KR101335100B1 - Rotary compressor - Google Patents

Abstract

[assignment]
The compressor can be miniaturized without causing pressure loss in the suction gas flow path, and a rotary compressor of resource saving, high efficiency and low vibration is provided.
[Solution]
The rotary compressor according to the present invention includes a compression mechanism driven by an electric motor through a crankshaft in a sealed container, the compression mechanism has a generally cylindrical inner space, and a suction port for sucking low pressure fluid of a refrigeration cycle into the inner space is radially provided. And a connecting pipe connecting the suction port to the suction port and the suction pipe outside the sealed container, and the cross-sectional shape of the suction port, the connecting pipe and the suction pipe is a non-circular shape having a larger rotation direction dimension than the axial dimension of the crankshaft. do.

Description

[0001] ROTARY COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor that compresses refrigerant gas used in refrigeration cycles of refrigeration and air conditioning devices such as air conditioners and refrigerators.

Conventionally, a rotary compressor configured such that the length of the cylinder circumferential direction of the cylinder suction port is set larger than the length of the cylinder longitudinal direction, or the length of the cylinder longitudinal direction of the suction port is set larger than the length of the cylinder circumferential direction. Is proposed (for example, refer patent document 1).

In addition, a suction fitting having a cylinder suction port having a non-circular cross-sectional shape having a larger rotational direction dimension than the axial dimension of the main shaft, and having one connection portion having the non-circular cross-sectional shape and the other having a circular cross-sectional shape is provided. A rotary compressor configured to be connected to a suction pipe through the air has been proposed (see Patent Document 2, for example).

Japanese Patent Laid-Open No. 5-99170 Japanese Patent Laid-Open No. 2003-214370

The rotary compressor described in Patent Document 2 connects a cylinder suction port having a non-circular cross section and a suction pipe having a circular cross section through a suction fitting. In order to prevent the pressure loss caused by the reduction of the flow path area between the cylinder suction port, which is a flow path for low pressure fluid, and the suction pipe, the inner diameter of the suction pipe must be made large with respect to the axial dimension of the suction port. As a result, the miniaturization of the compressor by reducing the axial dimension of the compressor is a factor. In addition, in the multi-cylinder compressor, the axial spacing of the plurality of suction pipes cannot be reduced, and the influence was remarkable.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and it is possible to realize miniaturization of the compressor without generating pressure loss of the intake gas flow path, and to provide a resource-saving, high-efficiency, low-vibration rotary compressor.

The rotary compressor according to the present invention includes a compression mechanism driven by an electric motor through a crankshaft in a sealed container,

Compression mechanism

A cylinder having a substantially cylindrical inner space, and having a suction port for suctioning low pressure fluid of a refrigeration cycle into the inner space;

A connecting pipe connecting the suction port and the suction pipe outside the sealed container,

The cross-sectional shape of the suction port, the connection pipe and the suction pipe is characterized in that the non-circular shape is larger than the axial dimension of the crankshaft.

In the rotary compressor according to the present invention, since the cross-sectional shape of the suction port, the connecting pipe and the suction pipe is a non-circular shape in which the rotational direction dimension is larger than the axial dimension of the crankshaft, the cylinder, the connecting pipe, Since the axial dimension of the suction pipe can be reduced without causing pressure loss due to the reduction of the flow path area, it is possible to miniaturize by reducing the axial dimension of the compressor, thereby obtaining a resource-saving, high-efficiency, low vibration rotary compressor. It becomes possible.

BRIEF DESCRIPTION OF THE DRAWINGS The figure which shows Embodiment 1 and is a longitudinal cross-sectional view of the 2-cylinder rotary compressor 100. FIG.
2 is an enlarged view of the compression mechanism 3 of FIG. 1.
3 is a cross-sectional view of the first cylinder 8, showing a first embodiment.
4 is an enlarged view of a portion A of FIG. 1;
5 is a cross-sectional view of the suction port 50 showing a first embodiment.
6 is a cross-sectional view taken along line BB of FIG. 3.
FIG. 7 is a view showing Embodiment 1, wherein the suction port 50, 51, the suction pipes 40, 41 and the connection pipes 60, 61 have an external view of a two-cylinder rotary compressor 100 having a circular cross-sectional shape. .
FIG. 8 is a view showing Embodiment 1 of a two-cylinder rotary compressor 100 having suction ports 50 and 51, suction pipes 40 and 41, and connecting pipes 60 and 61 having a non-circular cross-sectional shape. Appearance.
FIG. 9 is a diagram showing Embodiment 1 showing a connecting pipe 60 in the case where the suction pipe inserting portion 60b is made circular and the press-fitting portion 60a is made non-circular and connected in the same flow path area. (a) is a long hole in the rotational direction, (b) is a long hole in the axial direction).
FIG. 10 is a diagram showing Embodiment 1, a longitudinal cross-sectional view of a two-cylinder rotary compressor 200 of Modification 1. FIG.
FIG. 11: is a figure which shows Embodiment 1. The longitudinal cross-sectional view of the 2-cylinder rotary compressor 200 of the modification 1 (connecting pipe connection part 22a, 23a of suction pipe 22, 23 is a non-circular cross-sectional shape).
12 is a diagram showing Embodiment 1, wherein the internal stress of the connecting pipe 60 when the suction port 50 having a long cross-sectional shape and the press-fitting portion 60a of the connecting pipe 60 is press-fitted. Schematic diagram showing the direction of.
FIG. 13: is a figure which shows Embodiment 1, and is a schematic diagram which shows one modification form of the press fitting part 60a of the connection pipe 60. FIG.
FIG. 14 is a diagram showing a first embodiment, and a sectional view of the press-fit portion 60a of the connecting pipe 60. FIG.
FIG. 15 is a diagram showing a first embodiment, showing a compression process angle θ determined by the suction port edge 50b and the discharge port edge 70a. FIG.

Embodiment Mode 1.

FIG. 1: is a figure which shows Embodiment 1, and is a longitudinal cross-sectional view of the 2-cylinder rotary compressor 100. As shown in FIG. The two-cylinder rotary compressor 100 is driven through the crankshaft 4 by an electric motor 2 and an electric motor 2 having a stator 2a and a rotor 2b in a sealed container 1 in a high pressure atmosphere. The mechanism 3 and the refrigeration oil which are not shown in figure (by lubricating the sliding part of the compression mechanism 3, are stored in the bottom part in the airtight container 1) are provided.

The airtight container 1 is comprised from the trunk | drum 1a, the upper container 1b, and the lower container 1c. The upper container 1b and the trunk | drum 1a, the lower container 1c, and the trunk | drum 1a are respectively integrated by welding.

The compression mechanism 3 is provided at the bottom of the sealed container 1, and the electric motor 2 is provided above the compression mechanism 3.

The compression mechanism 3 sucks and compresses low-pressure refrigerant gas from the suction pipes 40 and 41 connected to the low pressure side of the refrigeration cycle.

The high pressure refrigerant gas discharged from the compression mechanism 3 passes through the electric motor 2 and is discharged from the discharge tube 25 to the high pressure side of the refrigeration cycle.

The electric motor 2 is a brushless DC motor which normally uses a permanent magnet for the rotor 2b.

However, induction motors are sometimes used.

Electric power is supplied from the external power supply (not shown) to the stator 2a of the electric motor 2 via the glass terminal 26 and the lead wire 27.

Although mentioned later, the suction pipes 40 and 41 are connected to the connection parts 1d and 1e of the airtight container 1 by welding.

FIG. 2 is an enlarged view of the compression mechanism 3 of FIG. 1, and FIG. 3 is a diagram showing Embodiment 1 and is a cross-sectional view of the first cylinder 8. The structure of the compression mechanism 3 is demonstrated, referring FIG. 2, FIG. The crankshaft 4 is fixed to the rotor 2b of the electric motor 2, is provided on the opposite side of the main shaft 4a and the main shaft 4a supported by the main shaft support 6, and is provided with the sub bearing 7 The supporting shaft 4b and the eccentric shafts 4c and 4d formed by providing a predetermined phase difference (for example, 180 °) between the supporting shaft 4b and the supporting shaft 4b are provided.

The main shaft bearing 6 is roughly T-shaped in cross section. The main shaft 4a of the crank shaft 4 is fitted with a clearance for sliding, and the main shaft 4a is freely rotated. Moreover, one side (motor 2 side) of the opening part of the both ends of the 1st cylinder 8 is closed.

The auxiliary bearing 7 is roughly T-shaped in cross section. The sub shaft 4b of the crank shaft 4 is fitted with a clearance for sliding, and the sub shaft 4b is rotatably freely held. Moreover, one side (semi-motor 2 side) of the opening part of the both ends of the 2nd cylinder 9 is closed.

The compression mechanism 3 includes a first cylinder 8 on the main shaft 4a side and a second cylinder 9 on the side of the subshaft 4b.

The first cylinder 8 (cylinder) has a substantially cylindrical inner space, and is fitted with a first piston 11a (rolling piston) rotatably fitted to the eccentric shaft 4c of the crankshaft 4 in this inner space. Is prepared). Moreover, the 1st vane 5a which reciprocates in the vane groove 8b is provided, contacting the 1st piston 11a with rotation of the eccentric shaft 4c. The vane groove 8b is provided in the radial direction of the 1st cylinder 8, and penetrates in the axial direction.

Both axial end faces of the inner space of the first cylinder 8 in which the first piston 11a and the first vane 5a are accommodated rotatably fitted to the eccentric shaft 4c of the crankshaft 4 are Closing with the spindle 6 and the partition plate 10 to form a sealed chamber (30).

Moreover, the suction chamber 30a is located in front of the rotation direction (shown by the arrow in FIG. 3) of the crankshaft 4 by the 1st piston 11a and the 1st vane 5a. And a compression chamber 30b located behind the crankshaft 4 in the rotational direction.

The second cylinder 9 (cylinder) also has a cylindrical inner space, and a second piston 11b rotatably fitted to the eccentric shaft 4d of the crankshaft 4 is provided in this inner space. Moreover, the second vane (not shown) which reciprocates in the vane groove (not shown) is provided, in contact with the 2nd piston 11b with rotation of the eccentric shaft 4d. The vane groove is provided in the radial direction of the second cylinder 9 and penetrates in the axial direction.

The secondary piston 11b which is rotatably fitted to the eccentric shaft 4d of the crankshaft 4, and both axial end surfaces of the inner space of the 2nd cylinder 9 which accommodated the 2nd vane receive the secondary shaft ( 7) and the partition plate 10 are closed to form a yarn 31.

The seal 31 is formed of the suction chamber 31a (not shown) and the crankshaft 4 positioned in front of the crankshaft rotational direction by the second piston 11b and the second vane. It is partitioned by the compression chamber 31b (not shown) located in the back direction of rotation.

Suction which communicates the suction pipes 40 and 41 and the seals 30 and 31 to the 1st cylinder 8 and the 2nd cylinder 9, respectively, so that the low pressure fluid of a refrigeration cycle may be sucked into the seals 30 and 31, respectively. Ports 50 and 51 are perforated in the radial direction.

In addition, connecting pipes 60 and 61 are used to connect (connect) the suction ports 50 and 51 to the suction pipes 40 and 41. The press-fitting parts 60a and 61a of the connecting pipes 60 and 61 are press-fitted into the press-fitting import parts 50a and 51a which are provided to be expanded to the outside of the suction ports 50 and 51. do. Suction pipes 40 and 41 are inserted into the suction pipe insertion parts 60b and 61b of the connection pipes 60 and 61. The suction pipe insertion parts 60b and 61b are connected by welding with the connection parts 1d and 1e (refer FIG. 1) of the airtight container 1, and the suction pipes 40 and 41. FIG.

The connecting portions 1d and 1e of the hermetic container 1 are perpendicular to the centerline of the hermetic container 1 and toward the center direction of the hermetic container 1 so as not to interfere when the connecting tubes 60 and 61 are inserted. Prepared.

4 is an enlarged view of a portion A of FIG. 1. The trunk | drum 1a of the sealed container 1, the lower part container 1c, and the trunk | drum 1a of the sealed container 1, and connection part 1d, 1e are all welded. Therefore, the predetermined interval L1 is prevented between the connecting portion 1d, the connecting portion 1e, the end of the trunk portion 1a of the airtight container 1, and the connecting portion 1e so as not to be affected by the welding twist. , L2).

Although not shown in the figure, when the closed container 1 and the lower container 1c have an integral structure by drawing molding or the like, L2 indicates the distance between the end portion of the lower R shape of the closed container and the connecting portion 1e.

The low pressure fluid flowing from the refrigeration cycle passes through the suction pipes 40 and 41, the press-fitting portions 60a and 61a of the connection pipes 60 and 61, and the suction ports 50 and 51, and the seals 30 and 31. Is introduced. Therefore, the cross-sectional areas of the suction pipes 40 and 41, the press-fitting portions 60a and 61a of the connecting pipes 60 and 61, and the suction ports 50 and 51 are sequentially increased so that the suction pressure loss does not increase in the suction path of the low pressure fluid. , They are doing pretty much the same.

FIG. 5: is a figure which shows Embodiment 1, and is sectional drawing of the suction port 50. As shown in FIG. The suction port 50 is made into the non-circular cross-sectional shape which made the rotation direction dimension D larger than the axial dimension H1 of the crankshaft 4. Therefore, an axial dimension can be made small compared with the circular cross-sectional shape of the same cross-sectional area.

By setting the suction port 50 to a non-circular cross-sectional shape and H1 <D, the axial height H of the first cylinder 8 can be set small.

FIG. 6 is a cross-sectional view taken along line B-B in FIG. 3. As shown in FIG. 6, it is necessary to provide a clearance W between the inner circumference 8a of the first cylinder 8 and the outer circumference 11c of the first piston 11a to avoid contact with each other. There is. The product S of the clearance W and the axial height H of the first cylinder 8 is a leakage passage communicating the compression chamber 30b and the suction chamber 30a, and a factor of the compressor efficiency decreases. It is known to become. By setting the axial height H of the 1st cylinder 8 small, it becomes possible to reduce the leakage area S and to improve compressor efficiency.

As a feature of the present embodiment, the suction pipes 40 and 41 and the connection pipes 60 and 61 also have a non-circular cross section in which the rotation direction dimension is larger than the axial dimension of the crankshaft 4. Therefore, the suction pipes 40 and 41 and the connection pipes 60 and 61 can also be made smaller in axial height than in the case of the circular cross section of the same cross-sectional area.

7 and 8 show Embodiment 1, and FIG. 7 shows a two-cylinder rotary compressor in which the suction ports 50 and 51, the suction pipes 40 and 41 and the connecting pipes 60 and 61 have a circular cross-sectional shape. 8 is an external view of the two-cylinder rotary compressor 100 in which the suction ports 50 and 51, the suction pipes 40 and 41 and the connection pipes 60 and 61 have a non-circular cross-sectional shape.

In the two-cylinder rotary compressor 100 shown in FIG. 7, the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a circular cross-sectional shape. In the two-cylinder rotary compressor 100 shown in FIG. 8, the suction ports 50, 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a non-circular cross-sectional shape.

Suction ports 50, 51 when the distance L1 between the connection portion 1d and the connection portion 1e and the distance L2 between the end portion of the trunk portion 1a of the hermetic container 1 and the connection portion 1e are made constant. ), The suction pipes 40 and 41, and the connecting pipes 60 and 61 have a non-circular cross-sectional shape, the shafts of the suction pipes 40 and 41 connected to the first cylinder 8 and the second cylinder 9. While the direction distance can be set small, the axial arrangement of the second cylinder 9 can be set low.

In the two-cylinder rotary compressor 100 shown in FIG. 7, the distance between the axial center of the second cylinder 9 and the lower surface of the lower container 1c is K 'and the two-cylinder rotary compressor shown in FIG. 8 ( When the distance between the axial center of the 2nd cylinder 9 in 100) and the lower surface of the lower container 1c is set to K, it becomes a relationship of K '> K.

By making the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 into a non-circular cross-sectional shape, the effect shown below is achieved.

(1) Since the axial height of the 1st cylinder 8 and the 2nd cylinder 9 can be made low, the height dimension of the axial direction of a compressor can be reduced (miniaturized).

(2) Since the suction pipes 40 and 41 and the connection pipes 60 and 61 also have a non-circular cross-sectional shape, the space L1 between the connection portion 1d and the connection portion 1e and the trunk portion of the sealed container 1 The distance L2 between the end portion of 1a and the connection portion 1e remains the same, and the positions of the first cylinder 8 and the second cylinder 9 are set to the suction ports 50 and 51 and the suction pipes 40 and 41. ), The connecting pipes 60 and 61 can be lowered than in the case of the circular cross-sectional shape (low vibration due to the low center of the compressor).

On the other hand, even if the suction ports 50 and 51 have a non-circular cross-sectional shape, when the suction pipes 40 and 41 and the connection pipes 60 and 61 are circular, the first cylinder 8 and the second cylinder 9 It is not possible to reduce the height dimension in the axial direction of the compressor just by reducing the height in the axial direction. In this case, the external appearance of the two-cylinder rotary compressor 100 is as shown in FIG. The effect of downsizing of the compressor and low vibration due to low center of gravity is not obtained.

In the two-cylinder rotary compressor 100, the height in the axial direction of the first cylinder 8 and the second cylinder 9 is reduced, but the first cylinder 8 and the second cylinder 9 are reduced. The center of the axial direction of is the same as in the case of FIG.

The position of the support base 7 rises rather than the case of FIG. 7, the partition plate 10 becomes thick, and the position of the main support 6 falls.

FIG. 9 is a diagram showing Embodiment 1 showing a connecting pipe 60 in the case where the suction pipe inserting portion 60b is made circular and the press-fitting portion 60a is made non-circular, and connected to the same flow path area. (a) is a hole long in a rotation direction, (b) is a hole long in an axial direction.

As shown in FIG. 9, when the suction pipe insertion part 60b of the connection pipe 60 is made circular, and the press-fit part 60a is made non-circular, and it connects to the same flow path area, it has a shaft diameter part and low pressure. Suction pressure loss due to flow path resistance of the fluid is not avoided.

Therefore, it is inevitable to select a circular shape having the smallest diameter as the rotation direction dimension (Fig. 9 (a)) of the non-circular suction cross-sectional shape, which is contrary to the reduction in the compressor axial dimension.

The effects of the present embodiment can be obtained not only in the two-cylinder rotary compressor 100 (FIG. 1) but also in the multi-cylinder compressor. In addition, even in the one-cylinder compressor, the effect of reducing the cylinder axial height and lowering the axial arrangement of the cylinders can be obtained, which makes the compressor compact and low vibration.

In addition, the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a non-circular cross-sectional shape, whereby the axes of the first cylinder 8 and the second cylinder 9 are reduced. Since the direction height can be made low, the compressed gas load acting on the eccentric shaft 4c or the eccentric shaft 4d of the crankshaft 4 can be reduced. Moreover, since the axial height of the 1st cylinder 8 and the 2nd cylinder 9 can be made low, the distance to the main bearing 6 or the secondary bearing 7 which becomes a support point of a compressed gas load is It becomes small and the curvature of the crankshaft 4 by a compressed gas load can be suppressed.

When the crankshaft 4 becomes large in curvature, the inclination of the crankshaft 4 with respect to the main bearing 6 or the secondary bearing 7 becomes large, and since the fall of the bearing reliability by a single contact arises, It is necessary to secure the rigidity of the crankshaft 4 corresponding to the crankshaft 4 bending.

However, as long as the curvature of the crankshaft 4 can be suppressed, a design change to reduce the rigidity of the crankshaft 4, such as reduction of the shaft diameter, can be made, thereby enabling the compressor to be more efficient by reducing the shaft sliding loss. .

FIG. 10: is a figure which shows Embodiment 1, and is a longitudinal cross-sectional view of the 2-cylinder rotary compressor 200 of the modification 1. As shown in FIG. The difference from the two-cylinder rotary compressor 100 is that the accumulator 20 is provided adjacent to the sealed container 1.

The accumulator 20 discharges the low pressure fluid from the accumulator 20 and the inlet pipe 21 for introducing the low pressure fluid of the refrigeration cycle into the accumulator 20, and the suction pipes 22 and 23 connected to the connecting pipes 60 and 61. ).

In the rotary compressor, it is preferable to attach the accumulator 20 for the purpose of gas-liquid separation of low pressure fluid coming from a refrigeration cycle, separation of lubricating oil (freezer base oil) contained in a small amount in the low pressure fluid, and noise reduction by a muffler effect.

Even when the accumulator 20 is attached, the suction pipes 22 and 23 have a non-circular cross section whose rotation direction is larger than the axial dimension of the crankshaft 4, thereby obtaining the same effect as the two-cylinder rotary compressor 100. Can be.

However, the cross-sectional shape of the introduction pipe 21 of the accumulator 20 is circular. The cross-sectional shape of the piping of the refrigerating cycle machine is circular, and by fitting the cross-sectional shape of the inlet pipe 21 into a circle, it satisfies the basic performance of the compressor that it can be easily mounted in various refrigeration cycle machines.

The low pressure fluid coming from the refrigeration cycle passes through the inlet tube 21 of the accumulator 20, once into the accumulator vessel 24, and then into the intake tubes 22, 23 after gas-liquid separation and lubricating oil are separated. do. Therefore, suction pressure loss does not occur by the difference in the cross-sectional shape of the introduction pipe 21 and the suction pipes 22 and 23.

FIG. 11: is a figure which shows Embodiment 1, and is a longitudinal cross-sectional view of the 2-cylinder rotary compressor 200 of the modification 1 (connecting pipe connection part 22a, 23a of suction pipe 22, 23 is a non-circular cross-sectional shape). .

The suction pipes 22 and 23 of the accumulator 20 may not be the same non-circular cross-sectional shape over the entire length, as long as the required flow path areas can be secured. As shown in FIG. 11, the connection pipe connection parts 22a and 23a of the suction pipes 22 and 23 may have a non-circular cross-sectional shape, and the accumulator insertion parts 22b and 23b may have a circular cross-sectional shape. By setting it as such a structure, it becomes possible to make common parts of the accumulator container 24 and the model in which the suction pipes 22 and 23 are circular.

In addition, the suction pipes 22 and 23 may not be the same component over the whole length. The suction pipes 22 and 23 are generally selected from a copper material having good weldability and bend formability. Considering the recent market price improvement of the copper material, it is also possible to reduce the cost by replacing the circular cross-sectional portions of the accumulator insertion portions 22b and 23b of the suction pipes 22 and 23 with more inexpensive materials.

The non-circular cross-sectional shapes of the suction ports 50 and 51, the suction pipes 40 and 41 (connecting pipe connecting portions 22a and 23a), and the connecting pipes 60 and 61 are oval, long, and connecting circle. Or any of the shapes formed by connecting two circles in a short diameter, the axial height can be reduced with respect to the circular cross-sectional shape, so that the suction ports 50 and 51 and the suction pipes 40 and 41 ( It is possible to select appropriately in consideration of the processability, moldability, etc. of the connection pipe | tube connection part 22a, 23a), the connection pipes 60, 61, and the like.

12 and 13 show a first embodiment, and FIG. 12 shows a connection pipe when the suction port 50 and the press fitting portion 60a of the connection pipe 60 of the long hole are press-fitted. Schematic diagram which shows the direction of the internal stress of 60, FIG. 13 is a schematic diagram which shows one deformation | transformation form of the press fitting part 60a of the connection pipe 60. As shown in FIG.

As shown in FIG. 12, FIG. 13, when the long hole member is press-fitted, the internal stress which generate | occur | produced in the circular arc part 60d is transmitted to the flat part 60c, and the flat part 60c may deform | transform the inner peripheral side. There is. When the flat part 60c deforms to the inner circumferential side, the high pressure atmosphere refrigerant gas in the airtight container 1 flows into the suction chamber 30a due to the decrease in the press-fit sealability of the connecting pipe 60, and the compressor There exists a possibility of causing a fall of efficiency.

FIG. 14: is a figure which shows Embodiment 1, and is sectional drawing of the press fitting part 60a of the connection pipe 60. As shown in FIG. The press-fitting part 60a of the connecting pipe 60 shown in FIG. 14 has a cross-sectional shape as a long hole, and the flat part which connected two circles of the long hole with a suction port 50 is carried out. The convex shape 60e is made to the outer circumferential side within the range of.

Since the press-in part 60a of the connecting pipe 60 made the flat part a convex shape 60e to the outer peripheral side, the internal stress generated in the arc part 60d by the press-in deformation deforms the convex shape 60e of the flat part to the outer peripheral side. Since it is conveyed in the direction to make it, it becomes possible to obtain the connection pipe 60 without the indentation seal | sticker property fall, without deforming a flat part to an inner peripheral side.

As a method of directing the direction of the internal stress transmitted to the flat portion 60c to the outer circumferential side, it is possible to make the cross-sectional shape an ellipse. The direction of rotation becomes large with respect to this long hole.

FIG. 15 is a diagram showing Embodiment 1 and illustrates a compression process angle θ determined by the suction port edge 50b and the discharge port edge 70a.

When the rotation direction dimension of the suction port 50 becomes large, as shown in FIG. 15, the suction port edge 50b (Y point, the edge of the opposite side to the 1st vane 5a), and the discharge port 70 are discharged. Since the compression process angle θ determined by the port edge 70a (Z point, the opposite edge of the first vane 5a) decreases, and the exclusion volume decreases, the press-fit seal of the connector The embodiment (long hole) without a decrease in sealability or a decrease in exclusion volume is the best choice.

By the way, as the object of the global environment in the air conditioner to operate a refrigerating cycle by a two-cylinder rotary compressor according to the present embodiment by using a refrigerant (100, 200), protection of the ozone layer, global warming (CO ₂ such as discharge Suppression), energy saving, and resource reuse (recycling).

Among the issues related to the global environment, in the ozone layer protection, the air used for switching the refrigerant used from R22 (HFC22) having a high ozone destruction coefficient to R410A (HFC32: HFC125 = 50: 50 (weight ratio)) having a zero ozone destruction coefficient is zero. The harmonizer is already commercialized. HFC125 is represented by the chemical formula CHF ₂ -CF ₃ (chemical name pentafluoroethane).

On the other hand, demand for global warming prevention measures has increased increasingly. In air conditioners, it is assessed using indicators of global warming called Total Equivalent Warming Impact (TEWI). This TEWI is expressed as the sum of the effects of the refrigerant's release into the air (direct effect), the energy consumption of the device (indirect effect), and the CO ₂ emitted to produce the energy consumed when manufacturing the materials constituting the air conditioner. do.

The calculation of TEWI uses the Global Warming Potential (GWP), the amount of refrigerant, and the Annual Performance Factor (APF), which represents the efficiency of the air conditioner. In order to prevent global warming, it is necessary to select a refrigerant having a small GWP value and a large APF value in order to reduce the value of TEWI.

The GWP of the R410A currently used is 2090, which is larger than the 1810 of the R22 that was conventionally used. Therefore, in order to prevent global warming, a refrigerant having a GWP value of zero has been developed as a hydrocarbon based R290, a low GWP refrigerant having a GWP of 50 or less, HFO1234yf, etc. R32 (HFC32) is mentioned as a candidate.

The GWP value of this R32 is 675, which is about 1/3 compared to the GWP values of R22 and R410A, which can reduce the impact on global warming, but it is not a low GWP refrigerant compared to R290 or HFO1234yf. , When R32 is used, it is necessary to reduce the amount of refrigerant.

Regarding energy saving, since CO ₂ is indirectly emitted by electric power consumption when the air conditioner is operated, it contributes to the prevention of global warming by increasing the performance of the air conditioner to save energy.

In the home air conditioner, since the ratio of indirect CO ₂ emissions due to power consumption at the time of use is large, it can be linked to the reduction of CO ₂ emissions by promoting energy saving. In the case of using R32 as the refrigerant, since it is not a low GWP refrigerant as described above, it is necessary to reduce the amount of refrigerant and to save energy at the same time in order to reduce the influence on global warming.

1: sealed container
1a: torso
1b: Sangmyung Container
1c: Class name container
1d: connection
1e: Connection
2: electric motor
2a: stator
2b: rotor
3: compression mechanism
4: crankshaft
4a: spindle
4b: minor shaft
4c: eccentric shaft
4d: eccentric shaft
5a: first vane
6: spindle support
7: support
8: first cylinder
8b: vane groove
9: the second cylinder
10: partition plate
11a: first piston
11b: second piston
11c: outsourcing
20: accumulator
22: suction pipe
22a: connector connection
23: suction pipe
23a: connector connection
25: discharge tube
26: glass terminal
27: lead wire
30: thread
30a: suction chamber
30b: compression chamber
31: thread
31a: suction chamber
31b: compression chamber
40: suction pipe
41: suction pipe
50: suction port
50a: indentation import unit
50b: suction port fringing
51: suction port
51a: indentation import unit
60 connector
60a: indentation
60b: suction tube insert
60c: flat part
60d: arc
60e: convex shape
61: connector
61a: indentation part
61b: suction tube insert
70 discharge port
70a: discharge port edge
100: 2 cylinder rotary compressor
200: two cylinder rotary compressor

Claims (5)

A compression mechanism driven by an electric motor through a crankshaft in a sealed container,
The compression mechanism
A cylinder having a cylindrical inner space and a suction port for sucking low pressure fluid of a refrigeration cycle into the inner space;
And a connecting pipe connecting the suction port and the suction pipe outside the sealed container,
And a cross-sectional shape of the suction port, the connecting pipe, and the suction pipe is a non-circular shape having a larger rotation direction dimension than the axial dimension of the crankshaft. The method of claim 1,
An accumulator and an introduction tube for introducing low pressure fluid into the accumulator and the suction tube for discharging the low pressure fluid from the accumulator and connected to the connecting tube,
And a cross-sectional shape of the suction pipe is a non-circular shape having a larger rotation direction dimension than an axial dimension of the crankshaft, and a cross-sectional shape of the introduction pipe is a circular shape. The method of claim 1,
An accumulator and an introduction tube for introducing low pressure fluid into the accumulator and the suction tube for discharging the low pressure fluid from the accumulator and connected to the connecting tube,
The cross-sectional shape of the connection pipe connecting portion of the suction pipe is a non-circular shape having a rotational dimension larger than the axial dimension of the crankshaft, the cross-sectional shape of the accumulator insertion portion of the suction pipe is circular, and the cross-sectional shape of the introduction pipe is circular. Rotary compressor, characterized in that. 4. The method according to any one of claims 1 to 3,
The non-circular cross-sectional shape is any one of a shape formed by connecting an ellipse, a manor, a connecting circle, or two circles in a short diameter. 4. The method according to any one of claims 1 to 3,
A non-circular cross-sectional shape of the connecting pipe press-fitted into the suction port is a long hole, and a flat portion connecting two circles of the long hole is convex toward the outer circumference in the range of the suction port and the press-fitting band of the connecting pipe. Rotary compressor, characterized in that.

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