KR101337109B1 - Two stage rotary compressor - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor, and more particularly, to a rotary two-stage compressor capable of preventing refrigerant leakage even when a refrigerant inlet pipe through which a refrigerant in a low pressure state is introduced is provided in a sealed container under high pressure.

In the rotary two-stage compressor according to the present invention, the low pressure compression assembly and the high pressure compression assembly are installed inside the high pressure sealed container, and the refrigerant inlet pipe is connected to the low pressure compression assembly through the sealed container so that the low pressure refrigerant flows therein. And a member such as a welded portion, a sealed tube, and the like, capable of sealingly fixing the refrigerant inlet tube to the sealed container and the low pressure compression assembly.

Description

[0002] TWO STAGE ROTARY COMPRESSOR [0003]

1 is a view showing an example of a conventional rotary twin compressor.

2 is a view showing an example of a conventional rotary two-stage compressor.

Figure 3 is a schematic diagram showing an example of a cycle comprising a rotary two-stage compressor according to the present invention.

4 is a view showing an example of a rotary two-stage compressor according to the present invention.

5 is a view showing an example of a low pressure compression assembly of a rotary two-stage compressor according to the present invention.

6 and 7 are a view of a portion of the rotary two stage compressor according to the present invention from above and below.

8 is a view showing a part of the rotary two-stage compressor according to the present invention cut away.

9 is a view showing an example of a rotary shaft of a rotary two-stage compressor according to the present invention.

10 is a view showing an example of the installation structure of the refrigerant inlet pipe in the rotary two-stage compressor according to the present invention.

11 is a view showing a part of the structure before the refrigerant inlet pipe is installed in the rotary two-stage compressor according to the present invention.

12 is a graph showing the input power according to the flow path diameter of the rotary two-stage compressor according to the present invention.

DESCRIPTION OF THE REFERENCE NUMERALS

100: rotary compressor 101: airtight container

120: low pressure compression assembly 130: high pressure compression assembly

140: intermediate plate 151: refrigerant inlet pipe

152: refrigerant outlet pipe 153: injection pipe

201: sealed appearance 202: sealed inner tube

203: weld

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor, and more particularly, to a rotary compressor capable of preventing leakage of a refrigerant even when a refrigerant inlet tube through which a refrigerant in a low pressure state is introduced is provided in a sealed container under high pressure.

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

These compressors can be classified into reciprocating compressors for compressing refrigerant while linearly reciprocating inside the cylinders by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder. And a rotary compressor for compressing the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder to form a compression space in which the working gas is sucked and discharged between the roller and the cylinder which are eccentrically rotated. And a scroll compressor for compressing the refrigerant while the turning scroll is rotated along the fixed scroll to form a compressed space in which the working gas is sucked and discharged between the orbiting scroll and the fixed scroll. Divided into

In particular, a rotary compressor includes two rollers and two cylinders at the top and bottom, a rotary twin compressor for compressing the rest of the total compression capacity of the upper and lower rollers and cylinder pairs, A pair of rollers and two cylinders, two cylinders communicating, one pair compressing a relatively low-pressure refrigerant, and the other pair compressing a relatively high-pressure refrigerant after the low- Compressors and the like.

Korean Patent Publication No. 1994-0001355 discloses a rotary compressor. An electric motor is located inside the shell, and a rotating shaft is installed so as to pass through the electric motor. Further, a cylinder is located in the lower portion of the electric motor, and an eccentric portion fitted in the rotary shaft and a roller fitted in the eccentric portion are located inside the cylinder. The cylinder is provided with a coolant discharge hole and a coolant inflow hole, and a vane is provided between the coolant discharge hole and the coolant inflow hole so as not to mix with the high-pressure coolant compressed by the low-pressure coolant. Also, a spring is provided at one end of the vane in order to maintain the eccentrically rotating roller and the vane in contact with each other. When the rotating shaft is rotated by the electric motor, the eccentric portion and the roller rotate along the inner circumference of the cylinder to compress the refrigerant gas, and the compressed refrigerant gas is discharged through the refrigerant discharge hole.

Korean Patent Publication No. 10-2005-0062995 discloses a rotary twin compressor. Referring to FIG. 1, two cylinders 1035 and 1045 and an intermediate plate 1030 which compress the same capacity are provided, and the compression capacity is improved by twice compared to the first stage compressor.

Republic of Korea Patent Publication No. 10-2007-0009958 discloses a rotary two-stage compressor. Referring to FIG. 2, the compressor 2001 includes an electric motor 2014 having a stator 2007 and a rotor 2008 above an inside of a sealed container 2013, and two rotary shafts 2002 connected to the electric motor are provided. Eccentricity is provided. The main bearing 2009, the high pressure compression element 2020b, the intermediate plate 2015, the low pressure compression element 2020a and the sub bearing 2019 are laminated in order from the electric motor 2014 side with respect to the rotating shaft 2002. . Also disclosed is an intermediate tube 2040 for introducing refrigerant compressed in the low pressure compression element 2020a into the high pressure compression element 2020b.

However, the rotary two-stage compressor according to the prior art has a high pressure state inside the sealed container because the refrigerant inlet pipe for introducing the refrigerant into the low pressure compression element passes through the sealed container and is inserted into the low pressure compression element and is merely brazed. On the other hand, as the inside of the refrigerant inlet pipe and the compression element for the low pressure maintains the low pressure state, there is a problem that the leakage of refrigerant due to the sudden pressure difference is likely to occur.

In addition, in the rotary two-stage compressor according to the prior art, the refrigerant introduced through the refrigerant inlet tube is compressed in the low pressure compression element, and then passes through the intermediate tube in communication with each other outside the low pressure compression element and the high pressure compression element. It is difficult to reduce the flow path resistance of the refrigerant as the flow path of the intermediate pipe is increased because the flow path of the intermediate pipe is increased because the flow path of the intermediate pipe is increased, and the size and installation space of the intermediate pipe are limited in the sealed container. Therefore, there is a problem in that the compression efficiency is reduced.

The present invention has been made in order to solve the above problems of the prior art, a rotary type that can be installed so as to be sealed even if the refrigerant inlet pipe through which the refrigerant in the low pressure flows through the sealed container in the high pressure state to prevent leakage of the refrigerant The purpose is to provide a two-stage compressor.

Another object of the present invention is to provide a rotary two-stage compressor having an internal flow path between a low pressure compression assembly in which a refrigerant is compressed and a high pressure compression assembly in which a refrigerant is compressed. There is this.

One embodiment of the present invention for solving the above problems is a closed container in a high pressure state; A rotating shaft provided in the sealed container and transmitting a rotational force; A low pressure compression assembly in which primary compression of the refrigerant is performed inside the low pressure cylinder according to the rotation of the rotary shaft; A high pressure compression assembly in which secondary compression of the refrigerant compressed first in the high pressure cylinder is performed according to the rotation of the rotary shaft; A refrigerant inlet pipe which is fixed to the low pressure cylinder to penetrate the sealed container, and supplies the refrigerant to the low pressure compression assembly; And, it is provided between the sealed container and the low pressure cylinder and the refrigerant inlet pipe, and means for tightly fixing the refrigerant inlet pipe to the sealed container and the low pressure cylinder; provides a rotary two-stage compressor comprising a.

In addition, the means provides a rotary two-stage compressor, characterized in that the welding portion welded between the through-hole of the sealed container and the outer diameter of the refrigerant inlet pipe.

In addition, the welding unit provides a rotary two-stage compressor, characterized in that provided on the outside of the sealed container.

In addition, the means provides a rotary two-stage compressor, characterized in that at least two or more sealed pipes interposed between the low pressure inlet hole of the low pressure cylinder and the outer diameter of the refrigerant inlet pipe.

In addition, the sealing tube provides a rotary two-stage compressor, characterized in that installed in different materials overlapping in the radial direction.

In addition, the low pressure inlet hole of the low pressure cylinder provides a rotary two-stage compressor characterized in that the step is formed so that the diameter becomes smaller from the outer diameter to the inner diameter of the low pressure cylinder.

In addition, the intermediate plate partitioning between the low pressure cylinder and the high pressure cylinder; An intermediate pressure chamber in communication with the low pressure compression assembly and the high pressure compression assembly, wherein the refrigerant discharged from the low pressure compression assembly passes before the high pressure compression assembly is introduced; And an internal flow path through which the refrigerant flows by an intermediate pressure communication hole formed in the intermediate pressure chamber, the low pressure cylinder, the intermediate plate, and the high pressure cylinder, respectively, wherein the internal diameter of the refrigerant inlet pipe is larger than the internal diameter of the internal flow path. Provides a rotary two stage compressor.

In addition, the inner diameter of the refrigerant inlet pipe provides a rotary two-stage compressor, characterized in that formed larger than 2.2 times less than the inner diameter of the inner passage.

On the other hand, another embodiment according to the present invention is a closed container in a high pressure state; A rotating shaft provided in the sealed container and transmitting a rotational force; A low pressure compression assembly in which primary compression of the refrigerant is performed inside the low pressure cylinder according to the rotation of the rotary shaft; A high pressure compression assembly in which secondary compression of the refrigerant compressed first in the high pressure cylinder is performed according to the rotation of the rotary shaft; A refrigerant inlet pipe which is fixed to the low pressure cylinder to penetrate the sealed container, and supplies the refrigerant to the low pressure compression assembly; An intermediate plate partitioning between the low pressure cylinder and the high pressure cylinder; An intermediate pressure chamber in communication with the low pressure compression assembly and the high pressure compression assembly, wherein the refrigerant discharged from the low pressure compression assembly passes before the high pressure compression assembly is introduced; And an internal flow path formed by the intermediate pressure communication hole formed in the intermediate pressure chamber, the low pressure cylinder, the intermediate plate, and the high pressure cylinder, and having an inner diameter larger than that of the refrigerant inlet pipe. Provides only a compressor.

In addition, the rotary container is provided between the low-pressure cylinder and the refrigerant inlet tube, the refrigerant inlet tube is provided in close contact with the low-pressure cylinder and the container; provides a rotary two-stage compressor further comprises.

In addition, the means for welding the weld between the through-hole of the sealed container and the outer diameter of the refrigerant inlet pipe; And at least two or more sealing tubes interposed between the low pressure inlet of the low pressure cylinder and the outer diameter of the refrigerant inlet tube.

In addition, the low pressure inlet hole of the low pressure cylinder provides a rotary two-stage compressor characterized in that the step is formed so that the diameter becomes smaller from the outer diameter to the inner diameter of the low pressure cylinder.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

3 is a schematic diagram showing an example of a cycle including a rotary two-stage compressor according to the present invention. The heating cycle includes components such as a rotary two-stage compressor 100, a condenser 300, an evaporator 400, a phase separator 500, and a four-way valve 600. The condenser 300 constitutes an indoor unit, and the compressor 100, the evaporator 400, and the phase separator 500 constitute an outdoor unit. The refrigerant compressed in the compressor 100 flows into the condenser 300 of the indoor unit through the four-way valve 600, and the compressed refrigerant gas is heat-exchanged with the ambient and condensed. The condensed refrigerant passes through the expansion valve and becomes low pressure. The refrigerant passing through the expansion valve is separated into gas and liquid in the phase separator 500, and the liquid flows into the evaporator 400. The liquid is heat exchanged in the evaporator 400 and evaporated to be introduced into the accumulator 200 in a gaseous state and then introduced into the low pressure compression assembly (not shown) from the accumulator 200 through the refrigerant inlet pipe 151 of the compressor 100 do. The gas separated from the phase separator 500 flows into the compressor 100 through the injection pipe 153. The medium pressure refrigerant compressed by the low pressure compression assembly of the compressor 100 and the refrigerant introduced through the injection tube 153 are introduced into the high pressure compression assembly (not shown) of the compressor 100 and compressed to high pressure. The discharge pipe 152 is discharged to the outside of the compressor 100 again.

4 is a view showing an example of a rotary two-stage compressor according to the present invention. Rotary two-stage compressor 100 according to an embodiment of the present invention, the lower pressure compression assembly 120, the intermediate plate 140, the high pressure compression assembly 130 and the electric motor 110 from the bottom in the sealed container 101 ). And a refrigerant inlet pipe 151 connected to the accumulator 200 and a refrigerant discharge pipe 152 passing through the hermetically sealed container 101 and discharging the compressed refrigerant to the outside of the hermetically sealed container.

The electric motor 110 includes a stator 111, a rotor 112, and a rotating shaft 113. The stator 111 is provided with coils wound around lamination lamination of ring-shaped electromagnetic steel plates and lamination. The rotor 112 also has a lamination laminated with an electromagnetic steel plate. The rotating shaft 113 passes through the center of the rotor 112 and is fixed to the rotor 112. When the electric current is applied to the electric motor 110, the rotor 112 rotates by the mutual electromagnetic force between the stator 111 and the rotor 112, and the rotary shaft 113 fixed to the rotor 112 also rotates together with the rotor 112 Rotate together. The rotary shaft 113 extends from the rotor 112 to the low pressure compression assembly 120 so as to pass through the middle of the low pressure compression assembly 120, the intermediate plate 140 and the high pressure compression assembly 130.

The low pressure compression assembly 120 and the high pressure compression assembly 130 are stacked in this order from the bottom through the intermediate plate 140 and in the order of the low pressure compression assembly 120 to the intermediate plate 140 to the high pressure compression assembly 130 . Conversely, the high pressure compression assembly 120, the intermediate plate 140, and the high pressure compression assembly 130 may be stacked in this order from the bottom. In addition, regardless of the stacking order of the low pressure compression assembly 120, the middle plate 140 and the high pressure compression assembly 130, the lower bearing and the upper bearing 161 and the upper bearing 162 are respectively installed It helps the rotation of the rotary shaft 113, and supports the load of each component of the two-stage compression assembly stacked vertically. The upper bearing 162 is three-point welded to the hermetic container 101 to support the load of the two-stage compression assembly and fix it to the hermetic container 101.

The low-pressure compression assembly 120 is connected to the refrigerant inflow pipe 151 through the hermetically sealed container 101 from the outside. The lower bearing 161 and the lower cover 171 are positioned below the low pressure compression assembly 120 and the intermediate pressure chamber Pm is formed between the lower bearing 161 and the lower cover 171. The intermediate pressure chamber Pm is a space through which the refrigerant compressed in the low pressure compression assembly 120 is discharged and is a space in which the refrigerant is temporarily stored before the refrigerant is introduced into the high pressure compression assembly 130, And serves as a buffer space on the flow path through which refrigerant flows to the high-pressure compression assembly 130.

The center portion where the rotary shaft 131 is inserted / installed and the peripheral portion where the lower cover 171 is in contact with the lower bearing 161 are protruded downward, respectively, as shown in FIG. And the lower cover 171 is formed in a flat plate shape having a hole through which the rotation shaft 131 passes and being in close contact with the lower bearing 161. At this time, the downward protruding peripheral portion of the lower bearing 161 and the flat peripheral portion of the lower cover 171 are bolted together to the low-pressure cylinder 121 at a time. As another example, the lower bearing 161 may protrude downward only at the center of which the rotation shaft 113 is inserted / installed, and at the same time, other portions thereof may be formed flat, and the lower cover 171 may have a hole through which the rotation shaft 113 penetrates. The provided central portion may be formed flat, and at the same time, the periphery thereof may be stepped up to protrude upward. At this time, the flat peripheral portion of the lower bearing 161 and the peripheral portion protruding upwardly from the lower cover 171 are bolted to the low-pressure cylinder 121 at a time. In this case, the shape of the lower bearing 161 can be simplified to reduce the number of work, and the shape of the lower cover 171 can also be easily manufactured by pressing. Furthermore, the shape and the fastening method of the lower bearing 161 and the lower cover 171 are not limited to the above-mentioned method, and the intermediate pressure chamber Pm is formed in the lower bearing 161 However, the intermediate pressure chamber Pm may be formed in any one of the upper bearing 162 and the intermediate plate 140.

A discharge port (not shown) is provided at an upper portion of the upper bearing 162 located at the upper portion of the high-pressure compression assembly 130. Pressure refrigerant discharged from the high-pressure compression assembly 130 through the discharge port of the upper bearing 162 is discharged to the outside through the refrigerant discharge pipe 152 located at the upper portion of the closed vessel 101.

The lower bearing 161, the low pressure compression assembly 120, the intermediate plate 140 and the high pressure compression assembly 130 are provided with an internal flow passage 180 (not shown) for connecting the low pressure compression assembly 120 to the high pressure compression assembly 130 Is formed. The internal flow path 180 is formed vertically so as to be substantially parallel to the axial direction of the compressor.

Since the inner passage 180 is not a separate tube, the injection tube 153 (shown in FIG. 3) into which the refrigerant gas separated from the above-described phase separator 500 (shown in FIG. 3) flows into the inner passage 180. It can be installed anywhere. For example, a through hole (not shown) is formed in any one of the lower bearing 161, the intermediate plate 140, and the high pressure cylinder 131 forming the intermediate pressure chamber Pm, and the injection tube 153 is formed in the through hole. ), The refrigerant gas can be introduced, and the compression efficiency can be increased.

5 is a view showing an example of a low pressure compression assembly of a rotary two-stage compressor according to the present invention. The low pressure compression assembly 120 includes a low pressure cylinder 121, a low pressure eccentric portion 122, a low pressure roller 123, a low pressure vane 124, a low pressure elastic member 125, a low pressure inlet 126, (127). The rotary shaft 113 passes the central portion of the low-pressure cylinder 121, and the low-pressure eccentric portion 122 is fixed to the rotary shaft 113. At this time, the low-pressure eccentric portion 122 may be formed integrally with the rotary shaft 113. A low-pressure roller 123 is rotatably installed in the low-pressure eccentric portion 122, and the low-pressure roller 123 rotates while rotating along the inner diameter of the low-pressure cylinder 121 as the rotary shaft 113 rotates. A low-pressure inlet hole 126 and an intermediate-pressure discharge hole 127 are formed on both sides of the low-pressure vane 124. The space in the low-pressure cylinder 121 is partitioned by the low-pressure vane 124 and the low-pressure roller 123, so that the refrigerant before and after compression coexists in the low-pressure cylinder 121. Pressure refrigerant inflow hole 126 and the portion including the low-pressure refrigerant inflow hole S ₁ and the intermediate-pressure discharge hole 127 is divided by the low-pressure vane 124 and the low-pressure roller 123, And is referred to as a pressure refrigerant discharge portion (D _m ). Pressure elastic member 125 is a means for applying a force to the low-pressure vane 124 so that the low-pressure vane 124 maintains contact with the low-pressure roller 123. [ The vane hole 124h formed in the low-pressure cylinder 121 is formed so as to pass through the low-pressure cylinder 121 in the lateral direction so that the low-pressure vane 124 can be positioned. The low pressure vane 124 is guided through the vane hole 124 and a low pressure elastic member 125 for applying a force to the low pressure vane 124 extends through the low pressure cylinder 121 to the hermetically sealed container 101 . One end of the low pressure elastic member 125 is in contact with the low pressure vane 124 and the other end is in contact with the closed container 101 so that the low pressure vane 124 is kept in contact with the low pressure roller 123, .

The low pressure cylinder 121 is provided with an intermediate pressure communication hole (not shown) so that the refrigerant compressed by the low pressure compression assembly 120 can be introduced into the high pressure compression assembly 130 through the intermediate pressure chamber Pm formed by the lower bearing 161 120a are formed. The intermediate pressure communication hole 120a is formed so as not to overlap with the refrigerant inflow pipe 151 inserted into the low pressure inflow hole 126, that is, to prevent the internal flow path 180 and the refrigerant inflow pipe 151 from overlapping each other. ). Pressure refrigerant is introduced from the intermediate pressure chamber Pm into the high-pressure compression assembly 130 even if the refrigerant is partially overlapped with the refrigerant inlet pipe 151. However, in this case, it is not preferable since the internal flow path 180 can see a loss by the cross-sectional area overlapping the refrigerant inflow pipe 151. Further, while the refrigerant bypasses the periphery of the refrigerant inflow pipe 151, the pressure may be lowered.

As shown in FIG. 5, when the low pressure eccentric portion 122 rotates by the rotation of the rotary shaft 113, and the low pressure roller 123 rolls along the low pressure cylinder 121, the volume of the low pressure inflow portion S ₁ is reduced. Since the low pressure inlet S ₁ becomes low as it is increased, the refrigerant flows through the low pressure inlet hole 126. On the other hand, while the volume of the intermediate-pressure discharge portion D _m is reduced, the refrigerant filled in the intermediate-pressure discharge portion D _m is compressed and discharged through the intermediate-pressure discharge hole 127. As the low pressure eccentric part 122 and the low pressure roller 123 rotate, the volume of the low pressure inlet part S ₁ and the intermediate pressure discharge part D _m continuously changes, and discharges the compressed refrigerant every one revolution.

6 to 8 is a view showing a part of a rotary two-stage compressor according to an embodiment of the present invention. In order from the bottom, the lower bearing 161, the low pressure compression assembly 120, the intermediate plate 140, the high pressure compression assembly 130 is stacked. The low pressure refrigerant flows into the low pressure cylinder 121 through the refrigerant inlet pipe 151 and the low pressure inlet hole 126 and is compressed and then discharged through the intermediate pressure discharge hole 127 to the low pressure compression assembly 120 The lower bearing 161 and the lower cover 171. In this way, An intermediate pressure discharge hole 161h is formed in the lower bearing 161 so that the intermediate pressure discharge hole 127 and the intermediate pressure discharge hole 161h of the lower bearing 161 can overlap with each other, A valve (not shown) is provided under the intermediate pressure discharge hole 161h so that when the refrigerant compressed in the intermediate pressure discharge portion Dm of the low pressure compression assembly 120 is compressed to a predetermined pressure, . The refrigerant discharged to the intermediate pressure chamber Pm is again supplied to the intermediate pressure communication hole 120a and the intermediate plate 140 formed in the low pressure cylinder 121 through the intermediate pressure communication hole 161a formed in the lower bearing 161 And then flows into the high-pressure compression assembly 130 through the intermediate-pressure inlet hole 140a and the intermediate-pressure inlet groove 130a of the high-pressure cylinder 131. Intermediate pressure communication hole 161a of the lower bearing 161, intermediate pressure communication hole 120a of the low pressure compression assembly, intermediate pressure communication hole 140a of the intermediate plate 140, and intermediate pressure inflow of the high pressure compression assembly 130 The groove 130a forms an internal flow path 180 through which the medium pressure refrigerant compressed by the low pressure compression assembly 120 passes. At this time, the intermediate pressure inlet groove 130a of the high-pressure compression assembly 130 is formed in the shape of an inclined groove so as to communicate with the internal space of the high-pressure cylinder 131. [ A lower portion of the intermediate pressure inlet groove 130a is formed to abut the intermediate pressure communication hole 140a of the intermediate plate 140 to form a part of the internal flow passage 180. The refrigerant of the intermediate pressure And flows into the high pressure cylinder 131 through the groove 130a. When the medium pressure refrigerant flows into the high pressure compression assembly 130 through the internal flow path 180, the high pressure compression assembly 130 converts the medium pressure refrigerant to the high pressure in the same operating principle as the low pressure compression assembly 120. Compress.

As described above, when the internal passage 180 through which the refrigerant of the intermediate pressure passes is not formed by a separate pipe but is formed inside the closed container 101, the noise can be reduced and the length of the internal passage 180 Can be shortened, and the loss of the refrigerant pressure due to the resistance can be reduced. The intermediate pressure chamber Pm may be formed in any one of the upper bearing 162 and the intermediate plate 140 although the intermediate pressure chamber Pm is formed in the lower bearing 161 . In any case, the internal passage 180 is formed in the interior of the two-stage compression assembly so that the intermediate-pressure refrigerant compressed in the low-pressure compression assembly 120 through the internal passage 180 And is guided to the high pressure compression assembly 130. With such a configuration, the length of the flow path through which the refrigerant of the intermediate pressure is guided can be shortened, the flow loss can be minimized, and noise and vibration can be reduced without passing through the connection pipe passing through the closed container 101.

At this time, the intermediate pressure communication hole 120a of the low pressure compression assembly 120 constituting the internal flow path 180 to prevent the internal flow path 180 from being blocked by the refrigerant inlet pipe 151, and the intermediate pressure of the intermediate plate 140. The communication hole 140a and the intermediate pressure inlet groove 130a of the high pressure compression assembly 130 are formed to be spaced apart from the refrigerant inlet pipe 151 when viewed in the axial direction of the compressor 100.

The intermediate pressure communication hole 161a of the lower bearing 161 is formed to avoid the position where the refrigerant inlet pipe 151 is inserted so as not to overlap with the refrigerant inlet pipe 151 connected to the low pressure cylinder 121. The coolant inlet pipe 151 is inserted into the low-pressure inlet hole 126 formed in the low-pressure cylinder 121. The low pressure inlet hole 126 is formed close to the low pressure vane insertion hole 124h into which the low pressure vane 124 (shown in FIG. 5) is inserted. This is because as the low pressure inlet hole 126 is farther from the low pressure vane 124 (shown in FIG. 5), a dead volume that does not contribute to the compression of the refrigerant in the inner space of the low pressure cylinder 121 increases.

The intermediate pressure inflow groove 130a of the high pressure cylinder 131 is not formed so as to penetrate from the lower portion to the upper portion of the high pressure cylinder 131 but communicates with the lower portion of the high pressure cylinder 131 from the lower portion thereof to the inner space of the high pressure cylinder 131 As shown in FIG. At this time, the intermediate-pressure inlet groove 130a is formed close to the high-pressure vane hole 134h into which a high-pressure vane (not shown) is inserted. As in the low pressure compression assembly, the intermediate pressure inlet groove 130a must be formed close to the high pressure vane (not shown) to reduce the corpuscular volume in the interior space of the high pressure cylinder 131. [

The low-pressure vane 124 and the high-pressure vane (not shown) are located on the same axis. Therefore, the intermediate pressure communication hole 161a formed in the lower bearing 161 and the intermediate pressure inflow groove 130a formed in the high pressure cylinder 131 are not formed on the same axis, and horizontal positions are formed to be spaced apart from each other. In order to connect the intermediate pressure communication hole 161a of the lower bearing 161 and the intermediate pressure communication hole 130a of the high pressure cylinder 131 in the third embodiment of the present invention, The intermediate pressure communication hole 120a of the intermediate plate 140 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed to be substantially helical. The intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed to overlap each other in a spiral manner. That is, the intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 overlap to form a spiral communication hole. At this time, one end of the spiral communication hole overlaps with the intermediate pressure communication hole 161a of the lower bearing 161, and the other end overlaps with the intermediate pressure inlet groove 130a of the high pressure cylinder 131. One end of the intermediate pressure communication hole 120a of the low pressure cylinder 121 is connected to the intermediate pressure communication hole 161a of the lower bearing 161. That is, the intermediate pressure communication hole 120a of the low pressure cylinder 121 is formed such that one end of the intermediate pressure communication hole 120a which is in contact with the intermediate pressure communication hole 161a of the lower bearing 161 is passed through in the vertical direction of the low pressure cylinder 121, The remaining portion of the hole 120a is formed spirally as a whole, while the lower end portion of the intermediate pressure communication hole 120a gradually increases from one end to the other end. In addition, the intermediate pressure communication hole 140a of the intermediate plate 140, on the other hand, the other end of the spiral communication hole, that is, the other end overlapping the intermediate pressure inlet groove 130a of the upper cylinder 130 is perpendicular to the intermediate plate 140. It is formed to penetrate in the direction. Further, the upper end portion of the intermediate pressure communication hole 120a gradually increases from one end overlapping with the intermediate pressure communication hole 161a of the lower bearing 161 to the other end, and is formed spirally as a whole.

When the intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed in a spiral shape, the refrigerant is formed in the intermediate pressure communication hole 120a and the middle of the low pressure cylinder 121. The resistance received along the intermediate pressure communication hole 140a of the plate 140 is reduced. Of course, the intermediate pressure communication hole 120a of the low-pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are not only helical, but also shaped like an arcuate shape in which the height of the upper or lower end does not change .

When the intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed in a spiral or arc shape, the spiral or arcuate intermediate pressure communication holes 120a, The fastening holes 120b and 140b can be formed in the center portion of the fastening hole 120b. The lower bearing 161, the low-pressure cylinder 121, the intermediate plate 140, the high-pressure cylinder 131, and the upper bearing 162 are generally fastened through bolts. At this time, the fastening holes 161b, 120b, 130b, 140b, and 162b to which the bolts are fastened are the refrigerant inlet pipe 151, the medium pressure communication hole 161a, 120a, 130a, and 162a, the medium pressure inlet groove 140a, and the middle. Various members such as the pressure discharge hole 127 and the internal flow path should be avoided. Further, the fastening holes 161b, 120b, 130b, 140b, and 162b must be formed in at least three places, and the fastening force must be evenly distributed to the entire compressor assembly 105. [ The intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are connected to the intermediate pressure communication hole 161a and the high pressure cylinder 131 of the lower bearing 161, The length is longer than that of the intermediate pressure inflow groove 130a, which prevents the formation of a plurality of fastening holes 161b, 120b, 130b, 140b, and 162b. Therefore, when the intermediate pressure communication hole 120a of the low pressure cylinder and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed in a spiral or arc shape, the fastening hole 161b, 120b, 130b, 140b, 162b can be formed, which is advantageous for distributing a plurality of fastening holes 161b, 120b, 130b, 140b, 162b in the entire compressor assembly 105.

9 is a view showing an example of a rotary shaft provided in a rotary two-stage compressor according to the present invention. The low pressure eccentric portion 122 and the high pressure eccentric portion 132 are coupled to the rotary shaft 113. The low pressure eccentric 122 and the high pressure eccentric 132 are coupled to the rotating shaft 113 with a phase difference of generally 180 kHz to reduce vibration. The rotary shaft 113 is hollow hollow and has an oil communication hole 113a at a lower portion of the low pressure eccentric portion 122 and an upper portion of the high pressure eccentric portion 132. The rotating shaft 113 is formed as a hollow shaft, and a thin plate stirrer 113b bent in a spiral shape is inserted into the inside 113h. The stirrer 113b is fitted in the inside 113h of the rotating shaft 113 and rotates together with the rotating shaft 113 when the rotating shaft 113 rotates. As the stirrer 113b rotates together by the rotation of the rotary shaft 113, oil filled in the lower portion of the airtight container 101 (shown in FIG. 4) rises along the inside of the rotary shaft 113 along the stirrer 113b. A portion of the low pressure roller 121, the intermediate plate 140 and the high pressure cylinder 131 through the oil communication hole 113a formed in the rotating shaft 113, and the low pressure roller 123 (shown in FIG. 5). And a high pressure roller (not shown).

10 is a view showing an example of the installation structure of the refrigerant inlet pipe in the rotary two-stage compressor according to the present invention, Figure 11 is an example of the structure before the refrigerant inlet pipe is installed in the rotary two-stage compressor according to the present invention Some illustrated drawings. In the rotary two-stage compressor according to the present invention, the refrigerant inlet tube 151 is fixed to the low pressure compression assembly 120 through the sealed container 101, and the refrigerant inflow of the low pressure refrigerant flowing through the accumulator 200 flows. The pipe 151 penetrates the sealed container 101 in a high pressure state and is tightly fixed to the low pressure compression assembly 120 in a low pressure state to prevent leakage of the refrigerant.

Refrigerant inlet pipe 151 is composed of a kind of 'L' type of refrigerant pipe, the lower side of the container 101 is provided with a through hole (101h) through which the refrigerant inlet pipe 151 can pass, low pressure compression assembly 120 is provided with a low pressure inlet hole 126 in which the refrigerant inlet pipe 151 is inserted into one side of the low pressure cylinder 121. At this time, one end of the refrigerant inlet pipe 151 is covered so that the sealing appearance 201 and the sealing inner tube 202 of different materials overlap, and then the sealed container 101 through the through-hole 101h of the sealed container 101. The inner part of the low pressure cylinder 121 is inserted into the low pressure inlet hole 126, and the other part of the refrigerant inlet pipe 151 is disposed between the outer diameter of the refrigerant inlet pipe 151 and the sealed container 101 outside the sealed container 101. The brazing part is welded so that the welding part 203 may be provided.

At this time, the low pressure inlet hole 126 is installed so as to penetrate from the outer diameter of the low pressure cylinder 121 to the inner diameter, not only to easily fit the refrigerant inlet pipe 151, but also to prevent leakage of parts due to the pressure difference (leak). In order to reduce the diameter from the outer diameter of the low pressure cylinder 121 to the inner diameter is preferably formed to be stepped, it may be configured to be stepped as an example.

Of course, even if the low pressure inlet hole 126 is formed at a position that interferes with the intermediate pressure communication hole 120a of the low pressure cylinder 121, the low pressure cylinder (151) is inserted into the low pressure inlet hole 126 because the low pressure cylinder ( The refrigerant flowing along the intermediate pressure communication hole 120a of 121 may be prevented from leaking through the low pressure inlet hole 126.

On the other hand, while the refrigerant inlet pipe 151 maintains the low pressure state as the refrigerant of low pressure flows, the internal flow path including the intermediate pressure communication holes 161a, 120a, 130a, and 162a and the intermediate pressure inlet groove 140a ( 180 maintains an intermediate pressure as the refrigerant compressed in the low pressure compression assembly 120 flows, and thus resistance is greater in the inner flow path than the refrigerant inlet pipe 151. The inner flow path 180 is disposed on a straight line. The flow path through which the intermediate pressure refrigerant flows is shortened to reduce the flow path resistance. Furthermore, the inner diameter d2 of the inner flow path 180 is reduced to the inner diameter d1 of the refrigerant inlet pipe 151 or the low pressure inlet hole 126. It may be configured to reduce the flow path resistance by configuring larger than the inner diameter of.

12 is a graph showing the input power according to the diameter of the flow path of the rotary two-stage compressor according to the present invention. In the region where the input power P / Po of the rotary two stage compressor according to the present invention is relatively low, the medium in the medium pressure state with respect to the inner diameter d1 of the refrigerant inlet pipe through which the refrigerant in the low pressure state flows is inside. The ratio of the inner diameter d2 of the flow path is low in the range of 0.8 to 2.2. That is, in order to reduce the flow path resistance of the inner flow path in the intermediate pressure state to the flow path resistance of the coolant inflow pipe in the low pressure state, it is preferable that the inner diameter d2 of the inner flow path is larger than the inner diameter d1 of the coolant inflow pipe. As the inner diameter d2 of the inner passage is excessively larger than the inner diameter d1 of the refrigerant inlet tube, the refrigerant expands as it passes through the inner passage and can be changed to a low pressure state, thereby reducing the compression efficiency. It is preferable that it is formed larger within 2.2 times than the inner diameter d1 of this refrigerant inflow pipe.

In the foregoing, the present invention has been described in detail by way of examples on the basis of the embodiments of the present invention and the accompanying drawings. However, the scope of the present invention is not limited by the above embodiments and drawings, and the scope of the present invention will be limited only by the content of the following claims.

The rotary two-stage compressor according to the present invention configured as described above is welded at the same time even though the refrigerant inlet pipe into which the refrigerant in the low pressure flows is penetrated into the sealed container in the high pressure state. There is an advantage in that leakage of the refrigerant can be prevented and further compression efficiency can be increased.

In addition, the rotary two-stage compressor according to the present invention has an internal flow path between the low pressure compression assembly in which the refrigerant is first compressed and the high pressure compression assembly in which the refrigerant is secondly compressed, so that the length of the internal flow path can be reduced, and the intermediate pressure can be reduced. Since the inner diameter of the inner flow path is made larger than that of the low pressure refrigerant inlet pipe, the diameter of the inner flow path can be optimized without limiting the installation space. There is an advantage that can reduce the power consumption and at the same time increase the compression efficiency.

Claims (12)

Airtight containers under high pressure; A rotating shaft provided in the sealed container and transmitting a rotational force; A low pressure compression assembly in which primary compression of the refrigerant is performed inside the low pressure cylinder according to the rotation of the rotary shaft; A high pressure compression assembly in which secondary compression of the refrigerant compressed first in the high pressure cylinder is performed according to the rotation of the rotary shaft; A refrigerant inlet pipe which is fixed to the low pressure cylinder to penetrate the sealed container, and supplies the refrigerant to the low pressure compression assembly; And, It is installed between the hermetic container and the low pressure cylinder and the refrigerant inlet tube, and includes means for tightly fixing the refrigerant inlet tube to the hermetic container and the low pressure cylinder, The close fixing means is a rotary two-stage compressor, characterized in that at least two or more sealing pipes interposed between the low pressure inlet of the low pressure cylinder and the outer diameter of the refrigerant inlet pipe. The method of claim 1, Sealing tube is a rotary two-stage compressor, characterized in that installed to overlap in the radial direction with different materials. The method of claim 1, The low-pressure inlet hole of the low pressure cylinder is a rotary two-stage compressor characterized in that the step is formed so that the diameter becomes smaller from the outer diameter to the inner diameter of the low pressure cylinder. The method of claim 1, An intermediate plate partitioning between the low pressure cylinder and the high pressure cylinder; An intermediate pressure chamber in communication with the low pressure compression assembly and the high pressure compression assembly, wherein the refrigerant discharged from the low pressure compression assembly passes before the high pressure compression assembly is introduced; And an internal flow path through which the refrigerant flows by an intermediate pressure communication hole respectively formed in the intermediate pressure chamber, the low pressure cylinder, the intermediate plate, and the high pressure cylinder. The inner diameter of the refrigerant inlet pipe is a rotary two-stage compressor, characterized in that formed larger than the inner diameter of the inner passage. 5. The method of claim 4, The inner diameter of the refrigerant inlet pipe is a rotary two-stage compressor, characterized in that formed larger than 2.2 times less than the inner diameter of the inner passage. Airtight containers under high pressure; A rotating shaft provided in the sealed container and transmitting a rotational force; A low pressure compression assembly in which primary compression of the refrigerant is performed inside the low pressure cylinder according to the rotation of the rotary shaft; A high pressure compression assembly in which secondary compression of the refrigerant compressed first in the high pressure cylinder is performed according to the rotation of the rotary shaft; A refrigerant inlet pipe which is fixed to the low pressure cylinder to penetrate the sealed container, and supplies the refrigerant to the low pressure compression assembly; An intermediate plate partitioning between the low pressure cylinder and the high pressure cylinder; An intermediate pressure chamber in communication with the low pressure compression assembly and the high pressure compression assembly, wherein the refrigerant discharged from the low pressure compression assembly passes before the high pressure compression assembly is introduced; And, A rotary two-stage compressor comprising: an internal flow path formed by the intermediate pressure communication hole formed in the intermediate pressure chamber, the low pressure cylinder, the intermediate plate, and the high pressure cylinder, and having an inner diameter larger than that of the refrigerant inlet pipe. . The method of claim 6, And a means provided between the closed vessel, the low pressure cylinder, and the refrigerant inlet tube, and the means for tightly fixing the refrigerant inlet tube to the sealed vessel and the low pressure cylinder. Airtight containers under high pressure; A rotating shaft provided in the sealed container and transmitting a rotational force; A low pressure compression assembly in which primary compression of the refrigerant is performed inside the low pressure cylinder according to the rotation of the rotary shaft; A high pressure compression assembly in which secondary compression of the refrigerant compressed first in the high pressure cylinder is performed according to the rotation of the rotary shaft; A refrigerant inlet pipe which is fixed to the low pressure cylinder to penetrate the sealed container, and supplies the refrigerant to the low pressure compression assembly; An intermediate plate partitioning between the low pressure cylinder and the high pressure cylinder; An intermediate pressure chamber in communication with the low pressure compression assembly and the high pressure compression assembly, wherein the refrigerant discharged from the low pressure compression assembly passes before the high pressure compression assembly is introduced; An internal flow path formed by the intermediate pressure communication hole formed in the intermediate pressure chamber, the low pressure cylinder, the intermediate plate, and the high pressure cylinder, and having a larger inner diameter than the refrigerant inlet pipe; And It is installed between the hermetic container and the low pressure cylinder and the refrigerant inlet tube, and includes means for tightly fixing the refrigerant inlet tube to the hermetic container and the low pressure cylinder, The fixing means includes a weld welded between the through hole of the sealed container and the outer diameter of the refrigerant inlet pipe; And at least two or more sealing tubes interposed between the low pressure inlet of the low pressure cylinder and the outer diameter of the refrigerant inlet tube. 9. The method of claim 8, The low-pressure inlet hole of the low pressure cylinder is a rotary two-stage compressor characterized in that the step is formed so that the diameter becomes smaller from the outer diameter to the inner diameter of the low pressure cylinder. delete delete delete

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