JP5195055B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor used for an air conditioner, a refrigeration apparatus, and the like.

  Conventionally, as shown in FIG. 6, a rotary compressor includes a cylinder 112 having a cylinder chamber 111, a rotary piston 115 disposed in the cylinder chamber 111, a blade 122 provided in the rotary piston 115, and the above-described rotary compressor. Some have a rocking bush 105 that supports a blade 122 (see JP 2005-2832 A: Patent Document 1).

  The cylinder 112 has an inlet 116 that opens to the inner surface and communicates with the cylinder chamber 111. The cylinder chamber 111 communicates with the discharge port 117. The rotary piston 115 is rotatably fitted to the eccentric shaft portion 103 a of the drive shaft 103.

  The blade 122 divides the cylinder chamber 111 into a low pressure chamber 123 communicating with the suction port 116 and a high pressure chamber 124 communicating with the discharge port 117.

  The swing bush 105 is rotatably fitted in a hole 120 formed in the cylinder 112 so as to communicate with the cylinder chamber 111, and the blade 122 can swing with respect to the hole 120 and can move forward and backward. To support.

  On both end surfaces of the rotary piston 115 in the axial direction, notched portions 118 in which the end surface and the inner surface of the rotary piston 115 are notched are provided. This notch 118 is provided over the entire circumference of the rotary piston 115.

Since the notch 118 is provided over the entire circumference of the rotary piston 115, end plates (not shown) are arranged on both end faces of the cylinder 112, and the cylinder 112 is fastened together with the end plates. The contact area between the end face of the rotary piston 115 and the end plate can be reduced, and seizure of the rotary piston 115 can be prevented.
JP 2005-2832 A

  However, in the conventional rotary compressor, since the notch 118 is provided over the entire circumference of the rotary piston 115, the notch 118 is a portion facing the discharge port 117 in the rotary piston 115. Will exist.

  For this reason, the refrigerant gas in the high-pressure chamber 124 leaks out to the inner surface side of the rotary piston 115 through the discharge port 117 and the cutout portion 118 facing the discharge port 117, and there is a problem that the performance deteriorates. It was.

  On the other hand, when the width of the notch 118 is reduced to prevent the leakage of the refrigerant gas, the contact area between the end surface of the rotary piston 115 and the end plate increases, and the seizure of the rotary piston 115 cannot be prevented.

  That is, avoidance of seizure of the rotary piston 115 and prevention of performance degradation due to refrigerant gas leakage could not be realized at the same time.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a rotary compressor that simultaneously realizes avoidance of seizure of a rotary piston and prevention of performance deterioration due to refrigerant gas leakage.

In order to solve the above problems, a rotary compressor of the present invention is
A cylinder chamber that communicates with the discharge port, and a cylinder that has an intake port that opens to the inner surface and communicates with the cylinder chamber;
A rotary piston that is rotatably fitted to the eccentric shaft portion of the drive shaft and disposed in the cylinder chamber;
A blade that is provided on the rotary piston and that divides the cylinder chamber into a low-pressure chamber that communicates with the suction port and a high-pressure chamber that communicates with the discharge port;
A swinging bush that is rotatably fitted in a hole formed in the cylinder so as to communicate with the cylinder chamber, and supports the blade in a swingable and advancing and retracting manner with respect to the hole;
The axial end surface of the rotary piston is provided with a notch portion in which the end surface and the inner surface of the rotary piston are notched,
The notch is formed in a stepped shape having a radial width when viewed from the axial direction of the rotary piston, and at least a portion of the rotary piston facing the suction port excluding a portion facing the discharge port. , Is provided.

  According to the rotary compressor of the present invention, the notch is provided at least in a portion facing the suction port except for a portion facing the discharge port in the rotary piston. While avoiding the seizure of the piston, there is no bypass from the high-pressure chamber to the inner surface side of the rotary piston through the discharge port, thereby preventing performance degradation due to refrigerant gas leakage.

In the rotary compressor of one embodiment,
Having end plates disposed on both end faces in the axial direction of the cylinder to close the cylinder chamber;
The discharge port is provided in one of the end plates.

  According to the rotary compressor of this embodiment, since the discharge port is provided on one of the end plates, the discharge port is brought close to the center of the cylinder chamber so that a discharge passage that does not cause a dead volume is widened. It can be secured.

In the rotary compressor of one embodiment,
The notch is provided in all parts except the part facing the discharge port in the rotary piston,
The cutout portion is formed in a C shape with a portion facing the discharge port cut away when viewed from the axial direction of the rotary piston.

  According to the rotary compressor of this embodiment, the cutout portion is formed in a C shape with a portion facing the discharge port as viewed from the axial direction of the rotary piston. Is more reliably avoided, and performance degradation due to refrigerant gas leakage is more reliably prevented.

In the rotary compressor of one embodiment,
A cylinder chamber that communicates with the discharge port, and a cylinder that has an intake port that opens to the inner surface and communicates with the cylinder chamber;
A rotary piston that is rotatably fitted to the eccentric shaft portion of the drive shaft and disposed in the cylinder chamber;
A blade that is provided on the rotary piston and that divides the cylinder chamber into a low-pressure chamber that communicates with the suction port and a high-pressure chamber that communicates with the discharge port;
A swing bush that is rotatably fitted in a hole formed in the cylinder so as to communicate with the cylinder chamber, and supports the blade in a swingable and advancing and retracting manner with respect to the hole;
With
The axial end surface of the rotary piston is provided with a notch portion in which the end surface and the inner surface of the rotary piston are notched,
The notch is provided in at least a portion facing the suction port except for a portion facing the discharge port in the rotary piston,
The notch is provided only in a portion of the rotary piston that faces the suction port.

According to the rotary compressor of this embodiment, the notch is provided at least in a portion facing the suction port except for a portion facing the discharge port in the rotary piston. While avoiding the seizure of the rotary piston, the bypass that leads from the high-pressure chamber to the inner surface side of the rotary piston via the discharge port is eliminated to prevent the performance deterioration due to refrigerant gas leakage. Since the notch is provided only in a portion of the rotary piston that faces the suction port, the notch can be easily formed.

  According to the rotary compressor of the present invention, the notch portion is provided at least in a portion facing the suction port except for a portion facing the discharge port in the rotary piston. Avoidance and prevention of performance degradation due to refrigerant gas leakage are realized at the same time.

  Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.

(First embodiment)
FIG. 1 is an overall configuration diagram showing an embodiment of a rotary compressor according to the present invention. The rotary compressor includes a hermetic casing 1, and a motor 2 and a compression element 4 disposed in the hermetic casing 1.

  In the hermetic casing 1, the motor 2 is arranged at the upper part, and the compression element 4 is arranged at the lower part. The compression element 4 is rotationally driven by a drive shaft 3 extending from the motor 2.

  The compression element 4 includes a cylinder 12 having a cylinder chamber 11 therein, end plates 13 and 14 disposed at both axial end surfaces of the cylinder 12 to close the cylinder chamber 11, and the cylinder chamber 11. The rotary piston 15 is disposed.

  As shown in FIG. 2, the rotary piston 15 is formed in an annular shape, and an eccentric shaft portion 3a of the drive shaft 3 is rotatably fitted therein. The shaft center of the eccentric shaft portion 3a is offset from the center point of the drive shaft 3 by a predetermined amount. When the drive shaft 3 rotates, the rotary piston 15 does not rotate, and the cylinder chamber 11 is located at one place on the outer peripheral surface thereof. It revolves along the outer peripheral wall while contacting or approaching the outer peripheral wall.

  The cylinder 12 is provided with a suction port 16 that opens to the inner surface. In other words, the suction port 16 opens in the outer peripheral wall of the cylinder chamber 11. One of the end plates 13 is provided with a discharge port 17 that opens on one surface, and the discharge port 17 communicates with the cylinder chamber 11.

  A cylindrical hole 20 penetrating in the axial direction is formed at a position between the suction port 16 and the discharge port 17 of the cylinder 12, and the hole 20 communicates with the cylinder chamber 11. The swing bush 5 is accommodated in the hole 20. The swing bush 5 is rotatably fitted in the hole 20.

  The rotary piston 15 is integrally provided with a blade 22 extending in a radial direction from the outer peripheral surface thereof. The blade 22 is integrally formed with the rotary piston 15. Note that the blade may be formed of a separate member and connected to the rotary piston with an adhesive or the like.

  The swing bush 5 is composed of a pair of half bushes whose cross section is substantially semicircular. The pair of halved bushes support the blade 22 so as to be swingable and advanceable / retractable with respect to the hole 20 with the blade 22 sandwiched between the split surfaces.

  The blade 22 partitions the cylinder chamber 11 between the outer peripheral wall of the cylinder chamber 11 and the outer peripheral surface of the rotary piston 15 into a low pressure chamber 23 that communicates with the suction port 16 and a high pressure chamber 24 that communicates with the discharge port 17. Yes.

  In this state, the rotary piston 15 swings along the inner peripheral surface of the cylinder 12 (that is, the outer peripheral wall of the cylinder chamber 11) so that the half bushes 21, 21 are oscillated through the blade 22. Each revolution, the fluid such as the refrigerant gas sucked from the suction port 16 is compressed and discharged from the discharge port 17.

  As shown in FIG. 2 and FIG. 3, notches 18 in which the end surface and the inner surface of the rotary piston 15 are notched are provided on both end surfaces of the rotary piston 15 in the axial direction. FIG. 3 is a cross-sectional view taken along the line AA in FIG.

  The notch 18 is provided in at least a portion facing the suction port 16 except for a portion facing the discharge port 17 in the rotary piston 15.

  Here, the portion of the rotary piston 15 that faces the discharge port 17 refers to the entire portion of the rotary piston 15 that faces the discharge port 17 during the revolution of the rotary piston 15. The portion of the rotary piston 15 that faces the suction port 16 refers to the entire portion of the rotary piston 15 that faces the suction port 16 during the revolution of the rotary piston 15.

  That is, the notch 18 is provided in all parts of the rotary piston 15 except for the part facing the discharge port 17. The cutout portion 18 is formed in a C shape with a portion facing the discharge port 17 cut away when viewed from the axial direction of the rotary piston 15.

  The notch 18 is processed by spot facing and is formed in a stepped shape. The radial width of the rotary piston 15 at the notch 18 is constant over the circumferential direction of the rotary piston 15.

  According to the rotary compressor having the above-described configuration, the notch portion 18 is provided at least in a portion facing the suction port 16 except for a portion facing the discharge port 17 in the rotary piston 15. In addition to avoiding the seizure of the rotary piston 15 due to the deformation of 12, there is no bypass from the high-pressure chamber 24 to the inner surface side of the rotary piston 15 via the discharge port 17, thereby preventing performance degradation due to refrigerant gas leakage.

  That is, when the end plates 13 and 14 are arranged on both end surfaces in the axial direction of the cylinder 12 and the cylinder 12 is fastened together with the end plates 13 and 14, a part of the cylinder 12 where the suction port 16 opens has rigidity. Since it is small, the deformation of a part of the cylinder 12 becomes large.

  For this reason, the gap between the portion of the rotary piston 15 facing the suction port 16 and the end plates 13 and 14 is reduced, but the notch 18 is provided in a portion of the rotary piston 15. The contact between the part and the end plates 13 and 14 is reduced, and seizure of the rotary piston 15 is avoided.

  As described above, since a part of the cylinder 12 is deformed to the greatest extent, if the cutout portion 18 is provided in at least a portion of the rotary piston 15, the rotary piston 15 is not provided in the other portion of the rotary piston 15. It was found that seizure of the piston 15 can be avoided.

  Further, since the notch 18 is not located in the portion of the rotary piston 15 that faces the discharge port 17, there is no bypass that leads from the high pressure chamber 24 to the inner surface side of the rotary piston 15 via the discharge port 17, and the refrigerant gas leaks. Prevent performance degradation. For this reason, the discharge port 17 can be brought close to the center of the cylinder chamber 11, and a wide discharge passage that does not cause a dead volume can be secured.

  Further, since the discharge port 17 is provided in one of the end plates 13, the discharge port 17 can be brought close to the center of the cylinder chamber 11 to ensure a wide discharge passage that does not cause a dead volume.

  Further, since the cutout portion 18 is formed in a C shape with a portion facing the discharge port 17 cut away when viewed from the axial direction of the rotary piston 15, the seizure of the rotary piston 15 can be avoided more reliably. In addition, performance degradation due to refrigerant gas leakage is more reliably prevented.

(Second Embodiment)
FIG. 4 shows a second embodiment of the rotary compressor of the present invention. If the point which is different from the said 1st Embodiment is demonstrated, in this 2nd Embodiment, the shape of the notch part of a rotary piston will differ. Note that the same reference numerals as those in the first embodiment have the same configurations as those in the first embodiment, and thus description thereof is omitted.

  In the second embodiment, the cutout portion 18A of the rotary piston 15A is provided only in a portion facing the suction port 16 in the rotary piston 15A.

  The notch 18A is formed in a stepped shape. The radial width of the rotary piston 15 at the notch 18A is constant over the circumferential direction of the rotary piston 15A. The width of the cutout portion 18A is larger than the width of the cutout portion 18 of the first embodiment.

  Therefore, in addition to the operational effects of the first embodiment, the notch 18A is provided only in the portion of the rotary piston 15A that faces the suction port 16, and therefore the notch 18A can be easily formed. Can be formed.

  FIG. 5 shows another type of rotary compressor. When the difference from the first embodiment is described, the shape of the notch portion of the rotary piston is different. Note that the same reference numerals as those in the first embodiment have the same configurations as those in the first embodiment, and thus description thereof is omitted.

  In this other embodiment, the cutout portion 18B of the rotary piston 15B is provided only in a portion facing the discharge port 17 in the rotary piston 15B.

  The notch 18B is formed in a stepped shape. The radial width of the rotary piston 15B in the notch 18B is constant over the circumferential direction of the rotary piston 15B. The width of the cutout portion 18B is larger than the width of the cutout portion 18 of the first embodiment.

  In addition, this invention is not limited to the above-mentioned embodiment. For example, the notch may be provided intermittently rather than continuously. Further, the notch portion may be provided anywhere as long as it is provided in a portion facing the suction port and not provided in a portion facing the discharge port. Moreover, you may provide a discharge port so that it may open to the inner surface of a cylinder.

It is a longitudinal section showing a 1st embodiment of a rotary compressor of the present invention. It is a cross-sectional view in a rotary piston bottom dead center posture of a rotary compressor. It is AA sectional drawing of FIG. It is a cross-sectional view which shows 2nd Embodiment of the rotary compressor of this invention. It is a cross-sectional view which shows the rotary compressor of another form. It is a cross-sectional view showing a conventional rotary compressor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Sealed casing 2 Motor 3 Drive shaft 3a Eccentric shaft part 4 Compression element 5 Oscillation bush 11 Cylinder chamber 12 Cylinder 13, 14 End plate 15, 15A Rotary piston 16 Suction port 17 Discharge port 18, 18A Notch 20 Hole 22 Blade 23 Low pressure chamber 24 High pressure chamber

Claims (4)

A cylinder (12) having a cylinder chamber (11) communicating with the discharge port (17) and having a suction port (16) opened on the inner surface and communicating with the cylinder chamber (11);
A rotary piston (15, 15A) that is rotatably fitted to the eccentric shaft portion (3a) of the drive shaft (3) and disposed in the cylinder chamber (11);
A low pressure chamber (23) provided on the rotary piston (15, 15A) and communicating the cylinder chamber (11) with the suction port (16) and a high pressure chamber (24) communicating with the discharge port (17) A blade (22) partitioning into
The cylinder (12) is rotatably fitted in a hole (20) formed so as to communicate with the cylinder chamber (11), and the blade (22) can swing with respect to the hole (20). And a swinging bush (5) that is supported so as to freely advance and retract,
On the axial end surface of the rotary piston (15, 15A), a notch (18, 18A) in which the end surface and the inner surface of the rotary piston (15, 15A) are notched is provided,
The notch (18, 18A) is formed in a stepped shape having a radial width when viewed from the axial direction of the rotary piston (15, 15A), and the discharge port in the rotary piston (15, 15A). A rotary compressor characterized in that the rotary compressor is provided at least in a portion facing the suction port (16) excluding a portion facing (17). The rotary compressor according to claim 1.
Having end plates (13, 14) disposed on both end faces in the axial direction of the cylinder (12) for closing the cylinder chamber (11);
The rotary compressor according to claim 1, wherein the discharge port (17) is provided in one of the end plates (13). The rotary compressor according to claim 1 or 2,
The notch (18) is provided in all parts of the rotary piston (15) except for the part facing the discharge port (17),
The notch (18) is formed in a C-shape with a portion facing the discharge port (17) cut away when viewed from the axial direction of the rotary piston (15). . A cylinder (12) having a cylinder chamber (11) communicating with the discharge port (17) and having a suction port (16) opened on the inner surface and communicating with the cylinder chamber (11);
A rotary piston (15, 15A) that is rotatably fitted to the eccentric shaft portion (3a) of the drive shaft (3) and disposed in the cylinder chamber (11);
A low pressure chamber (23) provided on the rotary piston (15, 15A) and communicating the cylinder chamber (11) with the suction port (16) and a high pressure chamber (24) communicating with the discharge port (17) A blade (22) partitioning into
The cylinder (12) is rotatably fitted in a hole (20) formed so as to communicate with the cylinder chamber (11), and the blade (22) can swing with respect to the hole (20). And a swinging bush (5) that supports the reciprocating movement
With
On the axial end surface of the rotary piston (15A), there is provided a notch (18A) in which the end surface and the inner surface of the rotary piston (15A) are notched,
The notch (18A) is provided at least in a portion facing the suction port (16) except for a portion facing the discharge port (17) in the rotary piston (15A),
The rotary compressor according to claim 1, wherein the notch (18A) is provided only in a portion of the rotary piston (15A) facing the suction port (16).

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