JP2020084821A - Rotary compressor - Google Patents

Abstract

To provide a rotary compressor capable of restraining deterioration of efficiency of a compressor due to refrigerant leakage.SOLUTION: A rotary compressor includes a compression mechanism part with a 2-cylinder constitution, in which first and second pistons are respectively swung along inner peripheral walls (200A) of first and second cylinder chambers (22A) formed in first and second cylinders (21A). In the compression mechanism part, the blade hole (100) has an opening (100a) on a side of the first cylinder chamber (22A). In a plane view, an angle α1 formed by a straight line (L2) passing through a center point (O1) of the first cylinder chamber (22A) and center points (P1) of two ends (200Aa, 200Ab) communicated with the blade hole (100) of an inner peripheral wall (200A) of the first cylinder chamber (22A) and a center shaft (L1b) of a second passage part (101b), and an angle formed by the straight line (L2) and a center shaft of a second suction passage are smaller than an angle β formed by the straight line (L2) and the center shaft (L1a) of the first passage part (101a).SELECTED DRAWING: Figure 5

Description

Regarding rotary compressor.

2. Description of the Related Art Conventionally, some rotary compressors include a compression mechanism section having two cylinders arranged side by side with a partition plate in between and a piston that eccentrically rotates in each cylinder (for example, Japanese Patent Laid-Open No. 9-250477). Japanese Patent Publication (Patent Document 1)).

In the rotary compressor, the partition plate is provided with a suction passage communicating with the suction port of each cylinder, and the refrigerant is sucked into each cylinder from the suction pipe through the suction passage of the partition plate.

JP-A-9-250477

By the way, in the above rotary compressor, there is a sealing surface between the suction holes and the blade holes through which the blades advance and retreat on both end faces of the partition plate. In the above rotary compressor, since the seal length of the sealing surface cannot be sufficiently secured, there is a problem that refrigerant leakage occurs, volume efficiency is reduced, and the efficiency of the compressor is reduced.

The present disclosure proposes a rotary compressor that can suppress a decrease in compressor efficiency due to refrigerant leakage.

The rotary compressor of the present disclosure,
A first cylinder, a partition plate, and a second cylinder are laminated in order, and first and second cylinder chambers defined by an inner peripheral wall are formed in the first and second cylinders, and the first and second cylinders are formed. The first and second pistons are respectively provided with a compression mechanism portion of a two-cylinder configuration in which the first and second pistons make a rotational movement along the inner peripheral wall of the chamber (22A, 22B),
The compression mechanism section,
Blades for partitioning the first and second cylinder chambers into a high pressure side and a low pressure side, respectively,
Blade holes provided in the first and second cylinders so as to be connected to the first and second cylinder chambers, respectively, so as to support the blades so that they can move forward and backward,
A first suction passage that is circumferentially spaced from the blade hole of the first cylinder and extends in the radial direction;
An intake communication passage extending from the first intake passage of the first cylinder to the second cylinder through the partition plate;
The second cylinder has a second suction passage having a straight central axis extending in the radial direction so as to connect the suction communication passage and the second cylinder chamber,
The first suction passage of the first cylinder has a first passage portion whose one end is open to the outside and has a straight central axis, and one end of which is connected to the other end side of the first passage portion. Has a second passage portion having a straight central axis with the other end opening toward the center point of
In a plan view, a straight line passing through the center point of the first cylinder chamber and the center points of two ends of the inner peripheral wall of the first cylinder chamber that are continuous with the blade hole, and the center axis of the second passage portion. And an angle α2 formed by the straight line and the central axis of the second suction passage are smaller than an angle β formed by the straight line and the central axis of the first passage portion.

According to the present disclosure, due to refrigerant leakage, the angular range of the opening of the first suction passage that opens into the first cylinder chamber and the angular range of the opening of the second suction passage that opens into the second cylinder chamber are not increased. The decrease in compressor efficiency can be suppressed.

Further, in the rotary compressor according to one aspect of the present disclosure,
The second passage portion of the first cylinder is a groove provided on the partition plate side of the first cylinder.

According to the present disclosure, the second passage portion is formed by providing the groove on the partition plate side of the first cylinder, so that the first cylinder can be easily processed.

Further, in the rotary compressor according to one aspect of the present disclosure,
The second suction passage of the second cylinder is a groove provided on the partition plate side of the second cylinder.

According to the present disclosure, since the second suction passage is formed by providing the groove on the partition plate side of the second cylinder, the second cylinder can be easily processed.

Further, in the rotary compressor according to one aspect of the present disclosure,
The passage cross-sectional area of the second passage portion of the first cylinder is smaller than the passage cross-sectional area of the first passage portion.

According to the present disclosure, the wall thickness of the second passage portion of the first suction passage and the blade hole can be increased, and the thickness of the second suction passage and the blade hole can be increased.

Further, in the rotary compressor according to one aspect of the present disclosure,
The first cylinder is a lower cylinder that is stacked below the partition plate.

Further, in the rotary compressor according to one aspect of the present disclosure,
The second passage portion of the first cylinder is provided such that the central axis of the second passage portion passes through the center point of the first cylinder chamber.

According to the present disclosure, the angle range of the suction port of the first suction passage opening to the first cylinder chamber can be minimized.

It is a longitudinal section of a rotary compressor of a 1st embodiment of this indication. It is a top view of the principal part of the compression mechanism part of the rotary compressor. It is a top view of the principal part of the said compression mechanism part. It is a longitudinal cross-sectional view of the said compression mechanism part. It is a top view of the 1st cylinder of the said compression mechanism part. It is a top view of the 2nd cylinder of the said compression mechanism part. It is a figure explaining the angle range of the suction port of the 1st cylinder of the above-mentioned compression mechanism part. It is a figure explaining the angle range of the suction port of the 1st cylinder of a comparative example. It is a longitudinal section of a compression mechanism part of a rotary compressor of a 2nd embodiment of this indication. It is a longitudinal section of a compression mechanism part of a rotary compressor of a 3rd embodiment of this indication.

Hereinafter, embodiments will be described. In the drawings, the same reference numerals represent the same or corresponding parts. Further, dimensions such as length, width, thickness, and depth on the drawing are appropriately changed from an actual scale for the sake of clarity and simplification of the drawing, and do not represent actual relative dimensions.

[First Embodiment]
FIG. 1 is a vertical sectional view of a rotary compressor according to a first embodiment of the present disclosure.

As shown in FIG. 1, the compressor according to the first embodiment includes a closed container 1, a compression mechanism portion 2 arranged in the closed container 1, a compression mechanism portion 2 arranged in the closed container 1, and a compression mechanism portion 2. The motor 3 driven via the rotating shaft 12 is provided.

This rotary compressor is a two-cylinder oscillating piston compressor. In the rotary compressor, the compression mechanism section 2 is arranged on the lower side in the closed container 1, and the motor 3 is arranged on the upper side of the compression mechanism section 2. The motor 3 has an annular stator 4 fixed to the inside of the closed casing 1, and a rotor 5 arranged inside the stator 4 and fixed to the rotating shaft 12. The rotation of the rotor 5 drives the compression mechanism section 2 via the rotary shaft 12.

The compression mechanism unit 2 sucks the refrigerant gas from the accumulator 10 via the suction pipe 11. This refrigerant gas is obtained by controlling, together with this rotary compressor, a condenser, an expansion mechanism, and an evaporator (not shown) that form an air conditioner as an example of a refrigeration system.

The rotary compressor discharges the compressed high-temperature and high-pressure refrigerant gas (discharge gas) from the compression mechanism unit 2 to fill the inside of the closed container 1 and passes through the gap between the stator 4 and the rotor 5 of the motor 3. After cooling the motor 3, the discharge pipe 13 provided on the upper side of the motor 3 discharges it to the outside.

An oil reservoir 9 in which lubricating oil is reserved is formed below the high-pressure region in the closed container 1. This lubricating oil moves from the oil sump portion 9 to the sliding portion of the compression mechanism portion 2 through the oil passage 80 provided in the rotary shaft 12, and lubricates the sliding portion.

The compression mechanism 2 includes a front head 50 attached to the inner surface of the closed container 1, a second cylinder 21B attached to the lower side of the front head 50, and a partition attached to the lower side of the second cylinder 21B. And a plate 60. The second cylinder 21B, the front head 50, and the partition plate 60 form a second cylinder chamber 22B (shown in FIG. 2). The front head 50 is an example of an end plate.

The compression mechanism section 2 also includes a first cylinder 21A attached to the lower side of the partition plate 60, and a rear head 70 attached to the lower side of the first cylinder 21A. The first cylinder 21A, the partition plate 60, and the rear head 70 form a first cylinder chamber 22A (shown in FIG. 3). The rear head 70 is an example of an end plate.

The first cylinder 21A is a lower cylinder stacked below the partition plate 60, and the second cylinder 21B is an upper cylinder stacked above the partition plate 60.

FIG. 2 is a top view of the second cylinder 21B and the second piston 29B of the compression mechanism section 2. In FIG. 2, 110B is a through hole provided in the second cylinder 21B in the axial direction. The fastening bolt 44 (shown in FIG. 4) is inserted into the through hole 110B. A second cylinder chamber 22B defined by the inner peripheral wall 200B is formed inside the second cylinder 21B.

As shown in FIG. 2, this rotary compressor includes a second piston 29B in which a roller 27B and a blade 28B are integrally formed, and a second piston 29B sandwiched between a front head 50 and a partition plate 60 (shown in FIG. 1). The second piston 29B swings in the cylinder 21B. The inside of the second cylinder chamber 22B is partitioned by the blade 28B of the second piston 29B. That is, the suction chamber 22Ba is formed on the right side of the blade 28B, and the compression chamber 22Bb is formed on the left side of the blade 28B. The second piston 29B is divided into a high pressure side and a low pressure side by the blade 28B.

A suction pipe 11 (shown in FIG. 1) is connected to a second suction passage 103 formed in the second cylinder 21B via a suction communication passage 102 and a first suction passage 101 (shown in FIG. 3). .. The suction port 103a of the second suction passage 103 opens into the second cylinder chamber 22B. On the other hand, the discharge port 62B formed in the second cylinder 21B opens to the inner surface of the second cylinder chamber 22B.

The space between the blade 28B and the swing bushes 25B, 25B is lubricated with lubricating oil. The blades 28B are sandwiched from both sides by swinging bushes 25B, 25B and supported so as to be able to move forward and backward. The blade 28B appears and disappears in the back space 90B provided in the second cylinder 21B.

Then, the eccentric portion 26B is eccentrically rotated with the clockwise rotation of the rotary shaft 12, and the roller 27B fitted to the eccentric portion 26B causes the outer peripheral surface of the roller 27B to become the inner peripheral wall 200B of the second cylinder chamber 22B. Revolve while touching.

As the roller 27B revolves in the second cylinder chamber 22B, a low-pressure refrigerant gas is sucked into the suction chamber 22Ba from the suction port 103a, compressed in the compression chamber 22Bb to a high pressure, and then discharged from the discharge port 62B. Discharge high-pressure refrigerant gas.

After that, the refrigerant gas discharged from the discharge port 62B is discharged to the outside of the muffler covers 41 and 42 shown in FIG.

FIG. 3 is a top view of the first cylinder 21A and the first piston 29A of the compression mechanism section 2. In FIG. 3, 110A is a through hole provided in the first cylinder 21A in the axial direction. The fastening bolt 44 (shown in FIG. 4) is inserted into the through hole 110A. A first cylinder chamber 22A defined by the inner peripheral wall 200A is formed in the first cylinder 21A.

As shown in FIG. 3, this rotary compressor includes a first piston 29A in which a roller 27A and a blade 28A are integrally formed, and a first cylinder sandwiched by a partition plate 60 and a rear head 70 (shown in FIG. 1). The first piston 29A swings within 21A. The inside of the first cylinder chamber 22A is partitioned by the blade 28A of the first piston 29A. That is, the suction chamber 22Aa is formed on the right side of the blade 28A, and the compression chamber 22Ab is formed on the left side of the blade 28A. The first piston 29A is divided into a high pressure side and a low pressure side by the blade 28A.

The suction pipe 11 (shown in FIG. 1) is connected to the first suction passage 101 formed in the first cylinder 21A, and the suction port 101c of the first suction passage 101 is open to the first cylinder chamber 22A. . On the other hand, the discharge port 62A formed in the first cylinder 21A is open to the inner surface of the first cylinder chamber 22A.

The space between the blade 28A and the swing bushes 25A, 25A is lubricated with lubricating oil. The blades 28A are sandwiched from both sides by the swinging bushes 25A, 25A so as to be capable of advancing and retracting. The blade 28A appears and disappears in the back space 90A provided in the first cylinder 21A.

Then, the eccentric portion 26A is eccentrically rotated with the clockwise rotation of the rotary shaft 12, and the roller 27A fitted to the eccentric portion 26A causes the outer peripheral surface of the roller 27A to move to the inner peripheral wall 200A of the first cylinder chamber 22A. Revolve while touching.

As the roller 27A revolves in the first cylinder chamber 22A, low-pressure refrigerant gas is sucked into the suction chamber 22Aa from the suction port 101c, compressed in the compression chamber 22Ab to a high pressure, and then discharged from the discharge port 62A. Discharge high-pressure refrigerant gas.

After that, the refrigerant gas discharged from the discharge port 62A is discharged to the outside of the muffler covers 41 and 42 shown in FIG.

As shown in FIGS. 2 and 3, the first piston 29A has a blade 28A and a roller 27A formed integrally, and the second piston 29B has a blade 28B and a roller 27B formed integrally. Further, the blade holes 100 of the first and second cylinders 21A and 21B are bush holes provided in the first and second cylinders 21A and 21B so as to be continuous with the first and second cylinder chambers 22A and 22B. Swing bushes 25A, 25B that support the blades 28A, 28B swingably and reciprocally are disposed in the blade hole 100 that is the bush hole.

FIG. 4 is a vertical sectional view of the compression mechanism section 2. In FIG. 4, 44 is a fastening bolt for fastening the front head 50, the second cylinder 21B, the partition plate 60, the first cylinder 21A, and the rear head 70.

As shown in FIG. 4, the front head 50 has a disk-shaped main body portion 51 and a boss portion 52 provided upward in the center of the main body portion 51. The rotary shaft 12 is inserted through the main body 51 and the boss 52.

The main body portion 51 is provided with a discharge port 62B (shown in FIG. 2) communicating with the second cylinder chamber 22B. A discharge valve (not shown) is attached to the main body 51 such that the main body 51 is located on the opposite side of the second cylinder 21B. This discharge valve is a reed valve whose valve element is a leaf spring, and opens and closes the discharge port 62B.

Cup-shaped muffler covers 41 and 42 are attached to the upper side of the main body 51 so as to cover the discharge valve. The muffler covers 41, 42 are fixed to the main body 51 by bolts 43 or the like. A boss portion 52 is inserted through the muffler covers 41, 42. A muffler chamber is formed by the muffler covers 41 and 42 and the front head 50.

Further, the rear head 70 has a disc-shaped main body portion 71 and a boss portion 72 provided downward at the center of the main body portion 71. The rotary shaft 12 is inserted through the main body 71 and the boss 72.

The main body 71 is provided with a discharge port 62A (shown in FIG. 3) communicating with the first cylinder chamber 22A. A discharge valve (not shown) is attached to the main body portion 71 so as to be located on the opposite side of the main body portion 71 from the first cylinder 21A. This discharge valve is a reed valve whose valve element is a leaf spring and opens and closes the discharge port 62A.

A plate-shaped muffler cover 73 is attached to the lower side of the main body 71 so as to cover the discharge valve.

One end of the rotary shaft 12 is supported by the front head 50 and the rear head 70. One end portion (support end side) of the rotary shaft 12 is inserted into the inside of the first and second cylinder chambers 22A and 22B.

Eccentric portions 26A and 26B are provided on the support end side of the rotating shaft 12 so as to be located inside the first and second cylinder chambers 22A and 22B on the compression mechanism 2 side. The rotary shaft 12 and the eccentric portions 26A and 26B form a crankshaft. The eccentric portion 26A is fitted to the roller 27A of the first piston 29A, and the eccentric portion 26B is fitted to the roller 27B of the second piston 29B. The first and second pistons 29A and 29B are revolvably arranged in the first and second cylinder chambers 22A and 22B, respectively, and the first and second pistons 29A and 29B revolve to perform a compression action.

The compression mechanism unit 2 includes a front head 50, a second cylinder 21B, a partition plate 60, a first cylinder 21A, and a rear head 70, which are sequentially stacked, and is rotated by a crankshaft having eccentric portions 26A and 26B to rotate the first head. The first and second pistons 29A and 29B are swiveled along the inner peripheral walls 200A and 200B of the first and second cylinder chambers 22A and 22B formed in the first and second cylinders 21A and 21B, respectively.

Further, the compression mechanism portion 2 includes a first suction passage 101 extending in a radial direction at a circumferential interval from a blade hole 100 (shown in FIG. 3) of the first cylinder 21A, and a first cylinder 21A of the first cylinder 21A. A suction communication passage 102 extending from the first suction passage 101 to the second cylinder 21B through the partition plate 60, and a first suction passage 102 extending in the radial direction of the second cylinder 21B so as to communicate the suction communication passage 102 and the second cylinder chamber 22B. 2 suction passages 103.

The first suction passage 101 has a large-diameter connection portion on the inlet side to which the suction pipe 11 is connected. Further, the suction communication passage 102 is provided so as to penetrate the first cylinder 21A in the axial direction. The second suction passage 103 may be a groove provided on the partition plate 60 side of the second cylinder 21B.

Next, the first suction passage 101, the suction communication passage 102, and the second suction passage 103 provided in the first cylinder 21A and the second cylinder 21B will be described with reference to FIGS. FIG. 5 is a top view of the first cylinder 21A.

As shown in FIG. 5, in plan view, the first suction passage 101 of the first cylinder 21A includes a first passage portion 101a having a straight central axis with one end open to the outside, and the first passage portion 101a. Has a second passage portion 101b whose one end is connected to the other end side and whose central axis is linear toward the center point O1 of the first cylinder chamber 22A and whose other end side is open.

The central axis of the first passage portion 101a of the first suction passage 101 is set to L1a, and the center point of the two ends 200Aa and 200Ab connected to the blade hole 100 of the inner peripheral wall 200A of the first cylinder chamber 22A is set to P1. A straight line passing through the center point P1 and the center point O1 of the first cylinder chamber 22A is defined as L2. The intersection P2 of the central axis L1a and the straight line L2 is located closer to the blade hole 100 than the central point O1 of the first cylinder chamber 22A.
Here, the two ends 200Aa and 200Ab are connection positions between the inner peripheral wall 200A of the first cylinder chamber 22A and the inner peripheral wall of the blade hole 100 that is continuous with the inner peripheral wall 200A.

When the central axis of the second passage portion 101b of the first suction passage 101 in the first cylinder 21A is L1b, the angle α1 between the straight line L2 and the central axis L1b is smaller than the angle β between the straight line L2 and the central axis L1a. Is also small.

Similarly, when the central axis of the second suction passage 103 in the second cylinder 21B is L3 as shown in FIG. 6, the angle α2 between the straight line L2 and the central axis L3 is the straight line L2 and the first α shown in FIG. It is smaller than the angle β with the central axis L1a of the passage portion 101a.

This allows the partition plate 60 to pass through the partition plate 60 from the first suction passage 101 of the first cylinder 21A at the sealing surface between the first cylinder 21A and the partition plate 60 and the sealing surface between the second cylinder 21B and the partition plate 60. It is possible to secure a seal length X between the suction communication passage 102 extending to the second cylinder 21B and the blade hole 100 of the first and second cylinders 21A and 21B.

As shown in FIG. 7, in the suction port 101c of the first cylinder 21A of the compression mechanism unit 2, the central axis L1b of the second passage portion 101b of the first suction passage 101 passes through the center point O1 of the first cylinder chamber 22A. Therefore, the angle range θ1 of the suction port 101c viewed from the center point O1 of the first cylinder chamber 22A can be minimized.

On the other hand, in the comparative example shown in FIG. 8, a first suction passage 201 having a straight central axis L1a extending from the blade hole 100 of the first cylinder 21A in the circumferential direction and extending in the radial direction, and the first cylinder 21A, a suction communication passage 202 extending from the first suction passage 201 to the second cylinder 21B through the partition plate 60, and a second cylinder 21B extending in the radial direction so as to communicate the suction communication passage 202 and the second cylinder chamber 22B. An existing second suction passage (not shown). In the suction port 201c of the first cylinder 21A, an intersection P2 between the central axis L1a of the first suction passage 201 and the straight line L2 is located closer to the blade hole 100 than the central point O1 of the first cylinder chamber 22A.

In this case, in the angular range θ2 of the intake port 201c viewed from the center point O1 of the first cylinder chamber 22A, the center axis L1b of the second passage portion 101b shown in FIG. 7 passes through the center point O1 of the first cylinder chamber 22A. It becomes larger than the angle range θ1 of the suction port 101c.

In the comparative example shown in FIG. 8, since the central axis L1a of the first suction passage 201 does not face the center point O1 of the first cylinder chamber 22A, the angular range θ2 of the suction port 201c of the first cylinder 21A is widened and the suction closed. The volume of the suction chamber 22Aa at the cut position is reduced, the volumetric efficiency is reduced, and the efficiency of the compressor is reduced.

On the other hand, in the rotary compressor of the first embodiment, since the central axis L1b of the second passage portion 101b of the first suction passage 101 faces the central point O1 of the first cylinder chamber 22A, the above-mentioned comparative example. Compared with the above, the volume of the suction chamber 22Aa at the suction closed position can be suppressed from decreasing without expanding the angular range θ1 of the suction port 101c of the first cylinder 21A.

As described above, in the swing cylinder type rotary compressor having the two-cylinder configuration, the angular range of the suction port 101c of the first suction passage 101 opening to the first cylinder chamber 22A and the second opening to the second cylinder chamber 22B. A decrease in compressor efficiency due to refrigerant leakage can be suppressed without expanding the angular range of the suction port 103a of the suction passage 103.

Further, since the second passage portion 101b of the first cylinder 21A is provided such that the central axis of the second passage portion 101b passes through the center point O1 of the first cylinder chamber 22A, the first cylinder chamber 22A. The angle range of the suction port 101c of the first suction passage 101 opening to the bottom can be minimized.

[Second Embodiment]
FIG. 9 is a vertical cross-sectional view of the compression mechanism unit 2 of the rotary compressor according to the second embodiment of the present disclosure. The rotary compressor of the second embodiment has the same configuration as the rotary compressor of the first embodiment except for the first suction passage 301, the suction communication passage 302, and the second suction passage 303. Incorporate.

In the rotary compressor of the second embodiment described above, the compression mechanism portion 2 includes the first suction passage which is circumferentially spaced from the blade hole 100 (shown in FIG. 3) of the first cylinder 21A and extends in the radial direction. 301, a suction communication passage 302 extending from the first suction passage 301 of the first cylinder 21A through the partition plate 60 to the second cylinder 21B, and a second cylinder so that the suction communication passage 302 communicates with the second cylinder chamber 22B. 21B has a second suction passage 303 extending in the radial direction.

In addition, the first intake passage 301 of the first cylinder 21A has a first passage portion 301a whose one end is open to the outside, and one end of which is connected to the other end side of the first passage portion 301a. It has the 2nd passage part 101b which the other end side opens toward the point O1.

The second passage portion 301b of the first cylinder 21A is a groove provided on the partition plate 60 side of the first cylinder 21A.

The second suction passage 303 of the second cylinder 21B is a groove provided on the partition plate 60 side of the second cylinder 21B.

The first suction passage 301, the suction communication passage 302, and the second suction passage 303 are the same as the first suction passage 101 of the first embodiment except that the second passage portion 301b and the second suction passage 303 are grooves. It has the same structure as the suction communication passage 102 and the second suction passage 103.

The rotary compressor of the second embodiment has the same effects as the rotary compressor of the first embodiment.

Further, since the second passage portion 301b of the first suction passage 301 is formed by providing the groove on the partition plate 60 side of the first cylinder 21A, the first cylinder 21A can be easily processed.

Further, since the second suction passage 303 is formed by providing the groove on the partition plate 60 side of the second cylinder, the second cylinder 21B can be easily processed.

[Third Embodiment]
FIG. 10 is a vertical cross-sectional view of the compression mechanism unit 2 of the rotary compressor according to the third embodiment of the present disclosure. The rotary compressor of the second embodiment has the same configuration as the rotary compressor of the first embodiment except for the first suction passage 401, the suction communication passage 402, and the second suction passage 403. Incorporate.

As shown in FIG. 10, the compression mechanism unit 2 includes a first suction passage 401 that is circumferentially spaced from the blade hole 100 (shown in FIG. 3) of the first cylinder 21A and extends in the radial direction, and A suction communication passage 402 extending from the first suction passage 401 of the one cylinder 21A through the partition plate 60 to the second cylinder 21B, and a radial direction of the second cylinder 21B so as to communicate the suction communication passage 402 and the second cylinder chamber 22B. And a second suction passage 403 having a central axis that is linear.

The first suction passage 401 of the first cylinder 21A has a first passage portion 401a whose one end is open to the outside and has a straight central axis, and one end of which is connected to the other end side of the first passage portion 401a. It has a second passage portion 401b whose central axis is linear and whose other end side is open toward the center point O1 of the chamber 22A.

The first suction passage 401, the suction communication passage 402, and the second suction passage 403 have the same configuration as the first suction passage 101, the suction communication passage 102, and the second suction passage 103 of the first embodiment except for the passage cross-sectional area. Are doing

The first passage portion 401a of the first suction passage 401 has a circular sectional shape with an inner diameter r1 on the downstream side, and the second passage portion 401b and the second suction passage 403 have a circular sectional shape with an inner diameter r1. ..

here,
r1> r2 (1)
Is. From the above formula (1),
π(r1) ² > π(r2) ² (2)
And the passage cross-sectional area of the second passage portion 401b of the first cylinder 21A is S1 and the passage cross-sectional area of the first passage portion 401a and the second suction passage 403 is S2, from the above formula (2),
S1> S2 (3)
The relationship is established.

As described above, in the rotary compressor configured as described above, the passage cross-sectional area S1 of the second passage portion 401b of the first cylinder 21A is smaller than the passage cross-sectional area S2 of the first passage portion 401a and the second suction passage 403. .

Accordingly, by reducing the passage cross-sectional area after branching from the first passage portion 401a to the second passage portion 401b, it is possible to increase the thickness of the second passage portion 401b and the blade hole 100. Similarly, the wall thickness between the second suction passage 403 and the blade hole 100 is reduced by reducing the passage cross-sectional area after branching from the first passage portion 401a to the second suction passage 403 via the suction communication passage 402. You can earn.

The rotary compressor of the third embodiment has the same effects as the rotary compressor of the first embodiment.

In the first to third embodiments described above, the compression mechanism unit 2 having the first piston 29A in which the blade 28A and the roller 27A are integrally formed and the second piston 29B in which the blade 28B and the roller 27B are integrally formed is provided. Although the rotary compressor provided has been described, the present invention may be applied to a rotary compressor having a two-cylinder configuration including a compression mechanism section having a first piston and a second piston, which are separate blades and rollers.

Although specific embodiments of the present disclosure have been described, the present disclosure is not limited to the above-described first to third embodiments, and various modifications can be implemented within the scope of the present disclosure.

DESCRIPTION OF SYMBOLS 1... Airtight container 2... Compression mechanism part 3... Motor 4... Stator 5... Rotor 9... Oil sump part 11... Suction pipe 12... Rotation shaft 13... Discharge pipe 21A... 1st cylinder 21B... 2nd cylinder 22A... 1st cylinder Chamber 22Aa... Suction chamber 22Ab... Compression chamber 22B... Second cylinder chamber 22Ba... Suction chamber 22Bb... Compression chamber 25B, 25B... Oscillating bushes 26A, 26B... Eccentric portions 27A, 27B... Rollers 28A, 28B... Blades 29A... First Piston 29B...Second piston 41,42...Muffler cover 43...Bolt 44...Fastening bolt 50...Front head (end plate)
51... Main body part 52... Boss part 62A, 62B... Discharge port 60... Partition plate 70... Rear head (end plate)
71... Body part 72... Boss part 73... Muffler cover 80... Oil passage 90A, 90B... Rear space 100... Blade hole 101... First suction passage 101a... First passage portion 101b... Second passage portion 101c... Suction port 102... Intake communication passage 103... Second suction passage 103a... Intake port 200A, 200B... Inner peripheral wall 200Aa, 200Ab... End

Claims (6)

The first cylinder (21A), the partition plate (60), and the second cylinder (21B) are sequentially stacked, and are defined by the inner peripheral walls (200A, 200B) in the first and second cylinders (21A, 21B). First and second cylinder chambers (22A, 22B) are formed, and the first and second pistons (29A) are formed along the inner peripheral walls (200A, 200B) of the first and second cylinder chambers (22A, 22B). , 29B) is provided with a compression mechanism section (2) having a two-cylinder structure that makes a swivel motion,
The compression mechanism section (2) is
Blades (28A, 28B) for partitioning the first and second cylinder chambers (22A, 22B) into a high pressure side and a low pressure side, respectively,
Blades which are provided in the first and second cylinders (21A, 21B) so as to be connected to the first and second cylinder chambers (22A, 22B), respectively, so as to support the blades (28A, 28B) so as to be movable back and forth. A hole (100),
A first suction passage (101) which is circumferentially spaced from the blade hole (100) of the first cylinder (21A) and extends in the radial direction;
An intake communication passage (102) extending from the first intake passage (101) of the first cylinder (21A) to the second cylinder (21B) through the partition plate (60);
The second suction passage (which has a straight central axis (L3) extending in the radial direction of the second cylinder (21B) so as to communicate the suction communication passage (102) and the second cylinder chamber (22B) ( 103) and
The first suction passage (101) of the first cylinder (21A) includes a first passage portion (101a) having a straight central axis (L1a) with one end open to the outside, and a first passage portion (101a) thereof. 101a) has a second passage portion (101b) whose one end is connected to the other end side and whose other end side is open toward the center point (O1) of the first cylinder chamber (22A) and whose central axis (L1b) is linear. Have
In plan view, two ends (200Aa, 200Ab) connected to the center point (O1) of the first cylinder chamber (22A) and the blade hole (100) of the inner peripheral wall (200A) of the first cylinder chamber (22A). ), the straight line (L2) passing through the center point (P1) and the central axis (L1b) of the second passage portion (101b), the straight line (L2) and the second suction passage (103). The angle α2 formed by the central axis (L3) of) is smaller than the angle β formed by the straight line (L2) and the central axis (L1a) of the first passage portion (101a). Machine. The rotary compressor according to claim 1,
The rotary compressor, wherein the second passage portion (101b) of the first cylinder (21A) is a groove provided on the partition plate (60) side of the first cylinder (21A). The rotary compressor according to claim 1 or 2,
The rotary compressor, wherein the second suction passage (103) of the second cylinder (21B) is a groove provided on the partition plate (60) side of the second cylinder (21B). In the rotary compressor according to any one of claims 1 to 3,
The passage sectional area (S2) of the second passage portion (101b) of the first cylinder (21A) is smaller than the passage sectional area (S1) of the first passage portion (101a). Rotary compressor. The rotary compressor according to any one of claims 1 to 4,
The rotary compressor, wherein the first cylinder (21A) is a lower cylinder stacked below the partition plate (60). The rotary compressor according to any one of claims 1 to 5,
In the second passage portion (101b) of the first cylinder (21A), the central axis (L1b) of the second passage portion (101b) defines the center point (O1) of the first cylinder chamber (22A). A rotary compressor characterized by being provided so as to pass therethrough.

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