JP6206776B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor used for an air conditioner, a refrigerator, a blower, a hot water heater and the like.

  Rotary compressors are widely used in electrical appliances such as air conditioners, heating devices, and water heaters. As one of the efforts to improve the efficiency of the rotary compressor, a technique for suppressing a reduction in efficiency due to the refrigerant (suction refrigerant) sucked into the compression chamber receiving heat from the surroundings, so-called heat loss, has been proposed. Yes.

  The rotary compressor of Patent Document 1 has a sealed space in the suction side portion of the cylinder as means for suppressing heat reception of the suction refrigerant. This sealed space suppresses the transfer of heat from the high-temperature refrigerant in the sealed container to the inner wall of the cylinder.

JP-A-2-140486

  However, it is not always easy to form a sealed space in the cylinder as in Patent Document 1. Therefore, another technique that can effectively suppress the heat reception of the suction refrigerant is desired.

  In view of the above, an object of the present invention is to provide a rotary compressor that further minimizes the range in which a high-temperature compressed refrigerant can enter and further improves the heat insulation effect.

That is, the present invention includes a sealed container having an oil reservoir, a shaft disposed in the sealed container, a cylinder disposed in the sealed container, and disposed in the cylinder and coupled to the shaft. A compressed piston, an end plate member attached to the cylinder so as to form a cylinder chamber between the cylinder and the piston, and a vane that partitions the cylinder chamber into a suction chamber and a discharge chamber A suction port for supplying a refrigerant to be sucked into the suction chamber, a discharge port formed in the end plate member for discharging the compressed refrigerant from the discharge chamber, and adjusting a discharge amount of the refrigerant provided in the discharge port And a valve stop that restricts the movement of the valve, and the end plate member that closes the cylinder, and is discharged from the discharge chamber through the discharge port. Comprising a refrigerant discharge space in which the refrigerant can stay, and the closure member attached to the end plate member, a transmural flow path from said refrigerant discharge space you discharge the refrigerant into the closed vessel, the refrigerant discharge The space is constituted by an occupied space when the valve stop, the through flow channel, and a passage communicating the discharge port and the through flow channel are projected in the axial direction of the shaft , Rotary compressor.

  The rotary compressor of the present invention can minimize the range of the high-temperature compressed refrigerant by minimizing the volume of the refrigerant discharge space formed between the end plate member and the closing member. Thereby, since the temperature rise of an end plate member can be suppressed, it can also suppress that the heat | fever of a compressed refrigerant moves to a suction | inhalation refrigerant | coolant through an end plate member, Therefore Volume efficiency improves.

1 is a longitudinal sectional view of a rotary compressor according to an embodiment of the present invention. 1 is a cross-sectional view taken along the line IIA-IIA of the rotary compressor shown in FIG. 1 is a cross-sectional view taken along the line IIB-IIB of the rotary compressor shown in FIG. Bottom view of lower bearing member having refrigerant discharge space formed by minimum projection surface by valve stop, through flow passage, and passage of same rotary compressor Bottom view of lower bearing member with fixed valve and valve stop of the rotary compressor Bottom view of lower bearing member including space (relief part) for inserting valve and device for fixing valve stop of same rotary compressor Bottom view of lower bearing member with 3cc or more secured around the discharge port of the rotary compressor A longitudinal sectional view of a rotary compressor according to another embodiment of the present invention. The bottom view of the lower bearing member in which the relief part, passage, and through passage of the rotary compressor are integrally formed Longitudinal sectional view of oil holding part of the rotary compressor

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Motor 3 1st compression block 4 Shaft 4a 1st eccentric part 4b 2nd eccentric part 5 1st cylinder 6 Upper bearing member 7 Lower bearing member 7p Communication path 8 1st piston 9 1st closure member 10 2nd closure Member 11 Discharge pipe 13 Internal space 14 First suction pipe 15 Second cylinder 16 Second suction pipe 17 Stator 18 Rotor 19 First suction port 20 Second suction port 21 Terminal 22 Oil reservoir 25 First cylinder chamber 25a First suction chamber 25b first discharge chamber 26 second cylinder chamber 26a second suction chamber 26b second discharge chamber 28 second piston 30 second compression block 32 first vane 33 second vane 34 first vane groove 35 second vane groove 36 first Spring 37 Second spring 38 Middle plate 40 First discharge port 41 Second discharge port 43 First discharge valve 43a First valve 43b First valve Top 43c 1st fixing tool 44 2nd discharge valve 44a 2nd valve 44b 2nd valve stop 44c 2nd fixing tool 45 Passage 46 Through passage 51, 52 Refrigerant discharge space 53 Oil holding part 100 Rotary compressor 102 Compression mechanism 200 Rotary Compressor

  A rotary compressor according to a first embodiment of the present invention includes an airtight container having an oil reservoir, a shaft disposed inside the airtight container, a cylinder disposed inside the airtight container, and an inside of the cylinder. A piston connected to the shaft, an end plate member attached to the cylinder so as to form a cylinder chamber between the cylinders, and a vane that partitions the cylinder chamber into a suction chamber and a discharge chamber. A suction port for supplying the refrigerant to be sucked into the suction chamber, a discharge port formed in the end plate member for discharging the compressed refrigerant from the discharge chamber, a valve provided in the discharge port for adjusting the discharge amount of the refrigerant, and a valve A valve stop that restricts the movement of the cylinder, an end plate member that closes the cylinder, a refrigerant discharge space in which the refrigerant discharged from the discharge chamber through the discharge port can stay, and an end plate member A closed blocking member and a through channel that discharges the refrigerant from the refrigerant discharge space into the sealed container. The refrigerant discharge space communicates the valve stop, the through channel, the discharge port, and the through channel. The passage is constituted by an occupied space when projected in the axial direction of the shaft. According to the present embodiment, since the area of the refrigerant discharge space in which high-temperature compressed gas exists can be minimized, heat transfer to the lower bearing member can be suppressed, heating to the suction refrigerant is reduced, and volume efficiency is improved. To do.

According to a second embodiment of the present invention, in the rotary compressor according to the first embodiment, the refrigerant discharge space includes a space in which a device for fixing the valve stop can be inserted. According to the present embodiment, the valve stop and the valve can be easily fixed with a rivet or a bolt, so that mass productivity is improved.

In the rotary compressor according to the first or second embodiment, the third embodiment of the present invention includes an oil holding portion that takes in part of the oil stored in the oil reservoir in the end plate member. According to the present embodiment, since the oil held in the oil holding portion works as a heat insulating material, the refrigerant (intake refrigerant) in which the heat of the refrigerant (compressed refrigerant) in the refrigerant discharge space is sucked into the cylinder chamber through the lower bearing member. ) Can be suppressed, and the volumetric efficiency is improved.

According to a fourth embodiment of the present invention, in the rotary compressor according to the third embodiment, the oil holding unit is configured such that the flow of the taken-in oil is suppressed more than the oil pool. According to the present embodiment, since the heat insulating property of the oil held in the oil holding part is improved, the volume efficiency is further improved.

According to a fifth embodiment of the present invention, in the rotary compressor according to any one of the first to fourth embodiments, a muffler space is provided between the through passage and the sealed container. According to the present embodiment, the refrigerant compressed in the second compression block is the refrigerant compressed in the first compression block and the internal space of the first closing member, that is, the refrigerant discharge space (muffler space) on the upper shaft side. Join in. Therefore, even if the volume of the refrigerant discharge space on the lower shaft side is insufficient, it is possible to obtain a silencing effect due to the refrigerant discharge space (muffler space) on the upper shaft side inside the first closing member.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by this embodiment.

As shown in FIG. 1, the rotary compressor 100 of the present embodiment includes a sealed container 1, a motor 2, a compression mechanism 102, and a shaft 4. The compression mechanism 102 is disposed at the lower part of the sealed container 1. The motor 2 is disposed on the compression mechanism 102 inside the sealed container 1. The compression mechanism 102 and the motor 2 are connected by the shaft 4. A terminal 21 for supplying electric power to the motor 2 is provided on the top of the sealed container 1. An oil reservoir 22 for holding lubricating oil is formed at the bottom of the sealed container 1.
The motor 2 includes a stator 17 and a rotor 18. The stator 17 is fixed to the inner wall of the sealed container 1. The rotor 18 is fixed to the shaft 4. The rotor 18 and the shaft 4 are rotated by driving the motor 2. A discharge pipe 11 is provided on the top of the sealed container 1. The discharge pipe 11 penetrates the upper part of the sealed container 1 and opens toward the internal space 13 of the sealed container 1. The discharge pipe 11 serves as a discharge flow path that guides the refrigerant compressed by the compression mechanism 102 to the outside of the sealed container 1. During the operation of the rotary compressor 100, the internal space 13 of the sealed container 1 is filled with the compressed refrigerant. That is, the rotary compressor 100 is a high-pressure shell type compressor. According to the high-pressure shell type rotary compressor 100, the motor 2 can be cooled with the refrigerant, so that improvement in motor efficiency can be expected.

  The compression mechanism 102 is moved by the motor 2 so as to compress the refrigerant. Specifically, the compression mechanism 102 includes a first compression block 3, a second compression block 30, an upper bearing member 6, a lower bearing member 7, an intermediate plate 38, a first closing member 9 (first muffler member), and a second closing block. It has the member 10 (2nd muffler member). The refrigerant is compressed by the first compression block 3 or the second compression block 30. The first compression block 3 and the second compression block 30 are immersed in oil stored in the oil reservoir 22. In the present embodiment, the first compression block 3 is composed of parts common to the parts constituting the second compression block 30. Accordingly, the first compression block 3 has a suction volume equal to the suction volume of the second compression block 30.

  As shown in FIG. 2, the first compression block 3 includes a first cylinder 5, a first piston 8, a first vane 32, a first suction port 19, a first discharge port 40, and a first spring 36. . As shown in FIG. 3, the second compression block 30 includes a second cylinder 15, a second piston 28, a second vane 33, a second suction port 20, a second discharge port 41, and a second spring 37. . The first cylinder 5 and the second cylinder 15 are arranged concentrically with each other.

  The shaft 4 has a first eccentric part 4a and a second eccentric part 4b. The first eccentric portion 4 a and the second eccentric portion 4 b protrude outward in the radial direction of the shaft 4. The first piston 8 and the second piston 28 are disposed inside the first cylinder 5 and the second cylinder 15, respectively. In the 1st cylinder 5, the 1st piston 8 is attached to the 1st eccentric part 4a. In the second cylinder 15, the second piston 28 is attached to the second eccentric portion 4b. A first vane groove 34 and a second vane groove 35 are formed in the first cylinder 5 and the second cylinder 15, respectively. In the rotation direction of the shaft 4, the position of the first vane groove 34 coincides with the position of the second vane groove 35. The first eccentric portion 4a protrudes in a direction opposite to the protruding direction of the second eccentric portion 4b by 180 degrees. That is, the phase difference between the first piston 8 and the second piston 28 is 180 degrees. This configuration has an effect of reducing vibration and noise.

  The upper bearing member 6 (first end plate member) is attached to the first cylinder 5 so as to form a first cylinder chamber 25 between the inner peripheral surface of the first cylinder 5 and the outer peripheral surface of the first piston 8. It has been. The lower bearing member 7 (second end plate member) is attached to the second cylinder 15 so as to form a second cylinder chamber 26 between the inner peripheral surface of the second cylinder 15 and the outer peripheral surface of the second piston 28. It has been. Specifically, the upper bearing member 6 is attached to the upper part of the first cylinder 5, and the lower bearing member 7 is attached to the lower part of the second cylinder 15. An intermediate plate 38 is disposed between the first cylinder 5 and the second cylinder 15.

  The first suction port 19 and the second suction port 20 are formed in the first cylinder 5 and the second cylinder 15, respectively. The first suction port 19 and the second suction port 20 open toward the first cylinder chamber 25 and the second cylinder chamber 26, respectively. A first suction pipe 14 and a second suction pipe 16 are connected to the first suction port 19 and the second suction port 20, respectively.

  The first discharge port 40 and the second discharge port 41 are formed in the upper bearing member 6 and the lower bearing member 7, respectively. The first discharge port 40 and the second discharge port 41 open toward the first cylinder chamber 25 and the second cylinder chamber 26, respectively. A first discharge valve 43 is provided at the first discharge port 40 so as to open and close the first discharge port 40. The first discharge valve 43 includes a thin first valve 43a, a first valve stop 43b, and a first fixture 43c. The first valve 43a adjusts the discharge amount of the refrigerant. The first valve stop 43b restricts the movement of the first valve 43a. The first fixture 43c fixes both the first valve 43a and the first valve stop 43b.

  A second discharge valve 44 is provided at the second discharge port 41 so as to open and close the second discharge port 41. The second discharge valve 44 includes a thin second valve 44a, a second valve stop 44b, and a second fixture 44c. The second valve 44a adjusts the discharge amount of the refrigerant. The second valve stop 44b restricts the movement of the second valve 44a. The second fixture 44c fixes both the second valve 44a and the second valve stop 44b.

  The first vane groove 34 is arranged so that the first vane 32 (blade) can slide. The first vane 32 partitions the first cylinder chamber 25 along the circumferential direction of the first piston 8. Thereby, the first cylinder chamber 25 is partitioned into a first suction chamber 25a and a first discharge chamber 25b. The second vane groove 35 is arranged so that the second vane 33 (blade) can slide. The second vane 33 partitions the second cylinder chamber 26 along the circumferential direction of the second piston 28. Thus, the second cylinder chamber 26 is partitioned into the second suction chamber 26a and the second discharge chamber 26b. The first suction port 19 and the first discharge port 40 are located on the left and right sides of the first vane 32, respectively. The second suction port 20 and the second discharge port 41 are located on the left and right of the second vane 33, respectively. Through the first suction port 19, the refrigerant to be compressed is supplied to the first cylinder chamber 25 (first suction chamber 25 a). Through the second suction port 20, the refrigerant to be compressed is supplied to the second cylinder chamber 26 (second suction chamber 26a). The refrigerant compressed in the first cylinder chamber 25 pushes open the first discharge valve 43 and is discharged from the first discharge chamber 25b through the first discharge port 40. The refrigerant compressed in the second cylinder chamber 26 pushes the second discharge valve 44 open and is discharged from the second discharge chamber 26b through the second discharge port 41.

  The first piston 8 and the first vane 32 may be constituted by a single component, that is, a swing piston. The second piston 28 and the second vane 33 may be constituted by a single component, that is, a swing piston. The first vane 32 and the second vane 33 may be coupled to the first piston 8 and the second piston 28, respectively.

  A first spring 36 and a second spring 37 are disposed behind the first vane 32 and the second vane 33, respectively. The first spring 36 and the second spring 37 push the first vane 32 and the second vane 33 toward the center of the shaft 4, respectively. The rear part of the first vane groove 34 and the rear part of the second vane groove 35 are each in communication with the internal space 13 of the sealed container 1. Accordingly, the pressure in the inner space 13 of the sealed container 1 is applied to the back surface of the first vane 32 and the back surface of the second vane 33, respectively. Further, the lubricating oil stored in the oil reservoir 22 is supplied to the first vane groove 34 and the second vane groove 35.

  In the refrigerant discharge space 51, the refrigerant discharged from the first discharge chamber 25b through the first discharge port 40 can stay. As shown in FIG. 1, the first closing member 9 is attached to the upper bearing member 6 (first end plate member) so as to form the refrigerant discharge space 51 on the opposite side of the first cylinder chamber 25. Specifically, the first closing member 9 is attached to the upper portion of the upper bearing member 6 so that the refrigerant discharge space 51 is formed above the upper bearing member 6. The first discharge valve 43 is covered with the first closing member 9. The first closing member 9 is formed with a discharge port 9 a for guiding the refrigerant from the refrigerant discharge space 51 to the internal space 13 of the sealed container 1. The refrigerant discharged from the second discharge chamber 26 b through the second discharge port 41 can stay in the refrigerant discharge space 52. The second closing member 10 is attached to the lower bearing member 7 (second end plate member) so as to form the refrigerant discharge space 52 on the opposite side of the second cylinder chamber 26. Specifically, the second closing member 10 is attached to the lower part of the lower bearing member 7 so that the refrigerant discharge space 52 is formed below the lower bearing member 7. The second discharge valve 44 is covered with the second closing member 10. The refrigerant discharge spaces 51 and 52 each serve as a refrigerant flow path. The shaft 4 passes through the central portion of the first closing member 9 and the central portion of the second closing member 10 and is rotatable by being supported by the upper bearing member 6 and the lower bearing member 7.

  In the rotary compressor configured as described above, as shown in FIGS. 4 and 5, the refrigerant discharge space 52 includes the second valve stop 44 b, the through passage 46, the second discharge port 41, and the through passage 46. The communicating passage 45 is constituted by an occupied space (a space formed by the minimum projection plane) when projected in the axial direction of the shaft 4.

  Both the second valve stop 44b and the second valve 44a are fixed with rivets. As a fixing method, bolts or the like may be used in addition to rivets.

  Thereby, since the area of the refrigerant discharge space 52 in which the high-temperature compressed gas exists can be minimized, heat transfer to the lower bearing member is suppressed, so that heating to suction is reduced and volume efficiency is improved.

  Further, as shown in FIG. 6, the refrigerant discharge space 52 includes a space (a relief portion) 47 into which a device for fixing both the second valve 44a and the second valve stop 44b can be inserted. Accordingly, the second valve stop 44b and the second valve 44a can be easily fixed with a rivet or a bolt, so that mass productivity is improved.

  Moreover, as shown in FIG. 7, in the refrigerant | coolant discharge space 52, you may form the escape part 47, the channel | path 45, and the penetration flow path 46 integrally. Thereby, the flow of the high-pressure gas is improved and the pressure loss is reduced.

  Further, as shown in FIG. 1, the refrigerant discharge space 52 communicates with the refrigerant discharge space 51 through the through flow path 46. The through passage 46 penetrates the lower bearing member 7, the second cylinder 15, the intermediate plate 38, the first cylinder 5, and the upper bearing member 6 in a direction parallel to the rotation axis of the shaft 4. The refrigerant compressed by the second compression block 30 merges with the refrigerant compressed by the first compression block 3 in the internal space of the first closing member 9, that is, the refrigerant discharge space 51. Therefore, even if the volume of the refrigerant discharge space 52 is insufficient, a noise reduction effect by the refrigerant discharge space 51 can be obtained inside the first closing member 9. Further, the cross-sectional area (flow channel area) of the through flow channel 46 is larger than the cross-sectional area (flow channel area) of the second discharge port 41. Thereby, increase in pressure loss can be prevented.

As shown in FIG. 3, in the present invention, the first reference plane H1, the second reference plane H2, and the third reference plane H3 are defined as follows. Plane defined as a first reference plane H1 containing the center axis O ₁ and the center of the second cylinder 15 of the second vane 33 when the second vane 33 is most projected toward the central axis O ₁ of the second cylinder 15 To do. The first reference plane H <b> 1 passes through the center of the second vane groove 35. Also includes a center axis O _1, and a plane perpendicular to the first reference plane H1 is defined as a second reference plane H2. The plane including the central and central axis O ₁ of the second intake port 20 is defined as a third reference plane H3. Note that the center axis O ₁ of the second cylinder 15 substantially coincides with the rotation axis of the shaft 4 and the center axis of the first cylinder 5.

  Next, the oil holding part 53 will be described.

  As shown in FIG. 8, the compression mechanism 102 further has an oil holding portion 53. The oil retaining portion 53 is formed on the same side as the second suction port 20 as viewed from the first reference plane H1 and on the opposite side of the second cylinder chamber 26 with the lower bearing member 7 interposed therebetween. Specifically, the oil retaining portion 53 is in contact with the lower surface of the lower bearing member 7. The oil holding part 53 is configured to take in a part of the oil stored in the oil reservoir 22 and suppress the flow of the taken-in oil more than the oil flow in the oil reservoir 22. The oil flow in the oil holding portion 53 is gentler than the oil flow in the oil reservoir 22.

  In the rotary compressor 200, the oil level of the oil reservoir 22 is located above the lower surface of the first cylinder 5. In order to ensure reliability, the oil level of the oil reservoir 22 is preferably higher than the upper surface of the first cylinder 5 and lower than the lower end of the motor 2 during operation. The second cylinder 15, the lower bearing member 7 and the second closing member 10 are immersed in the oil in the oil reservoir 22. Therefore, the oil in the oil reservoir 22 can flow into the oil holding part 53.

  The refrigerant to be compressed is in a low temperature and low pressure state. On the other hand, the compressed refrigerant is in a high temperature and high pressure state. Therefore, a specific temperature distribution is generated in the lower bearing member 7 during the operation of the rotary compressor 100. Specifically, when the lower bearing member 7 is divided into a suction side portion and a discharge side portion, the suction side portion is at a relatively low temperature and the discharge side portion is at a relatively high temperature. The lower bearing member 7 is divided into a suction side portion and a discharge side portion on the first reference plane H1. The suction side portion includes a portion directly below the second suction port 20, and the discharge side portion is provided with a second discharge port 41.

  In the present embodiment, an oil holding portion 53 is formed on the same side as the second suction port 20 as viewed from the first reference plane H1. The oil holding portion 53 is in contact with the lower surface of the lower bearing member 7. In this case, since the oil held in the oil holding portion 53 serves as a heat insulating material, the refrigerant (suction) in which the heat of the refrigerant (compressed refrigerant) in the refrigerant discharge space 52 is drawn into the second cylinder chamber 26 through the lower bearing member 7. It can suppress moving to (refrigerant). Even if other members are disposed between the oil retaining portion 53 and the lower surface of the lower bearing member 7, such other members can be regarded as a part of the lower bearing member 7.

  As shown in FIGS. 8 and 9, in the present embodiment, the oil retaining portion 53 is formed by closing the first recess formed in the lower bearing member 7 with the second closing member 10. According to such a structure, an increase in the thickness of the lower bearing member 7 can be avoided, so that an increase in component costs can be avoided, and it is advantageous for reducing the weight of the rotary compressor 200. However, the oil retaining portion 53 may be formed by closing the first recess with a member different from the second closing member 10.

  The lower bearing member 7 is further provided with a communication path 7p. The communication path 7p extends in the lateral direction so as to allow the oil reservoir 22 and the oil holding portion 53 to communicate with each other. The oil in the oil reservoir 22 can flow into the oil holding part 53 through the communication path 7p (communication hole). When the plurality of communication paths 7p are formed, the oil in the oil reservoir 22 can surely flow into the oil holding portion 53. The size of the communication path 7 p is adjusted to a size that is necessary and sufficient for the oil in the oil reservoir 22 to flow into the oil holding portion 53. Therefore, the oil flow in the oil holding portion 53 is gentler than the oil flow in the oil reservoir 22. Therefore, the oil forms a relatively stable temperature stratification in the oil holding portion 53.

  In the present embodiment, the communication path 7p is configured by a small through hole. However, the communication path 7p may be configured by another structure such as a slit. As shown in FIGS. 9 and 10, the upper end of the communication path 7 p coincides with the lower surface 7 h of the lower bearing member 7 in the direction parallel to the rotation axis of the shaft 4, or from the lower surface 7 h of the lower bearing member 7. Is also located above. According to such a configuration, it is possible to prevent air or refrigerant from remaining in the oil holding portion 53.

  Further, the second recess formed in the lower bearing member 7 is closed by the second closing member 10 to form the refrigerant discharge space 52. That is, the lower bearing member 7 is formed with a first recess that functions as the oil retaining portion 53 and a second recess that functions as the refrigerant discharge space 52. The second closing member 10 is composed of a single plate member. The opening end surface of the first recess and the opening end surface of the second recess are on the same plane so that both the first recess and the second recess are closed by the second closing member 10. Such a structure is very simple and an increase in the number of parts can be avoided.

  As shown in FIG. 9, an oil retaining portion 53 is formed in a part of the periphery of the shaft 4, and a refrigerant discharge space 52 is formed in another part of the section. The oil retaining portion 53 is completely isolated from the refrigerant discharge space 52 by the rib 7 k provided on the lower bearing member 7. Most of the refrigerant discharge space 52 is formed on the same side as the second discharge port 41 when viewed from the first reference plane H1. On the other hand, the oil retaining portion 53 is formed on the same side as the second suction port 20 as viewed from the first reference plane H1. According to such a positional relationship, it is possible to suppress the heat of the refrigerant discharged into the refrigerant discharge space 52 from moving to the refrigerant sucked into the second cylinder chamber 26.

  Although not shown, the first compression block 3 may be omitted from the rotary compressor 200 shown in FIG. That is, it is a one-piston rotary compressor provided with only one cylinder. Thus, the present invention can also be applied to a one-piston rotary compressor.

  Further, although not shown in the figure, an oil retaining portion 53 may be formed inside the upper bearing member 6 of the rotary compressor. Further, according to the structure described with reference to FIG. 8, the oil retaining portion 53 can be formed above the upper bearing member 6. Thus, the oil holding part 53 may be formed on the upper side as viewed from the second cylinder chamber 26, or may be formed on the lower side.

  INDUSTRIAL APPLICATION This invention is useful for the compressor of the refrigerating-cycle apparatus which can be utilized for electrical appliances, such as a water heater, a warm water heating apparatus, and an air conditioning apparatus.

Claims (5)

An airtight container having an oil reservoir;
A shaft disposed inside the sealed container;
A cylinder disposed inside the sealed container;
A piston disposed within the cylinder and coupled to the shaft;
An end plate member attached to the cylinder so as to form a cylinder chamber between the cylinder and the piston;
A vane that partitions the cylinder chamber into a suction chamber and a discharge chamber;
A suction port for supplying the refrigerant to be compressed to the suction chamber;
A discharge port that is formed in the end plate member and discharges the compressed refrigerant from the discharge chamber;
A valve provided at the discharge port for adjusting the discharge amount of the refrigerant;
A valve stop for regulating the movement of the valve;
A refrigerant discharge space provided in the end plate member that closes the cylinder and in which the refrigerant discharged from the discharge chamber through the discharge port can stay;
A closing member attached to the end plate member;
A through passage for discharging the refrigerant from the refrigerant discharge space into the sealed container,
The refrigerant discharge space is configured as an occupied space when the valve stop, the through flow channel, and a passage communicating the discharge port and the through flow channel are projected in the axial direction of the shaft. Rotary compressor characterized by this. The rotary compressor according to claim 1 , wherein the refrigerant discharge space includes a space into which a device for fixing the valve stop can be inserted. The rotary compressor according to claim 1 , further comprising an oil holding portion that takes in a part of the oil stored in the oil reservoir in the end plate member. 4. The rotary compressor according to claim 3 , wherein the oil holding portion is configured so that the flow of the taken-in oil is suppressed more than the oil pool. 5. The rotary compressor according to any one of claims 1 to 4 , wherein a muffler space is provided between the through channel and the sealed container.