WO2018216916A1

WO2018216916A1 - Rotary compressor

Info

Publication number: WO2018216916A1
Application number: PCT/KR2018/004995
Authority: WO
Inventors: 조국현; 사범동
Original assignee: 엘지전자 주식회사
Priority date: 2017-05-26
Filing date: 2018-04-30
Publication date: 2018-11-29
Also published as: CN110678655A; CN110678655B; KR102339600B1; KR20180129430A

Abstract

The present invention relates to a rotary compressor comprising: a drive motor provided inside a case and a rotation shaft coupled to the drive motor, for delivering rotational force; a first cylinder and a second cylinder each having an open circular center part where a compression area is formed; a first roller and a second roller which rotate in the compression space; a first vane and a second vane for partitioning the compression space of each of the cylinders into a suction chamber and a compression chamber; a main bearing coupled to the top part of the first cylinder and a sub bearing coupled to the bottom part of the second cylinder; and a middle plate provided between the main bearing and the sub bearing, for separating the first cylinder and the second cylinder, wherein the middle plate may have an oil channel formed from a side surface towards the interior and have heat exchange occur due to oil moving along the oil channel.

Description

Rotary compressor

The present invention relates to a hermetic compressor, and to a rotary compressor capable of reducing the temperature of the compression unit.

The compressor is applied to a vapor compression refrigeration cycle device such as a refrigerator or an air conditioner. The compressor may be classified into a rotary type and a reciprocating type according to a method of compressing a refrigerant.

A rotary compressor is a method in which a rolling piston (hereinafter referred to as a roller) changes the volume of the compression space while rotating or pivoting in a cylinder, and a reciprocating compressor changes the volume of the compression space while the roller reciprocates in the cylinder. That's the way.

As a rotary compressor, there is a rotary compressor that compresses a refrigerant by using the rotational force of the electric drive.

In recent years, the rotary compressor is gradually miniaturized and the efficiency thereof is the main goal of technology development. In addition, research has been continuously made to obtain a larger cooling capacity by increasing the variable range of the operating speed of the miniaturized rotary compressor.

The rotary compressor is a compressor in which a roller and a vane contact each other, and the compression space of the cylinder is divided into a suction chamber and a discharge chamber around the vane. In the general rotary compressor, the vane inserted into the cylinder moves linearly while the roller rotates. Accordingly, the suction chamber and the discharge chamber form a compression chamber whose volume (volume) is variable to suck, compress, and discharge the refrigerant. You lose.

The rotary compressor has a vane rotary compressor in which the vane is inserted into the roller, and is rotated with the roller to be drawn out by centrifugal force and back pressure to form a compression space. Recently, the inner circumferential surface of the cylinder has an ellipse or an ellipse and a circle. A vane rotary compressor with a so-called hybrid cylinder, which is formed in a combined shape to reduce friction loss and increases compression efficiency, is also used.

In general, the hermetic compressor is provided with a driving motor for generating a driving force in the inner space of the sealed casing and a compression unit for compressing a fluid by receiving the driving force of the driving motor.

Inside the case, a driving motor and a compression unit are installed to compress and discharge the sucked refrigerant. The drive motor compresses the refrigerant sucked through the compression unit while rotating the rotating shaft.

Since heat is generated during the compression process, the temperature of the compression unit is increased. In this case, since the refrigerant sucked into the compression unit through the accumulator receives heat from the overheated mechanism part and the temperature rises, the specific volume is lowered, resulting in a loss of cold power, resulting in a lower efficiency of the compressor.

Conventionally, in order to limit the temperature rise of the compression unit according to the operation of the compressor, as in Patent Document 1, the oil storage space and the refrigerant discharge space is separated from each other in the sub-bearing, heat exchange while storing oil separately in the internal space of the mechanism part Was used. In this case, however, there is a high possibility that the leakage of the refrigerant occurs between the discharge chamber and the oil storage space, and there is a high possibility that the refrigerant leaks through the discharge chamber.

Accordingly, it is necessary to specify the structure of the compressor that does not leak refrigerant while lowering the temperature of the compression unit according to the driving of the compressor more effectively.

An object of the present invention is to provide a structure of a compressor that can lower the temperature of the rising compression unit in the compressor driving process.

Another object of the present invention is to cool the elevated temperature of the compression unit while exchanging heat with the oil contained in the case.

Another object of the present invention is to reduce the temperature of the elevated compression unit more efficiently while moving the oil contained in the case to the inside of the intermediate plate.

Another object of the present invention is to increase the efficiency of the compressor by reducing the work required to compress the refrigerant by limiting the temperature rise of the sucked refrigerant.

Another object of the present invention is to effectively reduce the temperature around the compression chamber through a simple structural change of the intermediate plate, without affecting the durability of the compression unit or modifying the shape of the cylinder.

In order to achieve the object of the present invention, a rotary compressor according to the present invention includes a drive motor installed inside the case and a rotating shaft coupled to the drive motor to transmit rotational force; A first cylinder and a second cylinder in which a compression space is formed in the center of the opened circle; A first roller and a second roller pivoting the compression space; First and second vanes which divide the compression space of each cylinder into a suction chamber and a compression chamber; A main bearing coupled to an upper portion of the first cylinder, and a sub bearing coupled to a lower portion of the second cylinder; And an intermediate plate disposed between the main bearing and the sub-bearing to separate the first cylinder and the second cylinder, wherein the intermediate plate is formed with an oil flow path formed inwardly from one side thereof and the oil flow path. Heat exchange may be achieved by the oil moving along.

In this case, the oil passage may be formed to penetrate the side of the intermediate plate, one side of the oil passage is formed to overlap with the compression chamber, it is possible to more efficiently absorb the heat generated by the drive of the compressor. .

According to another example related to the present invention, the oil passage may be formed in plural, and each oil passage may be formed in a direction crossing each other.

According to another example related to the present invention, the oil passage may be formed to have a circular cross section, or an inner surface of the oil passage may be formed with a groove having a predetermined shape, and the oil moves along the oil passage; Can be made to increase the contact area.

The rotary compressor having the above structure can be cooled by heat-exchanging the temperature of the compression unit which is raised in the compressor driving process with oil.

In addition, the oil accommodated in the case can exchange heat with the compression unit while moving along the oil flow path formed inside the intermediate plate, thereby limiting the temperature rise of the refrigerant flowing through the accumulator.

In addition, by limiting the temperature rise of the sucked refrigerant, it is possible to reduce the work required during the compression of the refrigerant to increase the efficiency of the compressor.

In addition, the oil channel has a simple structure that penetrates the side of the intermediate plate and is formed to overlap the compression space, thereby effectively lowering the elevated temperature of the compression chamber.

1 is a cross-sectional view showing an internal view of a rotary compressor according to the present invention.

Figure 2 is a perspective view showing the state of the compression unit located inside the rotary compressor.

3 is an exploded view showing each configuration of the compression unit of FIG.

4 is a plan view showing a state in which the compression unit is viewed from above.

5 is a view showing a state in which each oil channel is formed on the intermediate plate.

6A, 6B, and 6C are enlarged views of the inside of each oil passage formed in the intermediate plate.

7A to 7D are views showing various modification examples of the oil flow path formed in the intermediate plate 140.

EMBODIMENT OF THE INVENTION Hereinafter, the hermetic compressor which concerns on this invention is demonstrated in detail with reference to drawings.

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

In the following description of the embodiments disclosed herein, if it is determined that the detailed description of the related known technology may obscure the gist of the embodiments disclosed herein, the detailed description thereof will be omitted.

The accompanying drawings are only for easily understanding the embodiments disclosed in the present specification, and the technical idea disclosed in the present specification is not limited by the accompanying drawings, and all changes and equivalents included in the spirit and technical scope of the present invention are included. It should be understood to include water or substitutes.

1 is a cross-sectional view showing the inside of the rotary compressor 100.

The rotary compressor 100 according to the present invention includes a case 110, a drive motor 120, and a compression unit 130. In addition, the present invention, the two cylinders (133a, 133b) are installed inside the case 110, respectively, to form a different compression space (V), the structure of the so-called twin rotary compressor, the object.

Hereinafter, each configuration constituting the present invention, the case 110 is to form an appearance, made of a cylindrical shape extending in one direction, it may 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 drive motor 120 and the compression unit 130 may be fixedly installed on the inner surface of the intermediate shell 110b, and the upper and

lower shells

110a and 110c are respectively disposed on the upper and lower portions of the intermediate shell 110b. Installed in combination, it limits the external exposure of the components located inside the case 110.

The compression unit 130 is installed inside the case 110. The compression unit 130 serves to compress and discharge the refrigerant, and the

rollers

134a and 134b, the vanes 135, the

cylinders

133a and 133b, the main bearing 131, the sub bearing 132 and the intermediate plate. 140.

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

The stator 121 is fixedly installed in the case 110 and may be mounted on the inner circumferential surface of the cylindrical case 110 by shrinking. For example, the stator 121 may be fixedly installed on the inner circumferential surface of the intermediate shell 110b.

The rotor 122 may be disposed to be 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 by a magnetic field formed between the stator 121 and the rotor 122 to penetrate the center of the rotor 122. The rotational force is transmitted to the rotating shaft 123.

A suction port 114a is installed at one side of the intermediate shell 110b to allow suction of refrigerant to the

cylinders

133a and 133b, and a discharge port 114b is installed at one side of the upper shell 110a to provide a case ( The coolant flows out from the inside of the 110.

The compression unit 130 compresses the sucked refrigerant, and the compressed refrigerant is the first discharge space 137 and the second discharge formed by the

discharge plates

136a and 136b respectively installed at the upper and lower portions of the compression unit 130. After moving to the space 138, it is collected in the space above the case 110 and then moved along the discharge port 114b.

The refrigerant flowing into the cylinder 133a 133b along the suction passage 111 has

rollers

134a and 134b coupled to the eccentric portion 123a of the rotation shaft 123 along the inner circumferential surfaces of the

cylinders

133a and 133b. As it pivots, the refrigerant is compressed and discharged.

Since the friction generated between the components in the compression process and the discharge process increases the temperature of the compression unit 130, the refrigerant sucked into the compression unit 130 via the accumulator 11 is overheated compression unit 130 The heat is raised from the temperature rises. In this case, the specific volume of the refrigerant to be sucked is lowered, thereby causing a loss of cooling force, thereby lowering the efficiency of the compressor.

Accordingly, the rotary compressor 100 according to the present invention forms an oil passage 140a in the intermediate plate 140 which serves to separate the

cylinders

133a and 133b, and the oil is along the oil passage 140a. It is accommodated, and has the effect of lowering the temperature of the compression unit 130 is raised in accordance with the operation of the compressor.

2 is a perspective view showing a state of the compression unit 130 located inside the rotary compressor.

The compression unit 130 installed inside the case 110 compresses the sucked refrigerant and then moves to the upper portion of the inside of the compressor through the

discharge spaces

137 and 138, and then through the discharge port 114b. It is discharged to the outside.

Compression unit 130, the main bearing 131, the sub-bearing 132, the first cylinder 133a, the second cylinder 133b, the intermediate plate 140,

rollers

134a, 134b and vanes 135a, 135) as a configuration.

Each of the

cylinders

133a and 133b is provided at different positions along the rotation shaft 123 and includes a first cylinder 133a and a second cylinder (V) having a compression space V in which a refrigerant is accommodated in an open circular center portion. 133b). The first cylinder 133a and the second cylinder 133b are installed inside the case 110 forming the exterior of the rotary compressor 100, and the refrigerant flowing through the suction passage 111 may be accommodated in the center thereof. The compression space V can be formed.

An intermediate plate 140 is installed between the first cylinder 133a and the second cylinder 133b to separate the compression spaces V formed in the first cylinder 133a and the second cylinder 133b from each other. do.

Inside the

cylinders

133a and 133b,

rollers

134a and 134b which rotate about the rotating shaft 123 and form a compression space V while contacting the inner circumferential surface 133a of the

cylinders

133a and 133b are installed. do. The compression space V compresses the compression space V formed in the

cylinders

133a and 133b together with the

vanes

135a and 135b by the movement of the

rollers

134a and 134b, respectively. The compartment V2 can be partitioned.

The main bearing 131 is coupled to the upper portion of the first cylinder 133a and the sub bearing 132 is coupled to the lower portion of the second cylinder 133b.

The rollers 134a 134b include a first roller 134a installed inside the first cylinder 133a and a second roller 134b installed inside the second cylinder 133b.

Each roller 134a 134b is coupled to the

eccentric portions

123a and 123b of the rotation shaft 123, and the roller 134 rotates together with the rotation shaft 123 in the compression space V to compress the refrigerant. Will form.

The first roller 134a and the second roller 134b move in contact with the inner circumferential surfaces of the first and

second cylinders

133a and 133b, respectively, to form a compression of the refrigerant. That is, the first roller 134a and the second roller 134b will move while forming virtual contact lines P that extend up and down along the inner circumferential surfaces of the first and

second cylinders

133a and 133b, respectively.

Since the first roller 134a and the second roller 134b have rotation centers different from the center of the rotation shaft 123, the first roller 134a and the second roller 134b are formed of the first and second cylinders ( The refrigerant contained can be compressed while pivoting so as to contact the inner circumferential surfaces of 133a and 133b.

Vanes

135a and 135b are installed at one side of each

cylinder

133a and 133b, and

vanes

135a and 135b are drawn out into the compression space V to be in contact with the outer circumferential surfaces of the

rollers

134a and 134b to contact each cylinder 133a. , 133b) divides the compression space V inside the suction chamber V1 and the compression chamber V2, respectively.

The

vanes

135a and 135b include a first vane 135a accommodated in the first cylinder 133a and a second vane 135b accommodated in the second cylinder 133b.

For example, as shown in FIG. 2, the front end (not shown) of the first vane 135a is in contact with the outer circumferential surface of the first roller 134a accommodated in the compression space V of the first cylinder 133a. In addition, the compression space V of the first cylinder 133a can be divided into a suction chamber V1 and a compression chamber V2.

Similarly, the front end portion (not shown) of the second vane 135b is in contact with the outer circumferential surface of the first roller 134a accommodated in the compression space V of the second cylinder 133b, so that the second cylinder 133b Compression space (V) can be partitioned into suction chamber (V1) and compression chamber (V2), respectively.

Protrusion of each

vane

135a, 135b can be made by the pressure or elastic force of the oil formed in the back pressure space (not shown) in which the rear end of each

vane

135a, 135b is located.

The refrigerant flowing in from the suction passage 111 is compressed and then discharged. The compressed refrigerant moves along the discharge holes 133b formed on the inner surfaces of the

cylinders

133a and 133b.

By the movement between the

rollers

134a and 134b and the

cylinders

133a and 133b in the driving process of the compressor, the pressure of the refrigerant contained in the compression chamber V2 will increase. In this compression process, since the temperature of the compression unit 130 is increased, the temperature of the refrigerant flowing into the

overheated cylinders

133a and 133b is increased, so that the specific volume is lowered, thereby causing a loss of cold power.

Thus, the present invention, the oil flow path (140a, 140b) is formed in the intermediate plate 140, by reducing the temperature of the overheated compression unit 130, the temperature rise of the refrigerant flowing into each cylinder (133a, 133b) Can be limited.

The compression unit 130 is configured such that the first cylinder 133a, the second cylinder 133b, and the intermediate plate 140 are positioned between the main bearing 131 and the sub bearing 132, respectively.

The first roller 134a is installed at the first eccentric portion 123a of the rotating shaft 123 to form compression and discharge of the refrigerant while moving along the inner circumferential surface of the first cylinder 133a. Similarly, a second roller 134b is provided at the second eccentric portion 123b of the rotation shaft 123 to form compression and discharge of the refrigerant while moving along the inner circumferential surface of the second cylinder 133b.

In the hermetic compressor according to the present invention,

oil passages

140a and 140b may be formed in the intermediate plate 140 positioned between the first cylinder 133a and the second cylinder 133b.

The oil contained in the case 110 moves along the

oil passages

140a and 140b formed in the intermediate plate 140, thereby forming cooling of the first cylinder 133a and the second cylinder 133b. Since the oil surface of the oil accommodated in the case 110 is formed up to the upper surface of the intermediate plate 140, the oil can be moved along the

oil passages

140a and 140b, and the rotary shaft 123 of the compressor is driven. By rotation, the oil can move more smoothly to the centers of the

oil passages

140a and 140b.

In addition, each of the

oil passages

140a and 140b may be formed to penetrate the side surface of the intermediate plate 140 and may be formed inside the intermediate plate 140. One side of each of the

oil passages

140a and 140b passes through a position overlapping with the compression chambers V2 formed in the

cylinders

133a and 133b to facilitate absorption of heat generated in the compression chamber V2. .

That is, through a simple structural change to form the respective oil flow paths (140a, 140b) to penetrate the side of the intermediate plate 140, without affecting the durability of the compression unit 130, even without a structural change of the cylinder Therefore, the temperature around the compression chamber can be effectively reduced.

FIG. 4 is a view of the compression unit viewed from above, and shows the state of each of the

oil passages

140a and 140b formed in the intermediate plate 140 and the position of the compression unit 130. FIG. 5 shows the intermediate plate 140. Fig. 4 shows the state in which

oil passages

140a and 140b are formed.

As described above, a plurality of

oil passages

140a and 140b may be formed inside the intermediate plate 140, and the

oil passages

140a and 140b may cross each other. have.

In this case, each of the

oil passages

140a and 140b may be positioned to be spaced apart from the discharge refrigerant movement holes 142 through which the refrigerant is discharged.

As shown in FIG. 4, one side of each of the

oil passages

cylinders

133a and 133b, and thus, in the compression chamber V2. It is made to absorb the heat generated sufficiently.

Compression of the refrigerant contained in the compression chamber V2 of the

cylinders

133a and 133b by the relative motion between the

rollers

134a and 134b and the inner circumferential surfaces of the

cylinders

133a and 133b by the rotation of the rotation shaft 123. Since it is made, in order to reduce the temperature of the compression unit 130 by the heat generated at this time, each of the oil passages (140a, 140b) is formed so as to pass through the position overlapping the compression chamber (V2). Thus, the oil moving along each of the

oil passages

140a and 140b exchanges heat with the

overheated cylinders

133a and 133b to allow cooling.

As shown in FIG. 5, each of the

oil passages

140a and 140b may be formed to penetrate the other side from one side of the intermediate plate 140 and may be formed in a direction crossing each other. At this time, each of the

oil passages

140a and 140b is formed to be spaced apart from the bolt fastening hole 141 formed in the intermediate plate 140 and the discharge refrigerant movement hole 142 through which the discharged refrigerant moves. It is possible to prevent the phenomenon of leakage to the outside of the.

6A, 6B, and 6C are enlarged views of the inside of each of the

oil passages

140a and 140b formed in the intermediate plate 140.

As described above, each of the

oil passages

140a and 140b may pass through the side surface of the intermediate plate 140 and may be formed toward the center portion.

In this case, each of the

oil passages

140a and 140b may have various shapes. As shown in Figure 6a, the cross section of each

oil passage

140a, 140b may be made of a circle having a constant diameter. At this time, the diameter of each oil passage (140a, 140b), should be made to have a diameter smaller than the height of the intermediate plate 140, it may be made to have a diameter smaller than approximately 0.4 times the height of the intermediate plate.

In addition, grooves having a predetermined shape may be formed on the inner surfaces of the

oil passages

140a and 140b, for example, on the inner surfaces of the

oil passages

140a and 140b, respectively. A straight groove 143 may be formed along the direction in which the

oil passages

140a and 140b extend. Through this, the contact area between the oil moving along each of the

oil passages

140a and 140b and the inner surface of each of the

oil passages

140a and 140b is enlarged, so that the cooling effect of the heated compression unit 130 is further increased. It becomes possible.

In addition, a spiral groove 144 may be formed on an inner side surface of each of the

oil passages

140a and 140b along an inner side surface of each of the

oil passages

140a and 140b.

The spiral groove 144 may be formed at a set interval along the direction in which the

oil passages

140a and 140b extend, and through this, the contact area with the moving oil is enlarged, thereby increasing heat exchange performance and heating the compression unit. The cooling effect of 130 can be further increased.

7 (a) to 7 (d), which relate to another embodiment of the present invention, are views showing various modifications of the oil flow path formed in the intermediate plate 140.

As described above, the oil channel is formed to penetrate the side of the intermediate plate 140, and in particular, one side of the oil channel is made to overlap with the compression chamber of the cylinder that generates a relatively high heat during the operation of the compressor. .

As shown in (a) and (b) of FIG. 7, each of the

oil passages

140a and 140b may extend toward the center where the rotation shaft 123 is located at different sides of the intermediate plate 140. .

At this time, any one oil passage 140a may not extend to the rotation shaft 123 positioned to be inserted into the center of the intermediate plate 140.

In addition, as shown in (c) of FIG. 7, three

different oil passages

140a, 140b and 140c may be formed in the intermediate plate 140 of FIG. 7c, and FIG. 7d. As shown in FIG. 7, four

different oil passages

140a, 140b, 140c, and 140d may be formed in the intermediate plate 140 of FIG. 7 (d). At this time, each

oil passage

140a, 140b, 140c, 140d is formed along the direction crossing each other.

However, each

oil passage

140a, 140b, 140c should be formed to be spaced apart from the bolt fastening hole 141 formed in the intermediate plate 140 and the discharge refrigerant moving hole 142 for moving the discharged refrigerant. .

As shown in FIG. 7 (d), the plurality of oil passages 140a are formed to overlap each other with the compression chamber V2 that generates high heat during the driving of the compressor, thereby forming heat formed in the compression chamber V2. It can be lowered more effectively, and by reducing the temperature of the overheated compression unit 130, it is possible to obtain the effect of limiting the temperature rise of the refrigerant flowing into each cylinder (133a, 133b).

What has been described above is only embodiments for implementing a rotary compressor according to the present invention, the present invention is not limited to the above embodiments, and do not depart from the gist of the present invention as claimed in the claims below. Anyone skilled in the art to which the present invention pertains within the scope will have the technical idea of the present invention to the extent that various modifications can be made.

The present invention may be variously applied and applied in the field of producing or using a rotary compressor.

Claims

A drive motor installed inside the case and a rotating shaft coupled to the drive motor to transmit rotational force;

A first cylinder and a second cylinder installed at different positions along the rotation axis and having a compression space formed at a central portion of the opened circle;

First and second rollers coupled to the rotating shaft to pivot the compression spaces formed in the respective cylinders;

First and second vanes which divide the compression space of each cylinder into a suction chamber and a compression chamber;

A main bearing coupled to an upper portion of the first cylinder, and a sub bearing coupled to a lower portion of the second cylinder; And

An intermediate plate installed between the main bearing and the sub bearing to separate the first cylinder and the second cylinder;

The intermediate plate, the oil flow path is formed toward the inside from one side, the rotary compressor, characterized in that the heat exchange by the oil moving along the oil flow path.
The method of claim 1,

The oil flow path, the rotary compressor, characterized in that formed to penetrate the side of the intermediate plate.
The method of claim 1,

One side of the oil passage, it is formed so as to overlap with the compression chamber.
The method of claim 1,

The oil channel is composed of a plurality,

Each of the oil passages are formed in a direction crossing each other.
The method of claim 1,

The oil flow path is a rotary compressor, characterized in that the refrigerant is formed to be spaced apart from the discharge hole.
The method of claim 1,

The said oil flow path is a rotary compressor characterized by having a circular cross section.
The method of claim 1,

The inner side of the oil passage, the rotary compressor characterized in that a groove of a predetermined shape is formed.
The method of claim 1,

The inner side of the oil flow path, the rotary compressor, characterized in that a spiral groove is formed.
The method of claim 1,

The inner side of the oil passage, the rotary compressor characterized in that the extending groove is formed along the direction in which the oil passage extends.
The method of claim 1,

The oil flow path, the rotary compressor, characterized in that formed to have a diameter smaller than the height of the intermediate plate.