KR101381085B1 - 2 stage rotary compressor - Google Patents

Abstract

The present invention is provided in a sealed container, a sealed container, a two-stage compression assembly including a low pressure compression assembly, an intermediate plate and a high pressure compression assembly, a low pressure compression assembly, and a low pressure refrigerant inlet and a high pressure to which a low pressure refrigerant flows. A compression assembly includes a medium pressure refrigerant inlet through which the medium pressure refrigerant compressed in the low pressure compression assembly is introduced, and the diameter of the medium pressure refrigerant inlet is in the range of more than 0.5 times and less than 1.1 times the diameter of the low pressure refrigerant inlet. Provided is a rotary two stage compressor. Through this configuration, the volume flow rate of the refrigerant flowing into the high pressure compression assembly through the medium pressure refrigerant inlet is appropriately adjusted to prevent excessive pressure or excessive decrease in pressure at which the medium pressure refrigerant is sucked into the high pressure compression assembly. can do.

Suction diameter, refrigerant inlet, diameter ratio, rotary two stage compressor

Description

Rotary two stage compressor {2 STAGE ROTARY COMPRESSOR}

1 is a view showing an example of a conventional rotary two-stage compressor;

2 is a view showing an example of a conventional rotary twin compressor;

3 is a schematic diagram showing an example of a cycle including a rotary two-stage compressor;

4 illustrates a rotary two stage compressor according to one embodiment of the present invention;

5 shows a low pressure compression assembly of a rotary two stage compressor according to one embodiment of the invention;

6 and 7 respectively show a part of a rotary two stage compressor according to an embodiment of the present invention from above and below;

8 is a view of a portion of the rotary two-stage compressor according to an embodiment of the present invention;

9 is a view showing an example of a rotary shaft provided in the rotary two-stage compressor of the present invention;

10 is a view showing a rotary two-stage compressor equipped with an injection tube according to an embodiment of the present invention;

11 and 12 are schematic diagrams showing suction diameters of the rotary two-stage compressor of the present invention, in which the U-shaped pipe and the inner flow path are intermediate pressure flow paths, respectively;

13 and 14 illustrate examples of low pressure refrigerant inlets included in a rotary two-stage compressor according to one embodiment of the present invention;

15 illustrates an example of a high pressure cylinder for comparing diameters of medium pressure refrigerant inlets of various sizes;

FIG. 16 is a graph showing the energy efficiency ratio EER according to the ratio d2 / d1 of the diameter d2 of the medium pressure refrigerant inlet 136 to the diameter d1 of the low pressure refrigerant inlet 126.

The present invention relates to a rotary two stage compressor. More particularly, the present invention relates to a rotary two stage compressor having a refrigerant inlet designed for compression capacity of each of the low pressure compression assembly and the high pressure compression assembly.

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. Rotary compressor that compresses the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder so that a compression space for absorbing and discharging the working gas is formed between the roller and the eccentric rotating roller and the cylinder. 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, the rotary compressor has two rollers and two cylinders at the top and the bottom, and a pair of roller and cylinders at the top and the bottom, and a rotary twin compressor for compressing the part and the rest at the top and the bottom. Two-stage compressor with two rollers and two cylinders in communication, one pair compresses relatively low pressure refrigerant and the other compresses relatively high pressure refrigerant after low pressure compression stage Further development.

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 rotary shaft is rotated by the electric motor, the eccentric portion and the roller rotate along the inner periphery 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.

The present invention adjusts the diameter ratio of the low pressure refrigerant inlet for introducing the low pressure refrigerant into the low pressure compression assembly and the medium pressure refrigerant inlet for introducing the medium pressure refrigerant compressed in the low pressure compression assembly into the high pressure compression assembly to be within a predetermined range. An object of the present invention is to provide a rotary two-stage compressor with improved compression efficiency.

In addition, an object of the present invention is to provide a rotary two-stage compressor including a connection flow path connecting the low pressure refrigerant inlet and the medium pressure refrigerant inlet.

It is another object of the present invention to provide a rotary two-stage compressor in which an injection tube is connected to a connection passage.

The present invention is provided in a sealed container, a sealed container, a two-stage compression assembly including a low pressure compression assembly, an intermediate plate and a high pressure compression assembly, a low pressure compression assembly, and a low pressure refrigerant inlet and a high pressure to which a low pressure refrigerant flows. A compression assembly includes a medium pressure refrigerant inlet through which the medium pressure refrigerant compressed in the low pressure compression assembly is introduced, and the diameter of the medium pressure refrigerant inlet is in the range of more than 0.5 times and less than 1.1 times the diameter of the low pressure refrigerant inlet. Provided is a rotary two stage compressor. Through this configuration, the volume flow rate of the refrigerant flowing into the high pressure compression assembly through the medium pressure refrigerant inlet is appropriately adjusted to prevent excessive pressure or excessive decrease in pressure at which the medium pressure refrigerant is sucked into the high pressure compression assembly. can do.

In another aspect of the present invention, there is provided a rotary two-stage compressor, characterized in that the diameter of the medium pressure refrigerant inlet is 0.6 to 1.0 times the diameter of the low pressure refrigerant inlet. Through such a configuration, the energy efficiency ratio (EER) can be improved to 9.8 or more.

In another aspect of the present invention, there is provided a rotary two-stage compressor, characterized in that the diameter of the medium pressure refrigerant inlet is 0.9 to 1.0 times the diameter of the low pressure refrigerant inlet. Through such a configuration, the energy efficiency ratio (EER) can be improved to 10.0 or more.

In another aspect of the present invention, the low pressure compression assembly includes a low pressure cylinder for providing a space in which the refrigerant is compressed, and the low pressure refrigerant inlet is a tube inserted into the refrigerant compression space of the low pressure cylinder. To provide. Through this configuration, the low pressure refrigerant can be stably supplied to the compression space inside the low pressure cylinder. At this time, the inner diameter of the tube is the diameter of the low pressure refrigerant inlet.

In still another aspect of the present invention, a low pressure compression assembly includes a low pressure cylinder providing a space in which a refrigerant is compressed, and the low pressure refrigerant inlet includes a hole formed in the low pressure cylinder and a tube inserted into the hole. It provides a two-stage compressor. In this case, when the hole is processed to have a step with a portion having a large inner diameter outside the cylinder and a portion having a small inner diameter inside the cylinder, the pipe for introducing the refrigerant may be inserted only to a portion where the step is formed. Therefore, the installation of the pipe into which the refrigerant is introduced becomes convenient.

In another aspect of the present invention, there is provided a rotary two-stage compressor further comprising an intermediate pressure passage connecting the low pressure refrigerant inlet and the high pressure refrigerant inlet. Through this configuration, the refrigerant compressed in the low pressure compression assembly can be introduced into the high pressure compression assembly.

In another aspect of the present invention, there is provided a rotary two-stage compressor, characterized in that the intermediate pressure flow path is a U-shaped tube passing through the hermetically sealed container. Through such a configuration, it is possible to facilitate installation of a pipe that provides an intermediate pressure flow path.

In another aspect of the present invention, there is provided a rotary two-stage compressor, characterized in that the intermediate pressure passage is an inner passage formed inside the two stage compression assembly. Through this configuration, since the medium pressure refrigerant flows only inside the sealed container, vibration and noise of the entire compressor can be reduced. In addition, the length of the intermediate pressure passage through which the medium pressure refrigerant flows may be shortened to reduce the pressure loss.

In another aspect, the present invention provides a rotary two-stage compressor, further comprising an injection tube connected to the intermediate pressure flow path. Through this configuration, the refrigerant passing through the condenser can be injected into the rotary two stage compressor by separating the gaseous refrigerant from the phase separator, thereby improving the compression efficiency of the compressor.

In another aspect of the present invention, there is provided a rotary two-stage compressor, characterized in that it further comprises an intermediate pressure chamber located on the intermediate pressure passage. Through such a configuration, the phase difference between the discharge stroke and the suction stroke of the low pressure compression assembly and the high pressure compression assembly can be buffered, so that the medium pressure refrigerant can be stably supplied to the high pressure compression assembly.

In another aspect of the present invention, the intermediate pressure chamber provides a rotary two-stage compressor, characterized in that formed by a bearing and a bearing cover. Through this configuration, the intermediate pressure chamber can be easily formed without adding a separate member.

In another aspect of the present invention, the intermediate pressure chamber provides a rotary two-stage compressor, characterized in that located in any one of the top and bottom of the two-stage compression assembly.

3 is a schematic diagram illustrating an example of a refrigeration cycle configured by a rotary two-stage compressor. 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. Among them, 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 a rotary two-stage compressor according to an embodiment of the present invention. The rotary two-stage compressor 100 according to an embodiment of the present invention includes a low pressure compression assembly 120, an intermediate plate 140, a high-pressure compression assembly 130, and a motor 110, . 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 includes laminations in which ring-shaped electrical steel sheets are laminated, and coils wound on the laminations. 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 welded to the hermetically sealed container 101 at three points to support the load of the two-stage compression assembly and is fixed to the hermetically sealed 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. In addition, a lower bearing 161 and a lower cover 171 are positioned below the low pressure compression assembly 120. An intermediate pressure chamber Pm is formed between the lower bearing 161 and the lower cover 171. The intermediate pressure chamber Pm is a space in 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, from the low pressure compression assembly 120. The high pressure compression assembly 130 serves as a buffer space on the flow path through which the refrigerant flows.

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.

5 is a cross-sectional view of the low pressure compression assembly 120. The low pressure compression assembly 120 includes a low pressure cylinder 121, a low pressure eccentric 122, a low pressure roller 123, a low pressure vane 124, a low pressure elastic member 125, a low pressure refrigerant inlet hole 126, and an intermediate pressure discharge. And a hole 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. In addition, the space in the low pressure cylinder 121 is divided by the low pressure vane 124 and the low pressure roller 123, and 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, .

In addition, the low pressure cylinder 121 has a medium pressure communication hole 120a so that the refrigerant compressed in the low pressure compression assembly 120 can flow into the high pressure compression assembly 130 through the intermediate pressure chamber Pm formed by the lower bearing 161. ) Is 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 are a part of a rotary two-stage compressor according to an embodiment of the present invention. A lower bearing 161, a low-pressure compression assembly 120, an intermediate plate 140, and a high-pressure compression assembly 130 are stacked in this order from the bottom. 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 into the intermediate pressure chamber Pm is formed in 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. It passes through the intermediate pressure communication hole 140a and flows into the high pressure compression assembly 130 through 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 refrigerant having a medium pressure flows into the high-pressure compression assembly 130 through the internal passage 180, the high-pressure compression assembly 130 compresses the refrigerant at an intermediate pressure to a high pressure by the same operating principle as in the low- do.

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. In addition, in the above, an example in which the intermediate pressure chamber Pm is formed in the lower bearing 161 is described, but the intermediate pressure chamber Pm may be formed in any one of the upper bearing 162 and the intermediate plate 140. Accordingly, although the specific structure may vary slightly, in any case, the internal flow path 180 is formed inside the two-stage compression assembly, so that the medium pressure refrigerant compressed in the low pressure compression assembly 120 through the internal flow path 180 is formed. 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 inflow pipe 151 is inserted so as not to overlap with the refrigerant inflow 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.

In addition, the intermediate pressure inlet groove 130a of the high pressure cylinder 131 is not formed to penetrate from the lower portion to the upper portion of the high pressure cylinder 131 so as to communicate with the internal space of the high pressure cylinder 131 from the lower portion of the high pressure cylinder 131. It is formed at an angle. 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, since the intermediate pressure inlet groove 130a should be formed close to the high pressure vane (not shown), it is possible to reduce the dead volume in the space inside 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. [ At this time, 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 the intermediate pressure communication hole 161a and the high pressure cylinder 131 of the lower bearing 161. Since the length is longer than the intermediate pressure inlet groove (130a) of the hindered to form a plurality of fastening holes (161b, 120b, 130b, 140b, 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 an example of a rotary shaft provided in the 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 generally coupled to the rotation shaft 113 with a phase difference of 180 ° to reduce vibration. In addition, the rotating shaft 113 is a hollow shaft having an empty inside, and has an oil communication hole 103a at the lower portion of the low pressure eccentric portion 122 and the upper portion of the high pressure eccentric portion 132. In addition, the stirrer 103b of the thin plate bent spirally is inserted into the rotation shaft 113. The stirrer 103b is fitted inside the rotating shaft 113, and rotates together with the rotating shaft 130 when the rotating shaft 113 rotates. As the stirrer 103b rotates together by the rotation of the rotary shaft 113, the oil filled in the lower portion of the sealed container 101 (shown in FIG. 4) rises along the inside of the rotary shaft 113 along the stirrer 103b. A portion of the low pressure roller 121, the intermediate plate 140 and the high pressure cylinder 131 through the oil communication hole (103a) formed in the rotary shaft 113, the low pressure roller 123 (shown in Figure 5) And a high pressure roller (not shown).

10 is a view illustrating a compressor in which an injection tube is inserted according to an embodiment of the present invention. In the two-stage compressor according to the present invention, since the internal flow path 180 is not a separate pipe, the injection pipe 153 into which the refrigerant gas separated from the above-described phase separator 500 flows is located anywhere in the internal flow path 180. It may be installed. For example, a through hole 153h 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 pipe is inserted into the through hole 153h. 153 may be inserted to allow refrigerant gas to flow. As shown in FIG. 8, a through hole 153h is formed to penetrate the intermediate pressure discharge hole 127 of the low pressure cylinder 121, or a through hole 153h is formed in the lower bearing 161. If the injection pipe 153 is inserted into 153h, a pressure loss occurs while passing through the intermediate pressure chamber Pm and the inner flow passage 180. However, even if the liquid refrigerant flows through the injection tube 153, it flows down to the lower portion of the intermediate pressure chamber Pm, and thus, the behavior of the compressor 100 is stable.

11 and 12 are schematic diagrams showing the suction diameters of the rotary two-stage compressor of the present invention in which the U-shaped pipe and the inner flow path are used as intermediate pressure flow paths, respectively.

Referring to FIG. 11, in an embodiment of the present invention in which the U-shaped tube is an intermediate pressure flow path, the refrigerant inlet pipe 151 is inserted into the low pressure compression assembly 120. The low pressure refrigerant introduced through the refrigerant inlet pipe 151 is compressed in the low pressure compression assembly 120 and discharged into the intermediate pressure chamber Pm. Thereafter, the intermediate pressure chamber (Pm) and the high pressure compression assembly 130, both ends are respectively introduced into the high pressure compression assembly 130 by the U-shaped pipe 182 connected, and then compressed to a high pressure and discharged into the sealed container 101. do. At this time, the refrigerant inlet pipe 151 is inserted, and the diameter of the refrigerant inlet hole 126 (shown in FIG. 4) flowing into the low pressure compression assembly 120 becomes the diameter d1 of the low pressure refrigerant inlet. In addition, the U-shaped tube 182 has the same diameter of one end connected to the intermediate pressure chamber (Pm) and one end connected to the high pressure compression assembly 130, the diameter of the U-shaped tube 182 is the diameter of the medium pressure refrigerant inlet ( d2).

Referring to FIG. 12, in another embodiment of the present invention using an inner flow path as a medium pressure flow path, a refrigerant inlet pipe 151 is inserted into the low pressure compression assembly 120 and is formed inside the two-stage compression assembly 105. Through the flow path 180, the medium pressure refrigerant compressed by the low pressure compression assembly 120 is introduced into the high pressure compression assembly 130. Similar to the embodiment of the present invention in which the U-shaped pipe is an intermediate pressure flow path, the diameter of the refrigerant inlet hole 126 (shown in FIG. 4) into the low pressure compression assembly 120 is inserted into the refrigerant inlet pipe 151. It becomes diameter d1 of this low pressure refrigerant | coolant inflow part. The diameter d2 of the medium pressure refrigerant inflow portion is the diameter of the inner flow passage 180.

13 and 14 are views illustrating examples of the low pressure refrigerant inlet included in the rotary two-stage compressor according to the embodiment of the present invention. FIG. 13 illustrates a first example. When the diameter of the low pressure refrigerant inlet hole 126 formed in the low pressure cylinder 121 is uniformly formed from the outer diameter to the inner diameter of the low pressure cylinder 121, the constant low pressure refrigerant inlet hole ( 126 is the diameter d1 of the low pressure refrigerant inlet.

FIG. 14 illustrates a second example, wherein the diameter of the low pressure refrigerant inlet hole 126 is smaller than the inner diameter side of the low pressure cylinder 121 than the outer diameter side, and the low pressure refrigerant inlet hole 126 is formed stepwise. At this time, the diameter of the low-pressure refrigerant inlet hole 126 is smaller than the diameter of the low-pressure refrigerant inlet portion diameter of the inner diameter side. When the low pressure refrigerant inlet hole 126 is formed stepped, the insertion position of the refrigerant inlet tube 151 (shown in FIG. 4) inserted into the low pressure refrigerant inlet hole 126 may be restricted, and thus the refrigerant inlet tube 151 is illustrated. 4) is easy to install.

FIG. 15 is a view illustrating an example of a high pressure cylinder for comparing the diameters of the medium pressure refrigerant inlets of various sizes, and FIG. 16 is a medium pressure refrigerant inlet unit (D1) for the diameter d1 of the low pressure refrigerant inlet unit 126. It is a graph showing the energy efficiency ratio EER according to the ratio d2 / d1 of the diameter d2 of 136. 15 and 16, the high pressure cylinder 131 is formed with a medium pressure refrigerant inlet 136 into which a U-shaped tube 182 (shown in FIG. 11) is inserted. The diameter d2 of the medium pressure refrigerant inlet 136 may be a smaller diameter A, the same diameter B, and a larger diameter C than the diameter d1 of the low pressure refrigerant inlet dl (shown in FIG. 11). . At this time, when the diameter d2 of the intermediate pressure refrigerant inlet 136 is too large, the volume inside the high pressure cylinder 131 that can be used for compression is substantially reduced, and the suction pressure is also lowered. That is, the seal compression distance is reduced, and the suction pressure drops, so that the loss is increased. Therefore, the ratio d2 / d1 of the diameter d2 of the medium pressure refrigerant inlet 136 to the diameter d1 of the low pressure refrigerant inlet 126 is preferably less than 1.1.

In addition, when the diameter d2 of the intermediate pressure refrigerant inlet 136 is too small, the seal compression length becomes long, and the internal volume of the high pressure cylinder 131 increases. However, due to friction, etc. during the flow of the medium pressure refrigerant acts as a loss of flow, the loss increases. Therefore, the ratio d2 / d1 of the diameter d2 of the medium pressure refrigerant inlet 136 to the diameter d1 of the low pressure refrigerant inlet 126 is preferably greater than 0.5.

That is, the ratio d2 / d1 of the diameter d2 of the medium pressure refrigerant inlet 136 to the diameter d1 of the low pressure refrigerant inlet 126 is as follows.

Is satisfied. In this case, it was confirmed through experiments that the energy efficiency ratio (EER) can be improved to 9.6 or more. In particular, when the ratio d2 / d1 of the diameter d2 of the medium pressure refrigerant inlet 136 to the diameter d1 of the low pressure refrigerant inlet 126 is between 0.6 and 1.0, the energy efficiency ratio EER Can be improved to 9.8 or higher.

Most preferably, when the ratio d2 / d1 of the diameter d2 of the medium pressure refrigerant inlet 136 to the diameter d1 of the low pressure refrigerant inlet 126 is set to a value between 0.9 and 1.0, The energy efficiency ratio could be improved to 10.0 or more.

FIG. 15 illustrates a high pressure cylinder included in a two-stage compressor according to an embodiment in which a U-shaped tube is an intermediate pressure flow path, but in the case of a high pressure cylinder according to another embodiment in which the internal flow path is an intermediate pressure flow path. The same condition applies, with the diameter of the internal flow path being the diameter d2 of the medium pressure refrigerant inlet.

3 to 10, a schematic operation principle of a rotary two-stage compressor according to an embodiment of the present invention will be described.

The refrigerant circulating in the refrigeration cycle is temporarily stored in the accumulator 200 before entering the compressor 100. The accumulator 200 serves as a temporary storage space of the refrigerant, and also functions as a gas-liquid separator so that only gas is introduced into the compressor 100. In the accumulator 200, a refrigerant of gas is introduced into the low pressure cylinder 121 of the low pressure compression assembly 120 through the refrigerant inlet pipe 151. The refrigerant inlet pipe 151 penetrates the sealed container 101 and is fixed by welding to the sealed container 101. It is also inserted into the refrigerant inlet hole 126 formed in the low pressure cylinder 121. The refrigerant inlet hole 126 penetrates to the inner diameter of the low pressure cylinder 121. The refrigerant introduced into the internal space of the low pressure cylinder 121 through the coolant inlet hole 126 is formed by the low pressure cylinder 121 and the low pressure roller 123 by the relative motion of the low pressure cylinder 121 and the low pressure roller 123. It is compressed by the volume change of space defined by the low pressure vane 124. The compressed refrigerant is introduced into the high pressure cylinder 131 through the internal passage 180 from the low pressure cylinder 121 and then compressed by the high pressure compression assembly 130.

The internal flow path 180 includes an intermediate pressure discharge hole 127 of the low pressure cylinder 121, an intermediate pressure chamber Pm, an intermediate pressure communication hole 161a of the lower bearing 161, and an intermediate pressure communication hole 120a of the low pressure cylinder 121. The intermediate pressure refrigerant may be introduced into the high pressure cylinder 131 from the low pressure cylinder 121 by the intermediate pressure communication hole 140a of the intermediate plate 140 and the intermediate pressure inlet groove 130a of the high pressure cylinder 131. To connect so that the euro. In this case, the intermediate pressure chamber Pm may be replaced with or removed from a pipe.

That is, the refrigerant compressed by the low pressure compression assembly 120 is discharged into the intermediate pressure chamber Pm formed under the low pressure cylinder 121 by the intermediate pressure discharge hole 127 formed in the low pressure cylinder 121. The intermediate pressure chamber Pm is defined by the lower bearing 161 and the lower cover 171. In addition, the lower bearing 161 is formed with an intermediate pressure discharge hole 161h to overlap the intermediate pressure discharge hole 127 of the low pressure cylinder 121. In addition, the lower bearing 161 is provided with a valve 191 for opening and closing the intermediate pressure discharge hole 161. The valve 191 opens the intermediate pressure discharge hole 127 of the low pressure cylinder 121 and the intermediate pressure discharge hole 161h of the lower bearing 161 above the set pressure. The intermediate pressure refrigerant discharged into the intermediate pressure chamber Pm by the opening of the valve 191 is the intermediate pressure communication hole 161a of the lower bearing 161, the intermediate pressure communication hole 120a of the low pressure cylinder 121, and the middle. The intermediate pressure communication hole 140a of the plate 140 and the intermediate pressure inlet groove 131a of the high pressure cylinder 131 flow into the internal space of the high pressure cylinder 131. At this time, the injection pipe 153 is connected to the intermediate pressure communication hole 120a of the low pressure cylinder 121, and the refrigerant of the gas separated from the phase separator 500 through the injection pipe 153 is transferred to the internal flow path 180. Sprayed. Since the refrigerant separated from the phase separator 500 is higher than the refrigerant passing through the evaporator 400, the refrigerant separated from the phase separator 500 may be transferred to the high pressure compression assembly 130 together with the refrigerant compressed from the low pressure compression assembly 120. When the water is introduced, compressed and discharged, the input power of the compressor 100 can be reduced.

The refrigerant separated from the phase separator 500 and the refrigerant compressed in the low pressure compression assembly 120 are introduced into the high pressure cylinder 131 through the intermediate pressure inlet groove 130a of the high pressure cylinder 131, and the high pressure compression is performed. The assembly 130 is compressed to high pressure on the same operating principle as the low pressure compression assembly 120. The refrigerant compressed to high pressure in the high pressure compression assembly 130 includes the upper bearing 162 and the upper cover through the high pressure discharge hole 137 of the high pressure cylinder 131 and the high pressure discharge hole 162h formed in the upper bearing 162. It discharges to the discharge space D provided between 172. In this case, a valve 192 is installed at the upper portion of the upper bearing 162 to open and close the high pressure discharge hole 137 of the high pressure cylinder 131 and the high pressure discharge hole 162h of the upper bearing 162. Therefore, the refrigerant is discharged by opening the high pressure discharge hole 137 of the high pressure cylinder 131 and the high pressure discharge hole 162h of the upper bearing 162 only when the refrigerant is compressed to a predetermined pressure or higher in the high pressure compression assembly 130. Discharge to (D). The high pressure refrigerant is temporarily stored in the discharge space D, and then discharged to the upper portion of the sealed container 101 through the discharge port 172p of the upper cover 172. The interior of the sealed container 101 is filled with a high pressure refrigerant. The high pressure refrigerant filled in the sealed container 101 is discharged to the outside through the discharge pipe 152 penetrating the upper portion of the sealed container 101, circulates the refrigeration cycle, and again accumulator 200 and the phase separator ( 500 is introduced into the compressor 100 and undergoes a compression process.

In addition, the lower portion of the sealed container 101 is filled with lubricating oil for lubricating the compressor assembly 105. The lubricating oil rises along the inside of the rotating shaft 113 by the rotation of the stirrer 103b inserted into the rotating shaft 113, and the low pressure compression assembly 120 through the oil communication hole 103 formed in the rotating shaft 113. It is introduced into the high pressure compression assembly 130 to lubricate the compressor assembly 105. In addition, the vane holes 124h and 134h formed in the low pressure cylinder 121 and the high pressure cylinder 131 flow into the low pressure compression assembly 120 and the high pressure compression assembly 130 to lubricate the compressor assembly 105.

The rotary two-stage compressor provided by the present invention includes a low pressure refrigerant inlet for introducing refrigerant into the low pressure compression assembly, and an intermediate pressure refrigerant inlet for introducing medium pressure refrigerant compressed in the low pressure compression assembly into the high pressure compression assembly. The compression capacity and volumetric flow rate of each compression assembly can be adjusted to improve the compression efficiency of the compressor.

In addition, the rotary two-stage compressor provided by the present invention can improve the compression efficiency of the compressor by adjusting the size of each refrigerant inlet according to the structure of the refrigerant inlet.

Claims (12)

chest; A two-stage compression assembly provided inside the closed container and including a low pressure compression assembly, an intermediate plate, and a high pressure compression assembly; A low pressure refrigerant assembly, the low pressure refrigerant inlet tube being fitted to introduce a low pressure refrigerant, and a stepped low pressure refrigerant inlet so that its diameter is smaller on the inner diameter side of the low pressure compression assembly than on the outer diameter side of the low pressure compression assembly; And A high pressure compression assembly is provided, and the medium pressure refrigerant inlet pipe is fitted so that the medium pressure refrigerant compressed in the low pressure compression assembly is introduced, and the diameter thereof is smaller on the inner diameter side of the high pressure compression assembly than on the outer diameter side of the high pressure compression assembly. Includes; stepped medium pressure refrigerant inlet; Steps formed in the low pressure refrigerant inlet limits the insertion position of the low pressure refrigerant inlet, Steps formed in the medium pressure refrigerant inlet restricts the insertion position of the medium pressure refrigerant inlet, A relatively small diameter at the medium pressure refrigerant inlet is in the range of more than 0.5 times and less than 1.1 times the diameter of the relatively smaller side at the low pressure refrigerant inlet. The method according to claim 1, The diameter of the relatively small side in the medium pressure refrigerant inlet is a rotary two-stage compressor, characterized in that 0.6 to 1.0 times the diameter of the relatively small side in the low pressure refrigerant inlet. 3. The method of claim 2, The diameter of the relatively small side in the medium pressure refrigerant inlet is a rotary two-stage compressor, characterized in that 0.9 to 1.0 times the diameter of the relatively small side in the low pressure refrigerant inlet. The method according to claim 1, And the low pressure compression assembly comprises a low pressure cylinder providing a space in which the refrigerant is compressed. The method according to claim 1, And the high pressure compression assembly comprises a high pressure cylinder providing a space in which the refrigerant is compressed. The method according to claim 1, And an intermediate pressure chamber providing a space for the compressed refrigerant in the low pressure compression assembly, and an intermediate pressure passage connecting the intermediate pressure chamber and the intermediate pressure refrigerant inlet. The method according to claim 6, The intermediate pressure flow path is a rotary two-stage compressor, characterized in that the U-shaped tube penetrating the sealed container. delete The method according to claim 6, The rotary two-stage compressor further comprises; an injection pipe connected to the medium pressure flow path. The method according to claim 6, And a middle pressure chamber located on the middle pressure flow path. 11. The method of claim 10, The intermediate pressure chamber is formed by a bearing and a bearing cover. 11. The method of claim 10, The intermediate pressure chamber is a rotary two-stage compressor, characterized in that located in one of the top and bottom of the two-stage compression assembly.

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