rotary shaft 123 while swirling along the inner circumferential surface of the cylinder 133, Compression. The efficiency of the compressor is deteriorated by the friction generated in the compression process.

Accordingly, in the rotary compressor 100 according to the present invention, the ratio of the inner diameter and the height formed in the cylinder 133 is formed within a constant range, so that the frictional loss generated in the compression unit 130 is reduced, Which will be described later.

FIG. 2 is a perspective view showing a state of a rotary shaft 123 and a compression unit 130 located inside the rotary compressor. Hereinafter, a compression process of a refrigerant will be described.

The suction of the refrigerant is performed in the compression unit 130. The compression unit 130 installed inside the case 110 compresses the sucked refrigerant and then moves to the upper side of the compressor through the discharge spaces 137 and 138 and then through the discharge pipe 114 And is moved to the outside.

The compression unit 130 includes a main bearing 131, a sub bearing 132, a cylinder 133, a roller 134, and a vane 135.

The cylinder 133 is installed inside the case 110 forming the outer appearance of the rotary compressor 100 and the compression spaces V1 and V2 accommodating the refrigerant flowing through the suction port 111 are formed at the center. Compression of the sucked refrigerant takes place inside the cylinder 133 forming the compression spaces V1 and V2.

The cylinder 133 is provided with a roller 134 which rotates around the rotation shaft 123 and forms the compression spaces V1 and V2 while contacting the inner peripheral surface 133a of the cylinder. The main bearing 131 is coupled to the upper portion of the cylinder 133 and the sub bearing 132 is coupled to the lower portion of the cylinder 133.

The roller 134 is engaged with the eccentric portion 123a of the rotary shaft 123 and the roller 134 is rotated together with the rotary shaft 123 in the compression spaces V1 and V2 and the inner peripheral surface 133a of the cylinder The refrigerant moves along the inner circumferential surface 133a of the cylinder while contacting with the refrigerant to form the refrigerant. The roller 134 will move while forming a virtual contact line P extending up and down along the inner circumferential surface 133a of the cylinder.

The roller 134 has a rotation center different from the center of the rotation shaft 123 so that the roller 134 rotates to contact the inner circumferential surface 133a of the cylinder and compresses the refrigerant.

A vane 135 is provided at one side of the cylinder 133 and the vane 135 is drawn out into the compression spaces V1 and V2 to be in contact with the outer peripheral surface of the roller 134 to compress the compression spaces V1, V2 into the suction space V1 and the compression space V2. The protrusion of the vane 135 may be caused by the pressure or elastic force of the oil formed in the back pressure space (not shown) where the rear end of the vane 135 is located.

The refrigerant introduced from the suction port 111 will be discharged after being compressed by the movement between the roller 134 and the cylinder 133. The compressed refrigerant moves along the discharge hole 133b formed in the inner surface of the cylinder 133 and then moves to the upper side of the main bearing 131 and the lower side of the sub bearing 132 respectively.

Friction loss due to friction occurs between the roller 134 and the inner circumferential surface of the cylinder 133, which causes the efficiency of the compressor to be reduced. Accordingly, the rotary compressor 100 according to the present invention can reduce the friction loss by positioning the ratio between the inner diameter Da formed at the center of the cylinder 133 and the height Ha of the cylinder 133 within a constant value range. It is possible to secure the capacity of the refrigerant compressed while being compressed.

Fig. 3 is a side view of the cylinder 133 of the rotary compressor 100 according to the present invention, and Fig. 4 is a perspective view showing the state of the cylinder 133. Fig.

The cylinder 133 is installed inside the case 110 and the compression spaces V1 and V2 where the refrigerant flowing through the suction port 111 is accommodated are formed at the center of the circular shape.

When the roller 134 is pivoted along the inner circumferential surface of the cylinder 133, a friction loss is generated.

The ratio of the inner diameter Da of the space portion formed in the central portion of the cylinder 133 of the rotary compressor 100 according to the present invention to the height Ha of the cylinder is in the range of 3.8 to 5.0, It is possible to secure the capacity of the refrigerant accommodated in the space portion of the cylinder 133 even if the height of the cylinder 133 is reduced.

[Equation 1]

3.8 <Da / Ha <5.0

As shown in FIGS. 3 and 4, Da means the inner diameter of the space forming the compression space where the refrigerant is accommodated and compressed, and Ha means the height of the cylinder.

The inner diameter Da of the cylinder 133 is configured to have the relationship of Equation 1 while the height Ha of the cylinder 133 is set to be 10 mm to 12 mm, 133 may have a value between 38 mm and 60 mm.

When the height of the cylinder 133 is reduced, the friction area formed between the roller 133 and the roller 134 is reduced, thereby reducing the friction loss. However, when the height of the cylinder 133 is reduced, the volume of the space formed at the center of the cylinder 133 is reduced, and the capacity of the refrigerant accommodated therein is reduced. Therefore, The inner diameter Da of the cylinder satisfying the relationship and the height Ha of the cylinder.

5 is a graph showing the efficiency of the compressor according to the conventional invention and the present invention.

If the friction area formed between the outer circumferential surface of the roller 134 and the inner circumferential surface of the cylinder 133 caused by the pivotal movement of the roller 134 as the rotation shaft 123 rotates is reduced, .

As shown in FIG. 5, the efficiency of the compressor is maximized in the vicinity of the height of the cylinder 133, and the height of the cylinder 133 is 10 mm or more The friction loss increases as the friction area increases and the efficiency of the compressor decreases. When the height of the cylinder 133 is less than 10 mm, the friction area is reduced. However, since the height of the cylinder 133 is reduced, the cylinder 133 is resistant to deformation due to impact generated when the compressor is driven. The capacity of the refrigerant is limited and the efficiency of the compressor is reduced.

The rotary compressor 100 according to the present invention is configured so that the height Ha of the cylinder 133 has a value of 10 mm to 12 mm so that the rotation of the rotary shaft 123 The inner diameter Da of the cylinder and the height Ha of the cylinder are reduced as shown in Equation 1 while reducing the friction area formed between the outer circumferential surface of the roller 134 and the inner circumferential surface of the cylinder 133, To have a value between 3.8 and 5.0, the efficiency of the compressor can be improved over the conventional capacity by the same capacity standard.

As shown in FIG. 5, the compressor according to the present invention increases the efficiency of the compressor on the same capacity basis as compared with the conventional compressor.

6 is a graph showing the relationship between the value obtained by dividing the height of the cylinder by the length of the eccentric portion 123a and the frictional loss occurring in the eccentric portion 123a of the rotary shaft 123. Fig.

The frictional loss generated in the eccentric portion 123a is minimized when the height Ha of the cylinder is 10 mm and the frictional loss generated in the eccentric portion 123a increases as the length Da 'of the eccentric portion 123a increases. It was confirmed that the friction loss becomes larger.

And the inner diameter of the cylinder of the roller 134 coupled to the eccentric portion 123a is in contact with the inner circumferential surface of the cylinder of the roller 134. As the inner diameter Da of the cylinder becomes larger, the length Da 'of the eccentric portion 123a also increases Will be. However, even if the length Ha of the cylinder increases in the range of 10 mm to 12 mm, the frictional loss occurring in the eccentric portion becomes low even if the length Da 'of the eccentric portion 123a increases. Specifically, the frictional loss of the eccentric portion 123a generated in the compressor having the cylinder inner diameter Da having the value of the cylinder height Ha between 10 mm and 12 mm and satisfying the above- Can be confirmed to have a value between a and b. For example, since the height of the eccentric portion can be made equal to the height Ha of the cylinder, when the value obtained by dividing the height of the eccentric portion by the length Da 'of the eccentric portion is 0.4, the friction loss is about 60 %.

7 shows a compressor according to another embodiment of the present invention in which a vane 135 'is integrally coupled to one side of a roller 134'.

The hinge-type vane 135 'may be provided in the vane insertion groove 135' 'formed on the outer side of the roller 134', and may be integrated with the roller 134 '.

A circular vane insertion groove 135 "is formed in the center of the roller 134 'on the outside of the roller 134', and one end of the vane 135 ' In a circular groove so that movement can be formed.

When the roller 134 'and the vane 135' are integrally formed as a hinge type, a pressure in the back pressure space (for example, (Not shown) need not be formed. Accordingly, even if the height Ha of the cylinder is lowered to have a value between 10 mm and 12 mm, it is not necessary to form a hole for forming the back pressure space, so that the rigidity of the cylinder can be ensured.

8 is a cross-sectional view showing the structure of a rotary compressor 200 according to another embodiment of the present invention. FIG. 9 is a sectional view showing a first cylinder 233 'formed in the rotary compressor 200 of FIG. 8, (233 ").

The rotary compressor 200 includes a case 210, a driving motor 220, and a compression unit 230. The configuration for this is the same as that described above and will be omitted.

However, the rotary compressor 200 of FIG. 8 has a structure of a twin rotary compressor in which refrigerant is compressed in two cylinders, not in a rotary compressor having one cylinder as in FIG.

The compression unit of the rotary compressor 200 includes a roller 234, a vane 235, first and second cylinders 233 and 233, a main bearing 231 and a sub bearing 232, an intermediate plate 239, As shown in FIG.

Unlike the rotary compressor 100 of FIG. 1, the rotary compressor 200 according to the present embodiment is installed at different positions along the rotating shaft 223 inside the case 210, The refrigerant is compressed through the first cylinder 233 'and the second cylinder 233', respectively, each of which has a compression space for compressing the refrigerant.

The first eccentric portion 223a and the second eccentric portion 223b are formed at different positions on the rotary shaft 223. The first eccentric portion 223a is provided with the first roller 234a and the second eccentric portion 223b, The second roller 234b is engaged with the second roller 234b.

The intermediate plate 239 is provided between the main bearing 231 and the sub-bearing 232 and between the first cylinder 233 'and the second cylinder 233 " As shown in FIG. In addition, the refrigerant is introduced through the suction passage 233a formed in the intermediate plate 239 rather than the cylinders 233 'and 233' '.

The refrigerant flowing along the suction passage 233a formed in the intermediate plate 239 is moved to the compression spaces of the first cylinder 233 'and the second cylinder 233' located respectively at the upper and lower positions, The first roller 234a coupled to the first eccentric portion 223a of the rotary shaft 223 rotates along the inner circumferential surface of the first cylinder 233 ' The second roller 234b coupled to the second eccentric portion 223b of the rotary shaft 223 is compressed by the second cylinder 233b in the compression space of the second cylinder 233 " The refrigerant circulates along the inner circumferential surface of the refrigerant pipe 233 "

 In the twin rotary compressor in which the refrigerant is compressed in the two cylinders 233 'and 233' 'as shown in FIG. 8, the efficiency of the compressor is lowered due to the friction generated in the compression process. The loss of efficiency of the compressor due to the loss is greater.

The rotary compressor 200 according to the present invention is characterized in that the ratio of the inner diameter and the height of the circular center portion in which the compression space accommodating the refrigerant formed in each of the first cylinder 233 'and the second cylinder 233 " It is possible to secure the compression capacity of the refrigerant while minimizing the friction loss generated in the compression unit 230. [

As described above, in the rotary compressor 200 according to the present invention, the ratio between the inner diameter Da of the space portion formed at the central portion and the height Ha of the cylinder is set to a value between 3.8 and 5.0 And the capacity of the refrigerant accommodated in the space portion of the cylinder 133 can be secured even if the height of the cylinder 133 is reduced.

[Equation 1]

3.8 <Da / Ha <5.0

As shown in FIGS. 3 and 4, Da means the inner diameter of the space forming the compression space where the refrigerant is accommodated and compressed, and Ha means the height of the cylinder.

In particular, if the inner diameter Da of the cylinder 133 is configured to have the above-mentioned relationship (1) while the height Ha of the first cylinder 233 'is configured to have a value of 10 mm to 12 mm, 233 'may be configured to have a value between 38 mm and 60 mm.

When the height of the first cylinder 233 'is reduced, the friction area formed between the first roller 233a and the first roller 234a is reduced, thereby reducing the friction loss. However, if the height of the first cylinder 233 'is reduced, the volume of the space formed in the central portion of the first cylinder 233' is reduced to reduce the capacity of the refrigerant to be accommodated. 1, and the height Ha of the first cylinder.

5, when the height Ha of the first cylinder 233 'is approximately 10 mm, the frictional loss generated in the first eccentric portion 223a is minimized, and the first eccentric portion 223a The larger the length Da 'of the first eccentric portion 223a is, the larger the frictional loss generated in the first eccentric portion 223a is.

The inner diameter Da of the first cylinder 233 'is smaller than the inner diameter Da of the second cylinder 233' because the first cylinder 233a coupled to the first eccentric portion 223a contacts the inner circumferential surface of the first cylinder 233 ' The length Da 'of the first eccentric portion 223a will also increase. However, even if the length Da of the first eccentric portion 223a increases in the region between 10 mm and 12 mm, the value of the frictional loss generated in the first eccentric portion 223a is lowered will be.

The ratio between the inner diameter Db of the space portion formed at the center of the second cylinder 233 "and the height Hb of the cylinder in the same manner as the above-described first cylinder 233 ' And may be set to have a value between 3.8 and 5.0. The contents and effects of this are the same as those of the first cylinder 233 'described above.

It is to be understood that the present invention is not limited to the above-described embodiments, and that various modifications and changes may be made without departing from the scope of the present invention as defined in the following claims It will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the scope of the present invention.

100, 200: rotary compressor 110, 210: case
121, 221: stator 122, 222: rotor
123, 223: rotating shaft 123a: eccentric portion
130, 230 compression unit 131, 231 main bearing
132, 232: sub-bearing 133: cylinder
134: roller 135: vane
223a: first eccentric portion 223b: second eccentric portion
233 ': first cylinder 233'': second cylinder
234a: first roller 234b: second roller
239: intermediate plate

Claims (7)

A drive motor installed inside the case;
A rotating shaft coupled to the driving motor to transmit rotational force;
A cylinder provided inside the case and having a compression space in which a refrigerant is received in a central portion of a circular shape;
A roller coupled to the rotary shaft for compressing the refrigerant sucked while rotating in the compression space;
A main bearing and a sub bearing coupled to the upper and lower portions of the cylinder, respectively; And
And a vane separating the compression space into a suction chamber and a compression chamber while being in contact with the roller,
Wherein a ratio between a center inner diameter (Da) of the cylinder and a height (Ha) of the cylinder satisfies the following expression (1).
[Equation 1]
3.8 <Da / Ha <5.0 The method according to claim 1,
And the height Ha of the cylinder is 10 mm or more and 12 mm or less. 3. The method of claim 2,
Wherein an inner diameter (Da) of the cylinder is 38 mm or more and 60 mm or less. 3. The method of claim 2,
Wherein the roller is coupled to an eccentric portion formed on the rotary shaft,
Wherein a height of the eccentric portion is equal to a height of the cylinder. 5. The method of claim 4,
And a value obtained by dividing the height of the eccentric portion by the length (Da ') of the eccentric portion is 0.4 or less. The method according to claim 1,
A circular groove is formed on one side of the outer peripheral surface of the roller,
And one end of the vane is positioned in the circular groove so as to be movable within a certain range by the pivoting movement of the roller. A drive motor installed inside the case;
A rotating shaft coupled to the driving motor to transmit rotational force;
A first cylinder and a second cylinder which are provided at different positions along the rotation axis inside the case and form a compression space in which a coolant is received in a central portion of the circular shape;
A first roller and a second roller coupled to the rotary shaft for compressing the refrigerant sucked while rotating the compression space formed in each of the cylinders;
A main bearing coupled to an upper portion of the first cylinder; a sub bearing coupled to a lower portion of the second cylinder;
An intermediate plate installed between the main bearing and the sub-bearing, the intermediate plate separating the first cylinder and the second cylinder; And
And a vane separating the compression space into a suction chamber and a compression chamber while being in contact with the rollers,
The ratio between the inner diameter Da of the central portion of the first cylinder and the height Ha and the ratio between the inner diameter Db of the central portion of the second cylinder and the height Hb satisfy the following relationship: Features a rotary compressor.
&Quot; (2) &quot;
3.8 < (Da / Ha) < 5.0,
3.8 &lt; (Db / Hb) &lt; 5.0

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