KR20150081142A - A rotary compressor - Google Patents

Abstract

The present invention relates to a rotary compressor. A rotary compressor according to an embodiment of the present invention includes a casing having an internal space; a motor formed in the internal space of the case and generating a driving force; a rotary shaft rotating while being joined to the motor; a rolling piston eccentrically rotating according to the rotation of the rotary shaft; a cylinder having a compression space unit wherein the rolling piston is received; a coolant sucking unit joined to the casing and having suction holes sucking a coolant; and a body unit connected to the coolant sucking unit and guiding the coolant sucked by the coolant sucking unit to the compression space unit of the cylinder. The present invention is characterized in that the height of one side of the coolant sucking unit is larger than the height of one side of the body unit.

Description

[0001] A rotary compressor [0001]

The present invention relates to a rotary compressor.

Generally, a compressor is a mechanical device that receives power from an electric motor such as an electric motor or a turbine and compresses air, refrigerant or various other operating gases to increase the pressure. The compressor is used for a household appliance such as a refrigerator and an air conditioner, It is widely used throughout.

Such a compressor is broadly classified into a reciprocating compressor that compresses the refrigerant while linearly reciprocating the piston inside the cylinder so as to form a compression space in which a working gas is sucked and discharged between the piston and the cylinder. A rotary compressor for compressing the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder and a compression space for sucking and discharging the working gas between the roller and the cylinder, a scroll compressor in which a compression space in which an operating gas is sucked and discharged is formed between a fixed scroll and a fixed scroll and the orbiting scroll rotates along the fixed scroll to compress the refrigerant.

The rotary compressor may include a doubled rotary compressor having a plurality of cylinders and operating the plurality of cylinders together, or at least one of the cylinders may be idle.

In the double rotary compressor, an independent suction system for connecting suction pipes to both cylinders is used. A common suction pipe is connected to one of the two cylinders, or an intermediate plate installed between the two cylinders separates the compression space An integrated suction system connecting one common suction line may be applied.

FIG. 1 is a cross-sectional view showing a structure of a double-acting rotary compressor to which a conventional integrated suction system is applied, and FIG. 2 is a sectional view showing a structure of a refrigerant suction unit of the double rotary compressor of FIG.

1 and 2, a conventional rotary compressor 10 is connected to a gas-liquid separator 2. The gas- The gas-liquid separator 2 is provided between the outlet side of the evaporator (not shown) and the inlet side of the rotary compressor 10, and is configured to separate the gas refrigerant in the refrigerant and supply it to the rotary compressor 10.

The rotary compressor 10 is provided with a transmission mechanism 12 for generating a driving force on the upper part of the inner space of the sealed casing 11 and a lower portion (Hereinafter referred to as a first compression section) and a second compression mechanism section 30 (hereinafter referred to as a second compression section) for compressing a refrigerant by a power.

A gas suction pipe 3 for introducing a refrigerant from the gas-liquid separator 2 is provided at one side of the casing 11 and a gas discharge pipe 4 through which compressed refrigerant is discharged is provided at an upper end of the casing 11 Can be installed.

The internal space of the casing 11 is maintained at a high pressure (discharge pressure) by the refrigerant discharged from the first compression unit 20 or the second compression unit 30.

The power transmission mechanism portion 12 is provided with a stator 13 fixed to the inner circumferential surface of the casing 11, a rotor 14 rotatably arranged in the stator 13, And a rotary shaft 15 which is heat-shrinked and rotated together. The transmission mechanism portion 12 may be a constant speed motor or an inverter motor.

The rotary shaft 15 is provided with a shaft portion 16 coupled to the rotor 14 and a first eccentric portion 17 and a second eccentric portion 17 eccentrically disposed on both sides of the lower end portion of the shaft portion 16, 18). The first eccentric portion 17 and the second eccentric portion 18 are arranged symmetrically with a phase difference of about 180 degrees. The first eccentric part 17 and the second eccentric part 18 are rotatably coupled to the first rolling piston 22 and the second rolling piston 32, respectively.

The first compression unit 20 includes a first cylinder 21 formed in an annular shape and installed in the casing 11 to form a first compression space V1, A first rolling piston (22) rotatably coupled to the deep portion (17) and compressing the refrigerant while being swirled in the first compression space (V1), and a second rolling piston A first vane 23 for partitioning the first compression space V1 of the cylinder 21 into a first suction chamber and a first discharge chamber and a first vane spring 24 for elastically supporting one side of the first vane 23, .

The second compression unit 30 includes a second cylinder 31 formed in an annular shape and provided below the first cylinder 21 to form a second compression space V2, A second rolling piston (32) rotatably coupled to the second eccentric part (18) and compressing the refrigerant while being pivoted in the second compression space (V2); and a second rolling piston A second vane 33 for partitioning the second compression space V2 of the second cylinder 31 into a second suction chamber and a second discharge chamber and a second vane spring 33 for elastically supporting one side of the second vane 33 34).

The first cylinder 21 is provided with a first cylinder suction portion 25 for guiding the refrigerant into the first compression space V1. The second cylinder 31 is provided with a second cylinder suction portion 35 for guiding the refrigerant to the second compression space V2.

The first and second cylinder suction units 25 and 35 include a first cylinder 21 and a second cylinder 21 which are in contact with upper and lower ends of the first and second branch flow passages 43 and 44 of the intermediate plate 40, (21) and the second cylinder (31) at a lower edge and an upper surface edge of the first cylinder (31).

The rotary compressor 10 is provided with an upper bearing 48 provided on the upper side of the first cylinder 21 and a lower bearing 49 provided on the lower side of the second cylinder 31, 21 and the second cylinder 31 to form the first and second compression spaces together with the upper and lower bearings 48, 49.

The upper bearing 48 and the lower bearing 49 are each formed in a disk shape, and a through hole through which the rotation shaft 15 passes is formed.

The intermediate plate 40 is provided with a suction hole 41 communicating with the suction port 11a of the casing 11, a suction channel 42 through which the refrigerant sucked through the suction hole 41 flows, A first branched flow path 43 and a second branched flow path 44 branched from the flow path 42 to the first cylinder suction portion 25 and the second cylinder suction portion 35 are included. Here, the inlet 11a of the casing 11 is engaged with the gas suction pipe 3.

The suction hole 41 is formed on an outer circumferential surface of the intermediate plate 40 and the suction passage 42 is formed to extend from the suction hole 41 to a predetermined depth radially inward of the intermediate plate 40 do.

The first branched flow passage 43 and the second branched flow passage 44 are provided at the inner end of the suction flow passage 42 toward the first cylinder suction portion 25 and the second cylinder suction portion 35, , That is, about the centerline of the suction passage 42, about 0 ° to about 90 °, more specifically, about 30 ° to about 60 °.

The rotary compressor 10 is provided with a first discharge valve 48a provided in the upper bearing 48 and through which the refrigerant compressed in the first cylinder 21 is discharged and a second discharge valve 48b provided in the lower bearing 49, And a second discharge valve 49a through which the refrigerant compressed in the second cylinder 31 is discharged.

The rotary compressor (10) is provided with a first discharge muffler (48b) provided above the upper bearing (48) for reducing refrigerant noise discharged through the first discharge valve (48a) And a second discharge muffler 49b provided below the second discharge valve 49 to reduce refrigerant noise discharged through the second discharge valve 49a.

A refrigerant compression process in the conventional rotary compressor 10 will be briefly described.

When the rotor 14 is rotated by applying power to the stator 13 of the transmission mechanism unit 12, the rotation shaft 15 rotates together with the rotor 14, and the rotational force of the transmission mechanism unit 12 To the first compression unit (20) and the second compression unit (30), and the first compression unit (20) and the second compression unit (30) The piston 32 is eccentrically rotated in the first compression space V1 and the second compression space V2.

The first vane 23 and the second vane 33 together with the first and second rolling pistons 22 and 32 form a first compression space having a phase difference of 180 degrees and compress the refrigerant .

The refrigerant is sucked from the gas-liquid separator 2 through the suction hole 41 of the intermediate plate 40 into the suction passage 42 and flows into the first branch passage 43 And is sucked and compressed into the first compression space (V1) of the first cylinder (21) through the first cylinder suction portion (25).

The second compression of the second cylinder 31 having a phase difference of 180 degrees with the first compression space V1 during the compression of the refrigerant in the first compression space V1 of the first cylinder 21, The space V2 performs the suction stroke. That is, while the second cylinder suction portion 35 is communicated with the suction passage 42, the refrigerant in the suction passage 42 flows through the second cylinder suction portion 35 of the second cylinder 31 And sucked and compressed into the second compression space V2.

With respect to such a conventional rotary compressor structure, in recent years, there has been increased interest in a rotary compressor having a compact but high efficiency in accordance with global energy regulations.

In order to realize the structure of the compact rotary compressor, when the height A2 of the intermediate plate 40 is reduced, the height of the suction hole 41 or the suction passage 42 formed in the intermediate plate 40 (A1) is correspondingly reduced.

Here, the height A2 of the intermediate plate 40 may mean the height at which the refrigerant is sucked and the height of the plate body portion. That is, the height of the portion where the refrigerant is sucked and the plate body portion may be equal to each other.

When the size of the suction hole 41 or the suction passage 42 is reduced, the flow rate of the refrigerant is lowered and the flow passage resistance of the refrigerant is increased.

In order to solve this problem, when the height A1 of the suction hole 41 or the suction passage 42 is increased without increasing the height A2 of the intermediate plate 40, The thickness A3 of the intermediate plate 40 formed on the outer side of the intermediate plate 40 becomes thin. If the thickness A3 of the intermediate plate 40 is reduced, the structure may be deformed or broken when the gas suction pipe 3 is assembled to the intermediate plate 40. [

If the height A2 of the intermediate plate 40 and the height A1 of the suction passage 42 are increased together, it is difficult to realize a compact compressor and the volume efficiency is lowered due to the leakage loss generated during the compression process. .

In addition, the interval between the first and second cylinders 21 and 31 is increased by the intermediate plate 40 whose height is increased, and the moment applied to the rotation shaft 15 increases, ) May be largely deformed.

FIG. 3 is a cross-sectional view showing a structure of a double-acting rotary compressor to which a conventional independent suction system is applied, and FIG. 4 is a cross-sectional view illustrating a structure of a refrigerant suction unit of the double rotary compressor of FIG. The structure of the rotary compressor according to FIG. 3 is similar to that of the rotary compressor described with reference to FIG. 1, and therefore, the difference will be mainly described. The description and the reference numerals of FIG. do.

3 and 4, the casing 11 of the rotary compressor 10 is provided with a first suction port 11a and a second suction port 11b. The first suction port 11a is coupled to the first suction pipe 2a extending from the gas-liquid separator 2 and the second suction port 11b is connected to the second suction pipe 2b extending from the gas- .

The rotary compressor (10) includes a first cylinder (21) and a second cylinder (31) which are partitioned by an intermediate plate (40) and each have a refrigerant suction portion.

The first cylinder 21 includes a suction hole 21a formed on the outer circumferential surface thereof for sucking refrigerant and a suction passage 21b extending from the suction hole 21a to the inside of the first cylinder 21 do. The second cylinder 31 includes a suction hole formed on the outer circumferential surface thereof for sucking the refrigerant and a suction passage extending from the suction hole to the inside of the second cylinder 31. The refrigerant suction structure of the first cylinder 21 and the second cylinder 31 is the same, and the refrigerant suction structure of the first cylinder is shown in FIG.

The refrigerant compressed in the first cylinder 21 is discharged through the first discharge valve 48a and passes through the interior of the casing 10 through the first discharge muffler 48b and flows through the gas discharge pipe 4, And is discharged from the compressor (10).

The refrigerant compressed in the second cylinder 31 is discharged through the second discharge valve 49a and reduced in noise through the second discharge muffler 49b. The refrigerant is introduced into the first discharge muffler 48b through a guide passage (not shown) communicated with the first discharge muffler 48b from the inside of the second discharge muffler 49b, Is discharged from the compressor (10) through the inside of the casing (10) through the muffler (48b) and through the gas discharge pipe (4).

When the height B2 of the first cylinder 21 or the second cylinder 31 is reduced in order to realize the structure of a compact rotary compressor with respect to such a conventional rotary compressor structure, Or the height B1 of the suction hole 21a or the suction passage 21b formed in the second cylinder 31 is correspondingly reduced.

When the size of the suction hole 21a or the suction passage 21b is reduced, the flow rate of the refrigerant is lowered and the flow path resistance of the refrigerant is increased.

In order to solve this problem, it is desirable to increase the height B1 of the suction hole 21a or the suction passage 21b without increasing the height B2 of the first cylinder 21 or the second cylinder 31 The thickness B3 of the first cylinder 21 or the second cylinder 31 formed outside the suction passage 21b is reduced. When the thickness B3 of the first cylinder 21 or the second cylinder 31 is reduced, the first suction pipe 2a and the second suction pipe 2b are connected to the first cylinder 21 and the second cylinder 31, There arises a problem that the structure is deformed or broken when assembled to the base 31.

Meanwhile, when the height B2 of the first cylinder 21 or the second cylinder 31 and the height B1 of the suction passage 21b are increased together, it is difficult to implement a compact compressor, Volumetric efficiency may be reduced due to leakage loss.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rotary compressor which is compact and can achieve high efficiency.

A rotary compressor according to an embodiment of the present invention includes: a casing having an inner space; A motor provided in an inner space of the case and generating a driving force; A rotating shaft coupled to the motor and rotating; A rolling piston eccentrically rotated according to the rotation of the rotary shaft; A cylinder having a compression space portion in which the rolling piston is accommodated; A refrigerant suction unit coupled to the casing and having a suction hole for sucking refrigerant; And a body portion communicating with the refrigerant suction portion and guiding the refrigerant sucked in the refrigerant suction portion to the compression space portion of the cylinder, wherein the one direction height of the refrigerant suction portion is formed to be larger than the one- do.

In addition, a plurality of the cylinders are provided, and the refrigerant suction portion is formed on an intermediate plate provided between the plurality of cylinders.

The main body is a plate body of the intermediate plate. The unidirectional height of the main body is a distance between a first surface defining the upper surface of the plate body and a second surface defining the lower surface of the plate body. do.

The refrigerant suction unit includes an outer extension extending upward or downward from the plate body, and the outer extension includes a top surface formed at a higher position than the first surface; And a lower surface portion formed at a lower position than the second surface.

In addition, the intermediate plate includes an inclined surface extending obliquely from the plate body toward the outer extending portion.

The cylinder further includes a cylinder body and a protrusion formed on the cylinder body and extending radially outwardly and formed with a vane hole in which the vane is movably disposed, And the line extending from the central portion C1 forms a first set angle in a clockwise or counterclockwise direction with respect to a line passing through the vane hole.

Further, the refrigerant suction portion is formed in the cylinder.

The body portion is a cylinder body of the cylinder, and the one-directional height of the body portion is a distance between a first surface defining the upper surface of the cylinder body and a second surface defining the lower surface of the cylinder body .

Further, the refrigerant suction portion includes an outer extension extending upward or downward from the cylinder body, and the outer extension includes a top surface formed at a higher position than the first surface; And a lower surface portion formed at a lower position than the second surface.

The one-way height of the refrigerant suction portion is a distance from an upper surface portion of the outer extension portion to the lower surface portion.

In addition, the cylinder includes an inclined surface extending obliquely from the cylinder body toward the outer extension.

The cylinder further includes a cylinder body and a protrusion formed on the cylinder body and extending radially outward from the cylinder body and formed with a vane hole in which the vane is movably disposed, and the coolant suction part is formed on the protrusion.

The one-way height of the refrigerant suction portion may be a sum of a height of the suction passage and an outer thickness of the suction passage. The refrigerant suction portion may include a suction passage through which the refrigerant sucked by the refrigerant suction hole flows, do.

The rotary compressor according to another aspect includes: a casing having an inner space; A motor provided in an inner space of the case and generating a driving force; A rotating shaft coupled to the motor and rotating; A rolling piston eccentrically rotated according to the rotation of the rotary shaft; A plurality of cylinders having a cylinder body in which the rolling piston is housed; An intermediate plate having a plate body provided between the plurality of cylinders; A refrigerant suction portion formed in the plurality of cylinders or the intermediate plate and sucking the refrigerant; And the refrigerant suction portion includes an outer extension extending upward or downward from the cylinder body or the plate body.

Further, the one-directional height of the outer extension is formed to be larger than the one-way height of the cylinder body or the plate body.

According to the present invention, since the size of the refrigerant suction portion provided in the cylinder or the intermediate plate can be relatively large in comparison with the body of the cylinder or the intermediate plate, the suction flow rate of the refrigerant increases, And the efficiency can be improved.

In addition, since the size (height) of the cylinder body or the intermediate plate body can be relatively small, the compressor can be compactly implemented, and the volume efficiency due to refrigerant leakage can be prevented, thereby improving the compressor efficiency.

Further, since the size (height) of the intermediate plate body is small and the distance between the first and second cylinders can be reduced, the moment applied to the rotation shaft is reduced, thereby preventing the rotation shaft from being deformed.

In addition, when the rotation shaft is prevented from being deformed, the diameter of the rotation shaft can be relatively small, thereby reducing the friction area between the rotation shaft and the peripheral structure, thereby improving wear reliability and improving mechanical efficiency.

Further, since the thickness of the cylinder or the intermediate plate at the portion where the refrigerant suction portion is formed can be maintained to be equal to or greater than the predetermined thickness, there is an effect that deformation or breakage of the structure can be prevented when the gas suction pipe is assembled to the cylinder or the intermediate plate.

1 is a cross-sectional view showing a structure of a double rotary compressor to which a conventional integrated suction system is applied.
2 is a cross-sectional view showing the structure of a refrigerant suction unit of the double rotary compressor of FIG.
3 is a cross-sectional view showing a structure of a double rotary compressor to which a conventional independent suction system is applied.
FIG. 4 is a cross-sectional view showing the structure of a refrigerant suction unit of the double rotary compressor of FIG. 3;
5 and 6 are views showing a coupling structure of a cylinder and an intermediate plate according to the first embodiment of the present invention.
7 is a cross-sectional view showing the suction structure of the intermediate plate according to the first embodiment of the present invention.
FIG. 8 is a cross-sectional view illustrating a refrigerant suction structure of an intermediate plate according to a second embodiment of the present invention.
9 and 10 are views showing a coupling structure of a cylinder and a bearing according to a third embodiment of the present invention.
11 is a cross-sectional view illustrating a refrigerant suction structure of a cylinder according to a third embodiment of the present invention.

Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. It is to be understood, however, that the spirit of the invention is not limited to the embodiments shown and that those skilled in the art, upon reading and understanding the spirit of the invention, may easily suggest other embodiments within the scope of the same concept.

FIGS. 5 and 6 are views showing a coupling structure of a cylinder and an intermediate plate according to a first embodiment of the present invention, and FIG. 7 is a sectional view showing a suction structure of an intermediate plate according to the first embodiment of the present invention.

5 to 7 show the structure of a double rotary compressor to which an integrated suction system is applied.

5 to 7, an intermediate plate 200 may be coupled between the first cylinder 100 and the second cylinder according to the first embodiment of the present invention. The intermediate plate 200 is provided with a coolant suction unit 210 for sucking the coolant from the gas-liquid separator 2 (see FIG. 1). The coolant suction unit 210 may be coupled to the casing 11 (see FIG. 1).

5 and 6, the first cylinder 100 is coupled to the upper side of the intermediate plate 200. As shown in FIG. The second cylinder is not shown in the drawing, but may be coupled to the first cylinder 100 under the first cylinder 100 in the same manner as the first cylinder 100 (see FIG. 1).

The first cylinder 100 includes an annular cylinder body 110 having a compression space V1 at the center thereof and a protrusion 120 extending radially outward of the cylinder body 110. The first cylinder body 110 and the protrusion 120 form a predetermined height D1.

The first rolling piston 150 is inserted into the compression space V1. A shaft insertion portion 152 is formed at the center of the first rolling piston 150, through which the rotary shaft 15 (see FIG. 1) is inserted. The first rolling piston 150 may have a substantially annular shape by the shaft inserting portion 152.

The protrusion 120 includes a vane hole 122 in which a vane 125 is disposed so as to be able to contact the outer circumferential surface of the first rolling piston 150. The vane hole 122 includes an elastic member receiving portion 123 in which an elastic member (not shown) is coupled to the vane 125 to provide a restoring force.

The elastic member may be coupled to the casing 11 (see FIG. 1) through a through hole 127 formed in the outer circumferential surface of the protrusion 120. The elastic member may be contracted or restored during the rotation of the first rolling piston 150, and the vane 125 may be moved in the vane hole 122 according to the deformation of the elastic member.

The intermediate plate 200 includes a substantially annular plate body 201 and a refrigerant suction portion 210 extending radially outward from the outer peripheral surface of the body 201. The refrigerant suction portion 210 may have a hollow pipe shape having a suction hole 211 through which the refrigerant can be sucked.

The plate body 201 is coupled to the lower side of the cylinder body 110. The plate body 201 includes a coupling surface 250 coupled to a lower surface of the cylinder body 110. The coupling surface 250 may form an upper surface of the plate body 201.

The refrigerant suction unit 210 is provided with a suction passage 215 extending from the suction hole 211 toward the center of the intermediate plate 200 and a suction passage 215 extending from the suction passage 215 to the first cylinder 100 and the second cylinder 200. [ A first branch flow channel 220 and a second branch flow channel 230 extending in the second cylinder direction.

The refrigerant can be sucked into the compression space V1 through the first branch passage 220 and the first cylinder suction portion 25 (see FIG. 1) of the first cylinder 100. [ The refrigerant can be sucked into the compression space portion V2 of the second cylinder through the second branch passage 230 and the second cylinder suction portion 35 of the second cylinder.

The height H2 of the refrigerant suction part 210 is formed to be larger than the height A2 of the plate body 201. [

Specifically, the plate body 201 includes a first surface 201a defining an upper surface and a second surface 201b defining a lower surface. The height A2 of the plate body 201 can be understood as a distance from the first surface 201a to the second surface 201b.

The refrigerant suction portion 210 includes an outer extension portion 213 extending upward or downward from the plate body 201. Specifically, the outer extension 213 includes a top surface 213a formed at a position higher than the first surface 201a and a bottom surface 213b formed at a position lower than the second surface 201b do.

The outer extension 213 is formed with an inclined surface extending obliquely from the first surface 201a to the upper surface portion 213a or extending obliquely from the second surface 201a to the lower surface portion 213b 214). In the drawing, the inclined surface 214 is shown to be inclined at an angle. Alternatively, the inclined surface 214 may be inclined in a vertical direction.

The height H2 of the refrigerant suction portion 210 may be understood as a distance from the upper surface portion 213a to the lower surface portion 213b.

That is, the refrigerant suction unit 210 is configured such that the diameter of the refrigerant suction unit 210 is increased in the vertical direction from the plate body 201.

The height H2 of the refrigerant suction portion 210 or the outside extension portion 213 is determined by the height H4 of the suction hole 211 or the suction flow passage 215 defining the size of the refrigerant flow, And the outer thickness H3 of the flow path 215. [

Therefore, the following equation can be established.

(1) A2 < H2, (2) A2 < H3 + H4

For example, when the value of H3 is formed to be 2 mm, (3) A2 <H4 + 2 mm can be established.

On the other hand, the H3 value may be equal to or greater than the thickness A3 described in FIG. The H4 value has a value larger than the height A1 described with reference to FIG.

That is, the structure of the plate body 201 and the refrigerant suction portion 210 of FIG. 7 is different from that of the conventional structure (FIG. 2), while the height A2 of the plate body 201 is maintained, 211 or the height H4 of the suction passage 215 is enlarged.

According to such a configuration, due to the expansion of the refrigerant suction portion, the suction flow rate of the refrigerant can be increased and the flow path resistance can be reduced. Since the height of the intermediate plate is not increased, a compact compressor structure can be realized, and the distance between the first and second cylinders is not increased, so that the axial deformation can be prevented.

Meanwhile, when the height of the refrigerant suction portion 210 is relatively increased, the refrigerant suction portion 210 may interfere with the protrusion 120 of the first cylinder 100. Accordingly, the present embodiment is characterized in that the coolant suction part 210 is rotated and disposed clockwise or counterclockwise from the center of the first cylinder 100.

5, a line extending from the central portion C1 of the first cylinder 210 to the coolant suction portion 210 passes through the vane hole 122 from the center portion C1, 1 in a clockwise or counterclockwise direction with respect to a line. Therefore, it is possible to prevent interference between the refrigerant suction unit 210 and the protrusion 120. The center portion C1 may be the center portion of the compression space portion V1 of the first cylinder 210. [

FIG. 8 is a cross-sectional view illustrating a refrigerant suction structure of an intermediate plate according to a second embodiment of the present invention.

8 is characterized in that the height of the plate body 201 is reduced while maintaining the height of the suction hole 211 or the suction passage 215 as compared with the structure of the refrigerant suction structure of the conventional intermediate plate.

In detail, the height of the suction hole 211 or the suction passage 215 is maintained at A1, and the height of the plate body 201 is reduced to H5. That is, the height A2 described in FIG. 2 is formed larger than H5.

According to this configuration, the height of the suction hole 211 or the suction passage 215 can be increased relative to the height of the plate body 201.

In other words, the sum of the height of the refrigerant suction portion 210, that is, the height A1 of the suction hole 211 or the suction passage 215 and the thickness H6 of the suction passage 215, Is formed to be larger than the height H5 of the main body 201.

Then, the following equation can be established.

(1) H5 < A1 + H6

For example, when the value of H6 is formed to be 2 mm, (3) a formula of H5 < A1 + 2 mm may be established. On the other hand, the H6 value may be equal to or greater than the thickness A3 described in FIG.

FIG. 9 and FIG. 10 are views showing a coupling structure of a cylinder and a bearing according to a third embodiment of the present invention, and FIG. 11 is a cross-sectional view illustrating a refrigerant suction structure of a cylinder according to a third embodiment of the present invention.

9 to 11 show the structure of a double rotary compressor to which an independent suction system is applied.

9 to 11, the upper bearing 400 may be coupled to the upper side of the first cylinder 300 according to the third embodiment of the present invention. The first cylinder 300 is provided with a coolant suction unit 350 for sucking the coolant from the gas-liquid separator 2 (see FIG. 1). The refrigerant suction unit 350 may be coupled to the casing 11 (see FIG. 1).

9, only the coupling structure of the first cylinder 300 and the upper bearing 400 is shown, but the spirit of the present invention can be similarly applied to the coupling structure of the second cylinder and the lower bearing (see FIG. 3) . That is, the structure of the refrigerant suction portion, which will be described below, can be equally applied to the second cylinder.

The upper bearing 400 includes a shaft insertion portion 410 formed at a substantially central portion thereof to receive a rotation shaft and a discharge valve 420 selectively opened to discharge refrigerant compressed in the first cylinder 300 .

The first cylinder 300 includes an annular cylinder body 310 having a compression space at a central portion thereof and a protrusion 320 extending radially outwardly of the cylinder body 310. The first cylinder body 310 and the protrusion 320 form a predetermined height B2 (see FIG. 4) except for a portion where the coolant suction portion 350 is provided.

The protruding portion 320 includes a vane hole 322 in which a vane is disposed so as to be able to contact the outer circumferential surface of the first rolling piston. In the vane hole 322, an elastic member coupled to the vane and providing a restoring force is disposed. The elastic member may be coupled to the casing 11 (see FIG. 1) through a through hole 327 formed in the outer peripheral surface of the protrusion 320.

The refrigerant suction unit 350 may be formed on the protrusion 320. A suction hole 351 for sucking refrigerant from the gas-liquid separator 2 is formed at an end of the refrigerant suction portion 350. A suction passage 352 for guiding the flow of the refrigerant introduced from the suction hole 351 is formed in the refrigerant suction portion 350. The suction passage 352 may extend from the suction hole 351 toward the center of the first cylinder 300.

The refrigerant suction unit 350 may be disposed at a position that rotates the vane hole 322 clockwise or counterclockwise with respect to the central portion C2 of the first cylinder 300. [

A line extending from the central portion C2 to the center of the coolant suction portion 350 or the suction hole 351 is formed so that a line passing through the vane hole 322 from the center portion C2 1 in the clockwise direction.

The height H7 of the refrigerant suction portion 350 is formed to be greater than a height B2 of the cylinder body 310 or a height B2 of the protrusion 320 excluding the refrigerant suction portion 350 .

In detail, the cylinder body 310 includes a first surface 310a defining an upper surface and a second surface 310b defining a lower surface. The height B2 of the cylinder body 310 can be understood as a distance from the first surface 310a to the second surface 310b.

The refrigerant suction portion 350 includes an outer extension portion 353 extending upward and downward from the cylinder body 310. The outer extension 353 includes an upper surface portion 353a formed at a position higher than the first surface 310a and a lower surface portion 353b formed at a lower position than the second surface 310b do.

The outer extension 353 is formed with an inclined surface extending obliquely from the first surface 310a to the upper surface portion 353a or extending obliquely from the second surface 310a to the lower surface 353b 354).

The height H7 of the refrigerant suction portion 210 can be understood as a distance from the upper surface portion 353a to the lower surface portion 353b.

That is, the coolant suction unit 350 is configured to expand in diameter in the vertical direction from the cylinder body 310.

The height H7 of the refrigerant suction portion 350 is set to be smaller than the height H8 of the suction hole 351 or the suction passage 352 defining the size of the refrigerant to flow, H9).

Therefore, the following equation can be established.

(1) B2 < H7, (2) B2 < H8 + H9

For example, when the value of H9 is formed to be 2 mm, (3) A2 <H8 + 2 mm can be established.

On the other hand, the H9 value may be equal to or greater than the thickness B3 described in FIG. The H8 value has a value larger than the height B1 described in Fig.

That is, the structure of the cylinder body 310 and the refrigerant suction portion 350 of Fig. 11 is different from that of the conventional structure (Fig. 4), while the height B2 of the cylinder body 310 is maintained, 351 or the height H8 of the suction passage 352 is enlarged.

According to such a configuration, due to the expansion of the refrigerant suction portion, the suction flow rate of the refrigerant can be increased and the flow path resistance can be reduced. Since the height of the intermediate plate is not increased, a compact compressor structure can be realized, and the distance between the first and second cylinders is not increased, so that the axial deformation can be prevented.

Other embodiments are suggested.

In the third embodiment, the height H8 of the suction hole 351 or the suction passage 352 is enlarged while the height B2 of the cylinder body 310 is maintained.

However, in comparison with the conventional structure (FIG. 4), the height of the cylinder body can be reduced while the height B1 of the suction hole or the suction passage is maintained. In this case, the height of the suction hole or the suction passage may be increased relative to the height of the cylinder body.

In summary, the height of the refrigerant suction portion is larger than the height of the plate body or the cylinder body. For convenience of explanation, the plate body or the cylinder main body is collectively referred to as a "main body portion ". The main body part can be understood as a structure for guiding the refrigerant sucked through the refrigerant suction part to the compression space part of the cylinder.

10: rotary compressor 11: casing
15: rotation shaft 20: first compression mechanism
30: second compression mechanism section V1, V2: compression space
100: first cylinder 110: cylinder body
120: protrusion 150: first rolling piston
200: intermediate plate 210: refrigerant suction part
211: Suction hole 213: Outer extension
214: slope surface 215: suction path
300: first cylinder 310: cylinder body
350: refrigerant suction portion 351: suction hole
352: Suction flow path 353: Outside extension
354:

Claims (15)

A casing having an internal space;
A motor provided in an inner space of the case and generating a driving force;
A rotating shaft coupled to the motor and rotating;
A rolling piston eccentrically rotated according to the rotation of the rotary shaft;
A cylinder having a compression space portion in which the rolling piston is accommodated;
A refrigerant suction unit coupled to the casing and having a suction hole for sucking refrigerant; And
A main body part communicating with the refrigerant suction part and guiding the refrigerant sucked in the refrigerant suction part to the compression space part of the cylinder,
Wherein the one-way height of the refrigerant suction portion is larger than the one-directional height of the main body portion. The method according to claim 1,
A plurality of the cylinders are provided,
And the refrigerant suction portion is formed on an intermediate plate provided between the plurality of cylinders. 3. The method of claim 2,
Wherein the main body portion is a plate body of the intermediate plate,
Wherein the unidirectional height of the main body portion is a distance between a first surface defining an upper surface of the plate body and a second surface defining a lower surface of the plate body. The method of claim 3,
In the refrigerant suction portion,
And an outer extending portion extending upward or downward from the plate main body,
An upper surface portion formed at a higher position than the first surface; And
And a lower surface portion formed at a lower position than the second surface. 5. The method of claim 4,
In the intermediate plate,
And an inclined surface extending obliquely from the plate body toward the outer extension. 3. The method of claim 2,
Wherein the cylinder includes a cylinder body and a protrusion extending radially outward from the cylinder body and formed with a vane hole in which the vane is movably disposed,
A line extending from the central portion C1 of the compression space portion of the cylinder to the coolant suction portion is formed so as to form a first set angle in a clockwise or counterclockwise direction with respect to a line passing through the vane hole from the central portion C1 Features a rotary compressor. The method according to claim 1,
And the refrigerant suction portion is formed in the cylinder. 8. The method of claim 7,
Wherein the main body portion is a cylinder body of the cylinder,
Wherein the one-way height of the main body is a distance between a first surface defining the upper surface of the cylinder body and a second surface defining the lower surface of the cylinder body. 9. The method of claim 8,
In the refrigerant suction portion,
And an outer extending portion extending upward or downward from the cylinder main body,
An upper surface portion formed at a higher position than the first surface; And
And a lower surface portion formed at a lower position than the second surface. 10. The method according to claim 4 or 9,
Wherein the unidirectional height of the refrigerant suction portion is a distance from an upper surface portion of the outer extending portion to the lower surface portion. 10. The method of claim 9,
In the cylinder,
And an inclined surface extending obliquely from the cylinder body toward the outer extension. 8. The method of claim 7,
Wherein the cylinder includes a cylinder body and a protrusion extending radially outward from the cylinder body and formed with a vane hole in which the vane is movably disposed,
And the refrigerant suction portion is formed on the protrusion. The method according to claim 1,
The refrigerant suction portion includes a suction flow path through which the refrigerant sucked in the refrigerant suction hole flows,
Wherein the unidirectional height of the refrigerant suction portion is a sum of a height of the suction passage and an outer thickness of the suction passage. A casing having an internal space;
A motor provided in an inner space of the case and generating a driving force;
A rotating shaft coupled to the motor and rotating;
A rolling piston eccentrically rotated according to the rotation of the rotary shaft;
A plurality of cylinders having a cylinder body in which the rolling piston is housed;
An intermediate plate having a plate body provided between the plurality of cylinders;
A refrigerant suction portion formed in the plurality of cylinders or the intermediate plate and sucking the refrigerant; And
In the refrigerant suction portion,
And an outer extension extending upward or downward from the cylinder body or the plate body. 15. The method of claim 14,
The one-
Wherein the valve body is formed to be larger than the one-way height of the cylinder body or the plate body.

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