JP6186593B2 - Rotary compressor - Google Patents

Description

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

  In refrigeration equipment, air conditioning equipment, etc., a compressor is used that sucks the working refrigerant evaporated by the evaporator, compresses it to the pressure necessary for condensation, and sends the working refrigerant at high temperature and high pressure into the working refrigerant circuit. Yes. A rotary compressor is known as one of such compressors. For example, as shown in FIG. 4, the rotary compressor is one in which the electric motor 2 and the compression mechanism 3 are connected by a crankshaft 31 and housed in the sealed container 1. The compression mechanism unit 3 includes a cylinder chamber 50 formed by the cylinder 30, the first end plate member 34 and the second end plate member 35 that close both end faces of the cylinder 30, the first end plate member 34, and the second end plate member 34. The piston 32 fitted to the eccentric portion 31a of the crankshaft 31 supported by the end plate member 35 and reciprocatingly follows the outer periphery of the piston 32 to move the cylinder chamber 50 into the suction chamber 49 and the discharge chamber 39. A partition vane 33 is provided.

  On the other hand, the cylinder 30 is opened with a suction passage 40 for sucking the working refrigerant toward the suction chamber 49, and the first end plate member 34 receives the working refrigerant from the discharge chamber 39 formed by turning from the suction chamber 49. A discharge hole 38 for discharging is opened. The discharge hole 38 is formed as a circular hole in plan view that passes through the first end plate member 34, and a discharge valve 36 that is released when a pressure of a predetermined size or more is applied to the upper surface of the discharge hole 38. Is provided. Further, a muffler chamber 51 constituted by a cup muffler 37 covering the discharge valve 36 and a first end plate member 34 is provided. On the suction chamber side, the sliding portion of the piston 32 passes through the suction passage 40 and moves away from the suction chamber while gradually expanding, and sucks the working refrigerant from the suction passage 40 into the suction chamber. On the other hand, on the discharge chamber side after the working refrigerant is closed, the piston 32 approaches the discharge hole 38 while gradually reducing the discharge chamber 39, and when the pressure is compressed to a predetermined pressure or higher, the discharge valve 36 is opened and discharged. The working refrigerant is discharged from the hole 38 and discharged from the muffler chamber 51 into the sealed container 1.

In the rotary compressor as described above, the sucked low-pressure / low-temperature working refrigerant becomes high-pressure / high-temperature working refrigerant before being discharged from the discharge hole 38, and is discharged from the discharge hole 38 to fill the inside of the sealed container. The oil in the oil sump 6 held in the same space is also close to the temperature of the hot working refrigerant.

  As a factor for reducing the efficiency of the rotary compressor, the compression mechanism 3 housed in the hermetic container is exposed to a high temperature, so that the working refrigerant (suction refrigerant) sucked into the cylinder chamber 50 becomes the cylinder 30, the first end plate member. 34, there is a problem that efficiency is reduced by receiving heat through the second end plate member 35, that is, so-called heat loss occurs.

  In order to solve the above problem, the compressor described in Patent Document 1 has a sealed space in the cylinder 30 as shown in FIG. 5 as means for suppressing the heat reception of the sucked refrigerant. Heat absorption from the refrigerant to the intake refrigerant.

JP-A-2-140486

  However, it is not always easy to form a sealed space in the cylinder as in Patent Document 1. In addition, only a limited effect of suppressing heat reception from the radial direction of the cylinder can be obtained. Therefore, another technique that can effectively suppress the heat reception of the working refrigerant is desired.

  The present invention solves the conventional problems, and provides a compressor capable of suppressing heat reception to the working refrigerant in the cylinder chamber through the end plate member, realizing high volumetric efficiency, and reducing compression power. For the purpose.

In order to solve the conventional problems, a rotary compressor of the present invention includes a sealed container having an oil reservoir at the bottom, a cylinder disposed in the sealed container, a piston disposed in the cylinder, a cylinder and a piston A first end plate member that closes one end face of the opening at both ends of the cylinder, a second end plate member that closes the other end face, and the cylinder chamber as a suction chamber. And a vane that divides into a discharge chamber, a suction passage that supplies the working refrigerant to be compressed to the suction chamber, and a muffler chamber that is provided on the first end plate member side and in which the working refrigerant discharged from the discharge chamber can stay. with which the oil holding portion to the second end plate member side to capture part of the oil of the oil reservoir is more configured in a substantially annular shape, the oil communication path to the respective oil holding portion communicating to the reservoir the oil But it It is those that are provided separately and independently.

  In the rotary compressor according to the present invention, it is possible to suppress heat reception to the working refrigerant through the second end plate member by suppressing the flow of oil at the oil holding portion provided on the second end plate member side. A highly efficient rotary compressor can be provided.

The longitudinal cross-sectional view of the rotary compressor in Embodiment 1 of this invention The bottom view of the 2nd end plate member in Embodiment 1 of the present invention The fragmentary sectional view of the oil holding part in Embodiment 1 of the present invention Longitudinal sectional view of a conventional rotary compressor Expanded cross-sectional view of the cylinder part in a conventional rotary compressor

According to a first aspect of the present invention, there is provided a sealed container having an oil reservoir at the bottom, a cylinder disposed inside the sealed container, a piston disposed inside the cylinder, and a cylinder chamber between the cylinders. A first end plate member that closes one end face of the opening at both ends of the cylinder, a second end plate member that closes the other end face, a vane that partitions the cylinder chamber into a suction chamber and a discharge chamber, and a compression A rotary compressor comprising a suction passage for supplying a working refrigerant to be sucked to a suction chamber, and a muffler chamber provided in the first end plate member, in which the working refrigerant discharged from the discharge chamber can stay. oil retaining portion on the plate member taking a part of the oil sump oil, a plurality of configurations to approximately annular shape, and its respective oil holding part oil communicating path communicating the reservoir the oil is separately independently Establishment It is characterized in that it is. Here, the “substantially annular shape” is a concave shape provided so as to exclude the bolt mounting portion from the center axis O1 of the cylinder to the outside in the radial direction, and is provided so as to surround the crankshaft. It means the shape that is made. In addition, surrounding with the periphery of a crankshaft includes the form currently formed only in a part of circumferential direction of the 2nd end plate member.

  The oil holding portion is configured so that the oil flow is suppressed more than the oil reservoir. By this action, it is possible to exert an effect of suppressing heat reception to the working refrigerant through the second end plate member. Accordingly, heat reception from the oil reservoir to the working refrigerant in the course of suction through the second end plate member can be suppressed, and volume efficiency can be improved. Moreover, the reduction of compression power is realizable by suppressing the heat reception to the working refrigerant in the middle of compression. From these effects, a highly efficient rotary compressor can be provided.

In the second invention, the barrier part forming the oil holding part is formed by the second end plate member or the closing member.

  In the oil holding part formed in a substantially annular shape connected in the circumferential direction, the oil holding part is provided with a barrier so that the oil flow in the circumferential direction is not promoted by the temperature distribution of the oil holding part. The oil flow in the section can be effectively suppressed.

  According to a third aspect of the present invention, the barrier portion includes the first barrier provided on a plane perpendicular to the center axis of the cylinder in the second end plate member and at a position including the vane projection portion that projects the vane. Have.

  In the vicinity of the vanes, the vicinity of the suction path that becomes the lowest temperature when the suction refrigerant that is low temperature is introduced and the discharge hole that becomes the highest temperature when the discharge refrigerant that is compressed and becomes high temperature pass through the vane. Adjacent to each other. That is, a large temperature gradient is generated in the vicinity of the vane as compared with other regions. By providing a barrier in the vane projection part, it is possible to effectively suppress the oil flow generated by the temperature distribution in the oil holding part.

According to a fourth aspect of the present invention, the barrier portion is formed on a plane perpendicular to the central axis of the cylinder of the second end plate member, and the first barrier with the suction passage projection portion projecting the suction passage interposed therebetween. A second barrier provided on the opposite side, wherein one of the oil retaining portions is sandwiched between the first barrier and the second barrier, and is formed at a position within the suction path projection portion a suction passage portion oil retaining portion.

  Since the low-temperature working refrigerant flows along the suction path, the vicinity of the suction path becomes even lower in the second end plate member on the suction path side. By providing an independent oil holding part in the vicinity of the suction path, it becomes possible to keep the held oil at a lower temperature, and heat reception to the working refrigerant in the suction path can be suppressed. In addition, since the vicinity of the suction path is in contact with the low-temperature working refrigerant for a long time, heat reception to the suction refrigerant is further effectively suppressed, and a compressor with high volumetric efficiency can be realized.

  In a fifth aspect, the barrier portion includes a third barrier that divides the oil holding portion into a discharge side oil holding portion and a suction side oil holding portion.

According to a sixth aspect of the present invention, one of the oil retaining portions is viewed from a reference plane including a center line of the vane when the vane protrudes most toward the center axis of the cylinder and the center axis of the cylinder. And formed on the same side as the suction passage.

  Since the suction chamber into which the working refrigerant is sucked from the suction path is in a lower temperature than the discharge chamber, the temperature of the second end plate member on the suction path side corresponding to the suction chamber is relatively low. By forming an independent oil holding portion at such a position, it becomes easy to maintain the held oil at a relatively low temperature state, and it is possible to more effectively suppress heat reception to the suction refrigerant.

  In a seventh aspect of the present invention, a closing member that partitions the oil retaining portion and the oil reservoir is formed.

  By adopting a configuration in which the oil in the oil reservoir and the oil holding portion are partitioned by the closing member, the flow of oil in the oil holding portion is further suppressed, and a highly efficient rotary compressor can be provided.

  In the eighth invention, the closing member is constituted by a single plate-like member. By reducing the number of parts, the part cost, assembly cost, and man-hour can be reduced.

  According to a ninth aspect of the present invention, the closing member or the second end plate member includes an oil communication path through which the oil holding portion and the oil reservoir communicate.

  Thereby, the oil in the oil reservoir can surely flow into the oil holding portion. The effect of the present invention can be stably exhibited by reliably guiding the oil to the oil holding portion. Moreover, since it can prevent that the air at the time of manufacture of a compressor remains in an oil holding | maintenance part, a highly reliable compressor can be provided.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a vertical rotary compressor according to a first embodiment of the present invention. In FIG. 1, the rotary compressor is one in which an electric motor 2 and a compression mechanism unit 3 are connected by a crankshaft 31 and stored in a sealed container 1. The compression mechanism unit 3 includes a cylinder chamber 50 formed by a cylinder 30 and a first end plate member 34 and a second end plate member 35 fixed by fastening bolts so as to close both end faces of the cylinder 30, A piston 32 fitted to the eccentric portion 31a of the crankshaft 31 supported by the end plate member 34 and the second end plate member 35, and a reciprocating motion following the eccentric rotation on the outer periphery of the piston 32, and a cylinder chamber A vane 33 is provided to partition 50 into a suction chamber 49 and a discharge chamber 39.

  On the other hand, the cylinder 30 is provided with a suction passage 40 for sucking the working refrigerant toward the cylinder chamber 50, and the first end plate member 34 receives the working refrigerant from the discharge chamber 39 formed by turning from the suction chamber 49. A discharge hole 38 for discharging is opened. The discharge hole 38 is formed as a circular hole in plan view that passes through the first end plate member 34, and a discharge valve 36 that is released when a pressure of a predetermined size or more is applied to the upper surface of the discharge hole 38. Is provided. A muffler chamber 51 composed of a cup muffler 37 covering the discharge valve 36 and a first end plate member 34 is provided.

On the suction chamber side, the sliding portion of the piston 32 passes through the suction passage 40 and moves away from the suction chamber 49 while gradually expanding, and sucks the working refrigerant from the suction passage 40 into the suction chamber. On the other hand, on the compression chamber side, the piston 32 approaches the discharge hole 38 while gradually reducing the discharge chamber 39, and when compressed to a predetermined pressure or higher, the discharge valve 36 opens and the working refrigerant flows out from the discharge hole 38. The muffler chamber 51 discharges the sealed container 1.

  FIG. 2 is a plan view of the second end plate member in the present embodiment. As shown in FIG. 2, in this specification, the reference plane H1 is defined as follows. A plane including the center line of the vane 33 and the center axis O1 of the cylinder 30 when the vane 33 protrudes most toward the center axis O1 of the cylinder 30 is defined as a reference plane H1. The reference plane H1 passes through the center of the vane groove 30a provided in the cylinder 30. The center axis O1 of the cylinder 30 substantially coincides with the rotation axis center of the crankshaft 31. The vane groove 30 a has an opening facing the cylinder chamber 50. When the position of the center of the opening of the vane groove 30a is defined as the reference position in the circumferential direction of the inner peripheral surface of the cylinder 30, the reference plane H1 may be a plane that passes through this reference position and includes the central axis O1. That is, “the center of the vane groove 30a” means the center of the opening of the vane groove 30a. The reference plane H1 includes a central axis O1 of the cylinder 30 and a contact point (specifically, a tangent line) between the cylinder 30 and the piston 32 when the vane 33 protrudes most toward the central axis O1 of the cylinder 30. It can be. Further, the center axis O1 of the cylinder 30 means the center axis of the cylindrical inner peripheral surface of the cylinder 30 in detail.

  As shown in FIG. 2, the second end plate member 35 has a substantially annular oil retaining portion 53 composed of 53 a, 53 b, and 53 c. The substantially annular oil retaining portion 53 is a concave shape provided in the second end plate member 35 so as to exclude the bolt mounting portion 35a from the central axis O1 of the cylinder 30 to the radially outer side, It is provided so as to surround the periphery of the crankshaft 31. The second end plate member 35 may be formed only on a part of the circumferential direction. The oil holding portion 53 is formed on the opposite side of the cylinder chamber 50 with the second end plate member 35 interposed therebetween. Specifically, the oil holding portion 53 is in contact with the lower surface of the second end plate member 35. The oil retaining portion 53 is configured to take in part of the oil in the oil reservoir 6 and to suppress the flow of oil more than the oil reservoir 6. Therefore, the oil flow in the oil holding part 53 is gentler than the oil flow in the oil reservoir 6. In addition, the shape of the oil holding part 53 is not limited to the shape of the present embodiment.

  In the rotary compressor, since the oil level of the oil reservoir 6 is located above the lower surface of the cylinder 30, the cylinder 30 and the second end plate member 35 are immersed in the oil in the oil reservoir 6. . Accordingly, the oil in the oil reservoir 6 can flow into the oil holding portion 53.

  Specifically, the oil retaining portion 53 suppresses heat reception of the working refrigerant in the cylinder chamber through the second end plate member 35 for the following main reasons. Oil is a liquid and has a high viscosity. Further, the oil flows into the concave portion forming the oil holding portion 53 from the oil reservoir 6 so that the oil flow can be suppressed in the concave portion. Therefore, the oil flow rate in the oil holding portion 53 is slower than the oil flow rate in the oil reservoir 6. In general, since the heat transfer coefficient at the surface of the object is proportional to the square root of the fluid velocity, the heat transfer coefficient at the lower surface of the second end plate member 35 is also small when the oil flow rate of the oil holding part 53 is slow. As a result, the heat gently moves from the oil in the oil holding portion 53 to the second end plate member 35. Since the second end plate member 35 hardly receives heat from the oil, the working refrigerant is also prevented from receiving heat from the second end plate member 35.

Further, a temperature distribution as described below occurs in the second end plate member 35 constituting the oil holding portion 53. The working refrigerant to be compressed in the cylinder chamber 50 is in a low temperature and low pressure state. On the other hand, the compressed working refrigerant is in a high temperature and high pressure state. Therefore, a specific temperature distribution is generated in the second end plate member 35 during the operation of the rotary compressor. Specifically, when the second end plate member 35 is divided into a suction passage side portion and a discharge hole side portion, the suction passage side portion is relatively low temperature, and the discharge hole side portion is relatively high temperature. The suction passage side portion is a portion including a portion directly below the suction passage 40 out of two portions obtained by dividing the second end plate member 35 by the reference plane H1. The discharge hole side portion is a portion including the portion directly below the discharge hole 38 of the two portions.

  As shown in FIG. 2, in the present embodiment, the effect of suppressing heat reception from the oil to the working refrigerant can be improved by providing the oil holding portion 53 at a position corresponding to the above temperature distribution. Details of the oil retaining portion 53 will be described below. In the present embodiment, a plurality of oil retaining portions 53 are formed on the second end plate member 35 on the side opposite to the cylinder 30. A barrier is provided between each of the suction side oil holding part 53a, the discharge side oil holding part 53b, and the suction path oil holding part 53c, and each oil holding part forms an independent space.

  Between the discharge side oil holding part 53b and the suction path part oil holding part 53c, on the plane perpendicular to the central axis O1 of the cylinder 30 in the second end plate member 35 and on the vane projection part 33a that projects the vane 33, A vane portion barrier 35 e extending radially outward from the central axis of the cylinder 30 is formed in the second end plate member 35. In the vicinity of the vanes of the second end plate member 35, the suction refrigerant having a low temperature is introduced, and therefore, the suction path having the lowest temperature and the discharge hole having the highest temperature when the discharge refrigerant compressed to the high temperature passes therethrough. Are adjacent to each other, so that the difference between the high temperature and the low temperature becomes a remarkable region.

  For this reason, the vane part barrier 35e is provided in this area | region, and the heat transfer by oil is suppressed by suppressing the flow of the oil from the discharge side oil holding part 53b which becomes comparatively high temperature to the suction path oil holding part 53c which becomes low temperature. The heat receiving to the working refrigerant can be suppressed.

  The suction passage oil retaining portion 53c is formed on a plane perpendicular to the central axis of the cylinder 30 in the second end plate member 35 and at a position that fits in the suction passage projection 40a that projects the suction passage 40. A barrier 35d is formed between the suction path projection section 40a and the suction side oil holding section 53a in the vicinity of the opposite side of the vane side.

  By providing an independent oil holding part in the vicinity of the suction path that is in the lowest temperature inside the compressor, the oil flow from the discharge-side oil holding part 53b that is relatively high in temperature and the suction path that is relatively low in temperature are provided. Since the flow of oil from the suction side oil holding portion 53a, which is higher than that in the vicinity, can be suppressed, the suction passage portion oil holding portion 53c is kept at a low temperature, and the heat exchange of the working refrigerant in the cylinder chamber in the suction passage 40 is performed. The amount can be minimized.

  Further, the suction side oil holding part 53a and the suction path oil holding part 53c are independently formed on the same side as the suction path 40 as viewed from the reference plane H1. The working refrigerant sucked into the suction chamber 49 from the oil in the oil reservoir 6 through the second end plate member 35 by suppressing the flow of oil in the suction path side portion that is relatively low temperature in the two oil holding portions 53a and 53c. It is possible to suppress heat reception.

  Similarly to the other oil holding portions 53, a discharge-side oil holding portion 53b configured to suppress the flow of oil is also formed on the same side as the discharge hole 38 when viewed from the reference plane H1. Yes. A barrier 35f is also provided between the suction-side oil holding portion 53a and the discharge-side oil holding portion 53b to form an independent space on the discharge side. By suppressing the heat reception to the discharged refrigerant on the discharge chamber side, the pressure rise can be suppressed and the compression power can be reduced. By forming the temperature stratification corresponding to each temperature zone in each oil holding part 53, the heat receiving to the working refrigerant can be effectively suppressed.

Further, in the present embodiment, the oil holding portion 53 formed on the second end plate member 35 is the closing member 1.
Closed at 0. The closing member 10 is composed of a single plate member. Such a structure is very simple and an increase in the number of parts can be avoided. However, all the oil holding portions 53 are not necessarily closed, and the effect of the present invention can be obtained as long as the oil flow in the oil holding portion 53 is suppressed with respect to the oil reservoir 6. The oil retaining portion 53 may be closed by the second end plate member 35 or another member without using the closing member 10.

  As shown in FIG. 3, the second end plate member 35 is further provided with an oil communication path 35b. The oil communication path 35b extends in the lateral direction from each oil space so as to allow the oil reservoir 6 and the oil holding portion 53 to communicate with each other. The oil in the oil reservoir 6 can flow into the oil holding portion 53 through the oil communication path 35b. The size of the oil communication path 35 b is adjusted to a size that is necessary and sufficient for the oil in the oil reservoir 6 to flow into the oil holding portion 53. Therefore, the oil flow in the oil holding portion 53 is suppressed more than the oil flow in the oil reservoir 6. Therefore, the oil forms a relatively stable temperature stratification in the oil holding portion 53. Further, the oil communication path 35 b may be provided in the closing member 10.

  In the present embodiment, the oil communication path 35b is configured by a small through hole. However, the oil communication path 35b may be configured by another structure such as a slit. As shown in FIG. 3, the upper end of the oil communication path 35 b substantially coincides with the upper end of the oil holding portion in the direction parallel to the rotation axis of the crankshaft 31, or from the lower surface 35 c of the second end plate member 35. Is also located above. According to such a configuration, it is possible to prevent air during the manufacture of the compressor from remaining in the oil holding portion 53, and thus it is possible to provide a highly reliable compressor.

  In the present embodiment, the oil holding portion 53 is formed by the second end plate member, but may be formed by the closing member 10 or other members. Further, in the present embodiment, a plurality of oil holding portions are provided, but the effect of the present invention can also be obtained by a single oil holding portion. In the present embodiment, the rotary compressor is a one-piston rotary compressor provided with only one cylinder 30, but the present invention can also be applied to a rotary compressor provided with a plurality of cylinders 30. In this embodiment, the three oil barriers are divided into three by forming three barriers. However, the present invention is not limited to this. For example, two barriers (35d, 35e) are formed. Thus, the oil holding portion may be divided into the suction passage oil holding portion 53c and the other two.

  As described above, the rotary compressor according to the present invention can reduce the leakage loss of the working refrigerant and the sliding loss and heating loss due to excessive oil supply, thereby improving the efficiency of the compressor. Thereby, it can apply also to uses, such as a heat pump type hot-water supply machine, besides the compressor for air conditioners using HFC system operation refrigerant.

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Electric motor 3 Compression mechanism part 6 Oil reservoir 10 Closure member 30 Cylinder 30a Vane groove 31 Crankshaft 31a Eccentric part 32 Piston 33 Vane 33a Vane projection part 34 First end plate member 35 Second end plate member 35a Bolt attachment 35b Oil communication path 35c Lower surface 35d Barrier 35e Vane barrier 35f Barrier 36 Discharge valve 37 Cup muffler
38 Discharge hole 39 Discharge chamber 40 Suction path 40a Suction path projection part 49 Suction chamber 50 Cylinder chamber 51 Muffler chamber 53 Oil holding part 53a Suction side oil holding part 53b Discharge side oil holding part 53c Suction path oil holding part

Claims (9)

A sealed container having an oil reservoir at the bottom, a cylinder disposed inside the sealed container, a piston disposed inside the cylinder, and a cylinder chamber formed between the cylinder and the piston, A first end plate member that closes one end face of the openings at both ends of the cylinder, a second end plate member that closes the other end face, and a vane that partitions the cylinder chamber into a suction chamber and a discharge chamber. A rotary compressor comprising: a suction passage for supplying a working refrigerant to be supplied to the suction chamber; and a muffler chamber provided on the first end plate member side in which the working refrigerant discharged from the discharge chamber can stay. ,
Wherein the second end plate member side oil retaining part for taking a part of the oil of the oil sump is a plurality of configurations in a substantially annular shape, the oil communication path to the respective oil holding portion communicating to the reservoir the oil each A rotary compressor provided separately and independently . The rotary compressor according to claim 1, wherein the barrier portion forming the oil holding portion is formed by the second end plate member or the closing member. The barrier portion, in the second end plate on a plane perpendicular to the central axis of the cylinder in the member, and claim 1 has a first barrier which is provided at a position including the vane vane projecting portion projecting or The rotary compressor according to 2. The barrier portion is provided on a plane perpendicular to the central axis of the cylinder in the second end plate member, and on the opposite side of the first barrier across the suction path projection portion that projects the suction path. Having a second barrier,
The one of the oil holding portions is a suction passage oil holding portion that is sandwiched between the first barrier and the second barrier and is formed at a position that fits in the suction passage projection portion. Rotary compressor. The rotary compressor according to claim 3, wherein the barrier portion includes a third barrier that divides the oil holding portion into a discharge side oil holding portion and a suction side oil holding portion. One of the oil holding portions is the same as the suction passage as seen from a reference plane including the center line of the vane and the center axis of the cylinder when the vane protrudes most toward the center axis of the cylinder. The rotary compressor of any one of Claim 1 to 5 formed in the side. The rotary compressor according to any one of claims 1 to 6, wherein a closing member that partitions the oil holding portion and the oil reservoir is formed. The rotary compressor according to any one of claims 1 to 7, wherein the closing member is constituted by a single plate-like member. The rotary compressor according to any one of claims 1 to 8, wherein an oil communication path through which the oil holding portion and the oil reservoir communicate with each other is provided in the closing member or the second end plate member.