JP2006152950A - Multi-stage compression type rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce a manufacturing cost and improve a volumetric efficiency of multi-stage compression type rotary compressor. <P>SOLUTION: The compressor comprises: an electric element 14 as a driving member; a cylinder 38; a roller 46 eccentrically rotating inside the cylinder 38 in such a manner that it is fitted by an eccentricity section 42 formed in a rotary shaft 16 of the electric member 14; a first and a second vanes 50, 52 which partition an inside of the cylinder 38 into a first compressing space 32 and a second compressing space 34 by contacting with this roller 46, respectively; a first and a second intake ports 160, 161 for inhaling refrigerant inside each compressing spaces 32, 34, respectively; and a first and a second discharging ports 47, 49 for discharging refrigerant compressed inside the compressing spaces 32, 34, respectively. The compression can be obtained by inhaling the refrigerant, which is compressed in the first compressing space 32 and discharged from the first discharging port 47, from the second inhaling port 161 to the second compressing space 34, and compressing it. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a multistage compression rotary compressor.

  Conventionally, this type of multi-stage compression rotary compressor, for example, a two-stage compression rotary compressor provided with first and second rotary compression elements, is driven by a drive element and a rotary shaft of the drive element in a sealed container. The first and second rotary compression elements are accommodated. The first and second rotary compression elements include an intermediate partition plate, first and second cylinders disposed on both sides of the intermediate partition plate, and a phase difference of 180 degrees in the first and second cylinders. And a first roller and a second roller which are fitted in an eccentric portion provided on the rotating shaft and rotate eccentrically in each cylinder, and a low pressure chamber which is in contact with the first and second rollers and which is in the low pressure chamber. First and second vanes that are divided into a high pressure chamber side and an opening surface on one side of the first cylinder (opposite side of the intermediate partition plate) and the other side of the second cylinder (opposite of the intermediate partition plate) And the support member that also serves as a bearing for the rotating shaft by closing the opening surface on the side.

Then, the refrigerant gas is sucked into the low pressure chamber side in the first cylinder from the suction port of the first rotary compression element (first stage), and is compressed by the operation of the first roller and the first vane to be intermediate pressure. It becomes. The compressed refrigerant gas is discharged from the first rotary compression element from the high pressure chamber side of the first cylinder through the discharge port and the discharge silencer chamber, and is discharged from the suction port of the second rotary compression element (second stage). The second cylinder is sucked into the low pressure chamber side of the second cylinder, and the second stage compression is performed by the operation of the second roller and the second vane to form a high-temperature and high-pressure refrigerant gas (for example, Patent Document 1). reference).
JP 2001-82371 A

  As described above, the first and second rotary compression elements of the conventional multistage compression rotary compressor include cylinders on both sides of the intermediate partition plate, rollers provided in each cylinder, and vanes in contact with the rollers, Since each cylinder has a structure including a support member that closes the opening surface on the side opposite to the side on which the intermediate partition plate is located, there has been a problem that the number of parts is large and the manufacturing cost is increased.

  In addition, a slight clearance is provided between the roller outer diameter and the cylinder inner diameter to ensure slidability. However, if the structure is such that each cylinder is compressed as described above, it is sucked into each cylinder. Since the refrigerant gas leaks from the entire circumference between the roller outer diameter and the cylinder inner diameter, there is a problem that the volume efficiency is remarkably lowered. In particular, in the case of a refrigerant having a high and low pressure difference that becomes extremely high pressure due to compression, such as carbon dioxide, the amount of leakage from the clearance has also increased.

  The present invention has been made to solve the problems of the related art, and aims to reduce the manufacturing cost and improve the volume efficiency of a multistage compression rotary compressor.

  A multistage compression rotary compressor according to the present invention includes a drive element, a cylinder, a roller that is fitted in an eccentric portion formed on a rotation shaft of the drive element and rotates eccentrically in the cylinder, and a cylinder that abuts on each of the rollers. First and second vanes that divide the interior into a first compression space and a second compression space, first and second suction ports for sucking refrigerant into each compression space, and each compression A first discharge port and a second discharge port for discharging the refrigerant compressed in the space, respectively. The refrigerant compressed in the first compression space and discharged from the first discharge port is The air is sucked into the second compression space from the suction port and compressed.

  In the multistage compression rotary compressor of the invention of claim 2, in addition to the above invention, vane slots formed in the cylinder and respectively accommodating the first and second vanes are arranged on a diagonal line passing through the center of the rotating shaft. It is.

  According to the multi-stage compression rotary compressor of the present invention, the first compression space and the second compression space can be formed in one cylinder, so that the number of parts can be reduced and the manufacturing can be performed. Costs can be significantly reduced.

  Further, by providing each compression space in one cylinder, leakage from the clearance between the roller outer diameter and the cylinder inner diameter can be reduced, and volume efficiency can be improved.

  Furthermore, by disposing the vane slot on a diagonal line passing through the center of the rotation shaft as in claim 2, the vane slot can be easily positioned and processed, and the manufacturing cost can be further reduced. become able to.

  Hereinafter, embodiments of the multistage compression rotary compressor of the present invention will be described in detail with reference to the drawings.

  FIG. 1 shows an embodiment of the multistage compression rotary compressor according to the present invention. The suction ports 160 and 161 and the discharge port 47 of the internal high-pressure rotary compressor 10 having the first and second compression spaces 32 and 34, 49 is a longitudinal sectional side view showing 49, and FIG. 2 is a plan sectional view of the cylinder 38 of the rotary compressor 10 of FIG.

  In each figure, the rotary compressor 10 of the present embodiment is an internal high-pressure type rotary compressor, and as a drive element disposed in the upper side of the internal space of the sealed container 12 in a vertical cylindrical sealed container 12 made of a steel plate. The electric element 14 and the rotary compression mechanism 18 that is disposed below the electric element 14 and is driven by the rotating shaft 16 of the electric element 14 are housed.

  The sealed container 12 has an oil reservoir at the bottom, a container body 12A that houses the electric element 14 and the rotary compression mechanism 18, and a generally bowl-shaped end cap (lid body) 12B that closes the upper opening of the container body 12A. A circular mounting hole 12D is formed on the upper surface of the end cap 12B, and a terminal (wiring is omitted) 20 for supplying power to the electric element 14 is mounted in the mounting hole 12D. ing. A mounting base 110 is provided at the bottom of the sealed container 12.

  The electric element 14 includes a stator 22 that is welded and fixed in an annular shape along the inner peripheral surface of the upper space of the sealed container 12, and a rotor 24 that is inserted and installed inside the stator 22 with a slight gap. The rotor 24 is fixed to a rotary shaft 16 that extends in the vertical direction through the center.

  The stator 22 has a laminated body 26 in which donut-shaped electromagnetic steel plates are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method. Similarly to the stator 22, the rotor 24 is also formed of a laminated body 30 of electromagnetic steel plates.

  The rotary compression mechanism 18 has first and second rotary compression elements. That is, the cylinder 38, the roller 46 fitted into the eccentric portion 42 formed on the rotating shaft 16 of the electric element 14, and eccentrically rotated in the cylinder 38, and the roller 38 is brought into contact with the roller 46 to contact the first inside the cylinder 38. First and second vanes 50 and 52 that are divided into a first compression space 32 as a rotary compression element and a second compression space 34 as a second rotary compression element, and an opening surface on the upper side of the cylinder 38 An upper support member 54 serving as a support member that closes and serves as a bearing for the rotating shaft 16 and a lower support that serves as a bearing for the rotating shaft 16 as well as the upper support member 54 by closing the lower opening surface of the cylinder 38. The member 56 is used.

  Also, the cylinder 38 discharges the refrigerant compressed in the compression spaces 32 and 34, and the first and second suction ports 160 and 161 for sucking the refrigerant into the compression spaces 32 and 34, respectively. First and second discharge ports 47 and 49 are respectively formed. That is, the first suction port 160 and the first discharge port 47 communicate with the inside of the first compression space 32 of the cylinder 38, and the second suction port 161 and the second discharge port 49 are connected to the second compression port 32 of the cylinder 38. It is formed so as to communicate with the compression space 34.

  Here, the excluded volumes of the first and second compression spaces 32 and 34 will be described with reference to FIGS. 3 and 4. That is, in FIG. 3, as shown in black in the cylinder 38, the first compression space 32 in which the left side in the cylinder 38 divided on the left and right by the first vane 50 and the second vane 52 is the first stage. Excluded volume. Further, as shown in black in FIG. 4, the second compression space 34 in which the right side in the cylinder 38 divided into the left and right by the first vane 50 and the second vane 52 is the second stage, as shown in black in the cylinder 38. Excluded volume. In the present embodiment, as described above, the inside of the cylinder 38 is divided into the first compression space 32 and the second compression space 34 by the first vane 50 and the second vane 52. The displacement volume of the first compression space 32 in the first stage and the displacement volume of the second compression space 34 in the second stage are determined by the position of the second vane 52, and the displacement of the first and second compression spaces 32, 34 is determined. The volume ratio has been determined. That is, one of the cylinders 38 defined by the first vane 50 and the second vane 52 (the left side in FIGS. 3 and 4) is connected to the first compression space 32 (first-stage excluded volume) and the other ( The right side in FIGS. 3 and 4 is a second compression space 34 (second-stage excluded volume).

  On the other hand, the upper support member 54 and the lower support member 56 include suction passages 58 and 60 that communicate with the inside of the cylinders 38 and 40 through the first and second suction ports 160 and 161, respectively, and the upper support member 54 and the lower support member 56. Discharge silencing chambers 62 and 64 formed by closing the recessed portions of the support member 56 with a cover as a wall are provided. That is, the discharge silencer chamber 62 is closed by the upper cover 66 that defines the discharge silencer chamber 62, and the discharge silencer chamber 64 is closed by the lower cover 68 that defines the discharge silencer chamber 64. The electric element 14 is provided above the upper cover 66 with a predetermined distance from the upper cover 66.

  The cylinder 38 is formed with vane slots 70 and 72 for accommodating the first and second vanes 50 and 52, respectively. The outside of the vane slots 70 and 72, that is, the vanes 50 and 52 are formed. On the back side, storage portions 70A and 72A for storing springs 74 and 76 as spring members are formed. The spring 74 abuts against the rear end portion of the first vane 50 and constantly urges the first vane 50 toward the roller 46. The spring 76 abuts against the rear end portion of the second vane 52 and constantly urges the second vane 52 toward the roller 46.

  Further, for example, the pressure (high pressure) in the sealed container 12 is also introduced into each of the storage units 70 </ b> A and 72 </ b> A and applied as the back pressure of the vanes 50 and 52. And each accommodating part 70A, 72A is opened to the vane slot 70, 72 side and the airtight container 12 (container main body 12A) side, and the airtight container 12 side of the springs 74, 76 accommodated in the accommodating part 70A, 72A is provided. Are provided with metal plugs 137, 139, which serve to prevent the springs 74, 76 from coming off.

  On the side surface of the container body 12A of the sealed container 12, suction passages 58, 60 of the upper support member 54 and the lower support member 56, a discharge silencer chamber 64 of the lower support member 56, and a position corresponding to above the electric element 14 are provided. The sleeves 141, 142, 143 and 144 are fixed by welding.

  One end of a refrigerant introduction pipe 92 for introducing refrigerant gas into the second compression space 34 of the cylinder 38 is inserted and connected in the sleeve 141, and one end of the refrigerant introduction pipe 92 communicates with the suction passage 58. The refrigerant introduction pipe 92 rises above the sealed container 12 and then extends downward to reach the sleeve 143, and the other end is inserted and connected into the sleeve 143 to communicate with the discharge silencing chamber 64.

  One end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the first compression space 32 of the cylinder 38 is inserted and connected into the sleeve 142, and one end of the refrigerant introduction pipe 94 communicates with the suction passage 60. A refrigerant discharge pipe 96 is inserted and connected into the sleeve 144, and one end of the refrigerant discharge pipe 96 communicates with the inside of the sealed container 12.

  On the other hand, the discharge silencer chamber 62 and the inside of the sealed container 12 communicate with each other through a hole 120 penetrating the upper cover 66, and a discharge pipe 121 is erected at the upper end of the hole 120. The high-temperature and high-pressure refrigerant gas compressed in the compression space 34 and discharged into the discharge silencer chamber 62 is discharged into the sealed container 12.

  Next, the operation of the rotary compressor 10 having the above configuration will be described with reference to FIGS. 3 to 6 are views showing the operation of the roller 46 and the first and second vanes 50 and 52 in the cylinder 38. FIG. When the stator coil 28 of the electric element 14 is energized through the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the roller 46 is eccentrically rotated in the cylinder 38 by being fitted to an eccentric portion 42 provided integrally with the rotary shaft 16.

  As a result, the low-pressure refrigerant is sucked into the first compression space 32 of the cylinder 38 from the refrigerant introduction pipe 94 of the rotary compressor 10 through the suction passage 60 and the first suction port 160. When the roller 46 passes through the first suction port 160 as shown in FIG. 3, the suction into the first compression space 32 is completed.

  The refrigerant gas sucked into the first compression space 32 is compressed by the operation of the roller 46 and the first and second vanes 50 and 52. When the refrigerant reaches a predetermined pressure, a discharge valve (not shown) that opens and closes the first discharge port 47 is opened, and the cylinder 38 and the discharge silencing chamber 64 communicate with each other. The refrigerant gas is discharged from the first discharge port 47 to the discharge silencer chamber 64. The discharge into the discharge silencer chamber 64 is performed until the roller 46 passes through the first discharge port 47 as shown in FIG.

  On the other hand, the refrigerant gas discharged into the discharge silencer chamber 64 enters the refrigerant introduction pipe 92 and exits from the rotary compressor 10. Here, the refrigerant gas in the refrigerant introduction pipe 92 exiting from the rotary compressor 10 is cooled by ambient air or a radiator (not shown) or the like in the process of passing through the refrigerant introduction pipe 92 to radiate heat.

  Thereafter, the refrigerant returns to the rotary compressor 10, enters the suction passage 58 from the refrigerant introduction pipe 92, and is sucked into the second compression space 34 of the cylinder 38 through the second suction port 161. The refrigerant is sucked into the second compression space 34 until the roller 46 passes through the second suction port 161 as shown in FIG. The refrigerant gas sucked into the second compression space 34 is compressed by the operation of the roller 46, the first vane 50, and the second vane 52. When the refrigerant in the second compression space 34 reaches a predetermined high pressure, a discharge valve (not shown) that opens and closes the second discharge port 49 opens, and the cylinder 38 and the discharge silencer chamber 62 are communicated with each other. The refrigerant gas in the second compression space 34 is discharged from the second discharge port 49 to the discharge silencer chamber 62. Note that the refrigerant is discharged into the discharge silencer chamber 62 until the roller 46 passes through the second discharge port 49 as shown in FIG.

  The refrigerant gas discharged into the discharge silencer chamber 62 is discharged from the discharge pipe 121 into the sealed container 12 through the hole 120 penetrating the upper cover 66. The refrigerant discharged into the sealed container 12 is discharged to the outside from a refrigerant discharge pipe 96 formed on the side surface of the container main body 12A above the electric element 14.

  As described above, by forming the first compression space 32 and the second compression space 34 in the cylinder 38 as in the rotary compressor 10 of the present invention, the number of parts constituting the rotary compression mechanism unit 18 is reduced. Will be able to. In other words, the conventional multi-stage compression rotary compressor closes the cylinder on both sides of the intermediate partition plate, the rollers provided in each cylinder, and the opening surface of each cylinder opposite to the side where the intermediate partition plate is located. Since the compression member is formed in each cylinder, the number of parts is large and the manufacturing cost is increased.

  However, according to the rotary compressor 10 of the present invention, since the two compression spaces 32 and 34 can be provided in one cylinder, the cylinder, roller, intermediate partition plate and the like constituting one conventional rotary compression element are provided. It becomes possible to abolish and the number of parts can be reduced. This makes it possible to significantly reduce the manufacturing cost.

  Furthermore, by providing the first and second compression spaces 32 and 34 in one cylinder 38, leakage from the clearance between the outer diameter of the roller 46 and the inner diameter of the cylinder 38 can be reduced. That is, in the conventional multistage compression rotary compressor, the refrigerant gas is compressed in each cylinder, and the refrigerant gas sucked into each cylinder leaks from the entire circumference between the roller outer diameter and the cylinder inner diameter. For this reason, the volumetric efficiency is deteriorated.

  However, by forming two compression spaces (the first compression space 32 and the second compression space 34) in one cylinder 38 as in the present invention, the clearance between the outer diameter of the roller 46 and the inner diameter of the cylinder 38 is also substantially reduced. As a result, the leakage of the refrigerant gas in the compression elements 32 and 34 from the clearance between the outer diameter of the roller 46 and the inner diameter of the cylinder 38 can be reduced.

  In particular, when carbon dioxide refrigerant is used for the rotary compressor 10, since carbon dioxide has a large difference between high and low pressure, there has been a problem that the amount of refrigerant leakage from the clearance is large and volume efficiency is further deteriorated. Even when carbon dioxide is used as a refrigerant, the amount of leakage can be reduced due to the structure.

  Thereby, the volumetric efficiency of the rotary compressor 10 can be improved.

  As described above in detail, the present invention can provide the rotary compressor 10 with low cost and high efficiency.

  Next, another embodiment of the rotary compressor of the present invention will be described. 7 is a longitudinal side view showing the suction ports 160 and 161 and the discharge ports 47 and 49 of the rotary compressor 10 in this case, and FIG. 8 is a plan sectional view of the cylinder 38 of the rotary compressor 10. 7 and 8 that are denoted by the same reference numerals as those in FIGS. 1 to 6 have the same or similar effects.

  The rotary compressor 10 of the present embodiment is an internal intermediate type rotary compressor. That is, in the rotary compressor 10 of this embodiment, an intermediate discharge passage (not shown) in which the discharge silencer chamber 64 formed in the lower support member 56 and the inside of the sealed container 12 pass through the cylinder 38, the upper support member 54, and the upper cover 66. A discharge pipe 123 is erected at the upper end of the intermediate discharge passage, is compressed in the first compression space 32 from the discharge pipe 123, and passes through the first discharge port 47 to the discharge silencer chamber 64. The discharged intermediate pressure refrigerant gas is discharged into the sealed container 12.

  In the rotary compressor 10 of this embodiment, as shown in FIG. 8, vane slots 70 and 72 that respectively accommodate the first and second vanes 50 and 52 are arranged on a diagonal line passing through the center of the rotary shaft 16.

  The excluded volumes of the first and second compression spaces 32 and 34 in this case will be described with reference to FIGS. 9 and 10. In FIG. 9, as shown in black in the cylinder 38, the excluded volume of the first compression space 32 in which the left side in the cylinder 38 divided on the left and right by the first vane 50 and the second vane 52 is the first stage. It becomes.

  On the other hand, as shown in black in the cylinder 38 in FIG. 10, the first vane 50 and the second suction port 161 in the right cylinder 38 partitioned by the first vane 50 and the second vane 52 are connected. The space (inside the cylinder 38 from the first vane 50 to the second suction port 161 on the rotation direction side of the roller 46) serves as an excluded volume of the second compression space 34 that is the second stage. That is, as described above, the cylinder 38 is partitioned into the first compression space 32 and the second compression space 34 by the first vane 50 and the second vane 52. The displacement volume of the first compression space 32 of the first stage is determined by the position of the second vane 52, and the displacement volume of the second compression space 34 of the second stage is determined by the position of the second suction port 161. Thus, the excluded volume ratio of the first and second compression spaces 32 and 34 is determined. That is, the excluded volume of the second compression space 34 is determined by the position of the second suction port 161.

  As described above, by setting the excluded volume according to the position of the second suction port 161, the first and second vanes 50 and 52 can be arranged on a diagonal line passing through the center of the rotating shaft 16 as described above. It becomes like this.

  Here, in the processing method of the vane slots 70 and 72, first, one end of one vane slot (for example, the vane slot 70) is positioned at one end not communicating with the cylinder 38, and the end mill is moved from above the cylinder 38 to the cylinder 38. The hole 71 is formed so as to be perpendicular to each other. Then, the end mill is moved from the hole 71 to a position (hole 73) that is previously positioned in a straight line in the horizontal direction. Then, the vane slots 70 and 72 are completed by grind | polishing the location processed with the end mill.

  As described above, by arranging the vane slots 70 and 72 on a diagonal line passing through the center of the rotating shaft 16, the vane slot can be easily positioned and can be easily processed by an end mill. .

  On the other hand, on the side surface of the container body 12 </ b> A of the sealed container 12, the suction passages 58 and 60 of the upper support member 54 and the lower support member 56, the discharge silencer chamber 62 of the upper support member 54, and the upper cover 66 are positioned correspondingly. The sleeves 141, 142, 145 and 146 are fixed by welding.

  In the sleeve 141, one end of a refrigerant introduction pipe 92 for introducing refrigerant gas into the second compression space of the cylinder 38 is inserted and connected in the same manner as in the above embodiment, and one end of the refrigerant introduction pipe 92 is connected to the suction passage. Communicate with 58. The refrigerant introduction pipe 92 rises above the sealed container 12 and then extends downward to reach the sleeve 146, and the other end is inserted and connected into the sleeve 146 to communicate with the sealed container 12.

  Further, one end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the first compression space 32 of the cylinder 38 is inserted and connected in the sleeve 142, and one end of the refrigerant introduction pipe 94 communicates with the suction passage 60. In addition, a refrigerant discharge pipe 96 is inserted and connected into the sleeve 145, and one end of the refrigerant discharge pipe 96 communicates with the discharge silencing chamber 62 of the upper support member 54.

  With the above configuration, the operation of the rotary compressor 10 of the present embodiment will be described with reference to FIGS. When the stator coil 28 of the electric element 14 is energized through the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the roller 46 is eccentrically rotated in the cylinder 38 by being fitted to an eccentric portion 42 provided integrally with the rotary shaft 16.

  As a result, the low-pressure refrigerant is sucked into the first compression space 32 of the cylinder 38 from the refrigerant introduction pipe 94 of the rotary compressor 10 through the suction passage 60 and the first suction port 160. When the roller 46 passes through the first suction port 160 as shown in FIG. 9, the suction into the first compression space 32 is completed.

  The refrigerant gas sucked into the first compression space 32 is compressed by the operation of the roller 46 and the first and second vanes 50 and 52. When the refrigerant reaches a predetermined pressure, a discharge valve (not shown) that opens and closes the first discharge port 47 is opened, and the cylinder 38 and the discharge silencing chamber 64 communicate with each other. The refrigerant gas is discharged from the first discharge port 47 to the discharge silencer chamber 64. The discharge into the discharge silencer chamber 64 is performed until the roller 46 passes through the first discharge port 47 as shown in FIG.

  On the other hand, the refrigerant gas discharged into the discharge silencer chamber 64 is discharged from the discharge pipe 123 into the sealed container 12 through an intermediate discharge passage (not shown). The intermediate-pressure refrigerant gas discharged into the sealed container 12 enters the refrigerant introduction pipe 92 from the other end of the refrigerant introduction pipe 92 connected to the closed container 12 and exits the rotary compressor 10. Here, the refrigerant gas in the refrigerant introduction pipe 92 exiting from the rotary compressor 10 is cooled by ambient air or a radiator (not shown) or the like in the process of passing through the refrigerant introduction pipe 92 to radiate heat.

  Thereafter, the refrigerant returns to the rotary compressor 10, enters the suction passage 58 from the refrigerant introduction pipe 92, and is sucked into the second compression space 34 of the cylinder 38 through the second suction port 161. The refrigerant is sucked into the second compression space 34 until the roller 46 passes through the second suction port 161 as shown in FIG. The refrigerant gas sucked into the second compression space 34 is compressed by the operation of the roller 46, the first vane 50, and the second vane 52. When the refrigerant in the second compression space 34 reaches a predetermined high pressure, a discharge valve (not shown) that opens and closes the second discharge port 49 opens, and the cylinder 38 and the discharge silencer chamber 62 are communicated with each other. The refrigerant gas in the second compression space 34 is discharged from the second discharge port 49 to the discharge silencer chamber 62. The refrigerant is discharged into the discharge silencer chamber 62 until the roller 46 passes through the second discharge port 49 as shown in FIG.

  The refrigerant gas discharged into the discharge silencing chamber 62 enters the refrigerant discharge pipe 96 connected to the discharge silencing chamber 62 and is discharged outside the rotary compressor 10.

  As described in detail above, also in this embodiment, the number of parts can be reduced, and the manufacturing cost can be remarkably suppressed. Further, similarly to the above embodiment, leakage from the clearance between the outer diameter of the roller 46 and the inner diameter of the cylinder 38 can be reduced. Thereby, the highly efficient rotary compressor 10 can be manufactured at low cost.

  In particular, when carbon dioxide refrigerant is used for the rotary compressor 10, since carbon dioxide has a large difference between high and low pressure, there has been a problem that the amount of refrigerant leakage from the clearance is large and volume efficiency is further deteriorated. Even when carbon dioxide is used as a refrigerant, the amount of leakage can be reduced due to the structure.

  Furthermore, in the case of this embodiment, the vane slots 70 and 72 can be easily positioned and processed by arranging the vane slots 70 and 72 on a diagonal line passing through the center of the rotating shaft 16 as described above. As a result, the manufacturing cost can be further reduced.

  In each of the embodiments described above, the rotary compressor 10 with the rotary shaft 16 installed vertically has been described. However, it goes without saying that the present invention can also be applied to the case where a rotary compressor with the rotary shaft installed horizontally is used. .

  Further, in each of the above embodiments, the rotary compressor 10 having the first and second compression spaces 32 and 34 is used. However, the present invention can be applied to a multistage compression rotary compressor having three or more compression spaces. .

It is a vertical side view which shows each suction port and discharge port of the multistage compression type rotary compressor of the Example of this invention. It is a plane sectional view of the cylinder of the rotary compressor of FIG. It is a figure which shows operation | movement of the 1st and 2nd vane and roller at the time of completion | finish of the 1st step | suction in the cylinder of FIG. It is a figure which shows the position of the 1st and 2nd vane and roller at the time of completion | finish of the 2nd step | paragraph in the cylinder of FIG. FIG. 3 is a diagram illustrating positions of first and second vanes and rollers at the end of the first-stage discharge in the cylinder of FIG. 2. FIG. 3 is a diagram illustrating positions of first and second vanes and rollers at the end of second-stage discharge in the cylinder of FIG. 2. It is a vertical side view which shows each suction port and discharge port of the multistage compression type rotary compressor of the other Example of this invention. It is a plane sectional view of the cylinder of the rotary compressor of FIG. It is a figure which shows operation | movement of the 1st and 2nd vane and roller at the time of completion | finish of the 1st step | suction in the cylinder of FIG. It is a figure which shows the position of the 1st and 2nd vane and roller at the time of completion | finish of the suction of the 2nd step | paragraph in the cylinder of FIG. It is a figure which shows the position of the 1st and 2nd vane and roller at the time of completion | finish of discharge of the 1st step | paragraph in the cylinder of FIG. It is a figure which shows the position of the 1st and 2nd vane and roller at the time of completion | finish of the discharge of the 2nd step | paragraph in the cylinder of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Rotary compressor 12 Sealed container 14 Electric element 16 Rotating shaft 18 Rotation compression mechanism part 20 Terminal 22 Stator 24 Rotor 26 Laminated body 28 Stator coil 30 Laminated body 32 1st compression space 34 2nd compression space 38 Cylinder 46 Roller 50 1st 1 vane 52 second vane 58, 60 suction passage 62, 64 discharge silencer chamber 70, 72 vane slot 70A, 72A storage part 74, 76 spring 92, 94 refrigerant introduction pipe 96 refrigerant discharge pipe 120 hole 121, 123 discharge pipe

Claims (2)

A driving element;
A cylinder,
A roller fitted into an eccentric portion formed on the rotating shaft of the drive element and rotated eccentrically in the cylinder;
First and second vanes that respectively contact the rollers and partition the cylinder into a first compression space and a second compression space;
First and second suction ports for sucking refrigerant into the respective compression spaces;
First and second discharge ports for discharging the refrigerant compressed in each compression space,
Multistage compression, wherein the refrigerant compressed in the first compression space and discharged from the first discharge port is sucked into the second compression space from the second suction port and compressed. Rotary compressor.   2. The multistage compression rotary compressor according to claim 1, wherein vane slots formed in the cylinder and respectively storing the first and second vanes are arranged on a diagonal line passing through the center of the rotating shaft.

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