JP2014009612A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem that since formation of a closed space in a cylinder of a rotary compressor is not always easy, another technique capable of effectively suppressing heat receiving of a suction refrigerant is required.SOLUTION: A rotary compressor 100 comprises: a closed vessel 1; a second cylinder 15; a second piston 28; a lower bearing member 7 (end plate member); a second vane 33; a second suction port 20; a second discharge port 41; a second partition member 10; and an oil holding part 53. The second partition member 10 is attached to the lower bearing member 7 so as to form a refrigerant discharge space 52 to be a flow channel of a refrigerant discharged from a second discharge chamber 26b through the second discharge port 41 on opposite side of a second cylinder chamber 26. A first communication path 7p is formed on the lower bearing member 7 so as to bring a part of oil stored in an oil reservoir 22 into the oil holding part 53. The oil holding part 53 is configured so that an upper end 7h is inclined from a horizontal direction and the first communication path 7p is communicated to the upper end 7h.

Description

  The present invention relates to a rotary compressor.

  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 cylinder chamber receiving heat from the surroundings, so-called heat loss, has been proposed. (For example, refer to Patent Document 1).

  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 capable of effectively suppressing the heat reception of the suction refrigerant is desired, and an object of the present invention is to provide a technique for improving the reliability of the rotary compressor.

  That is, in the present invention, a sealed container having an oil reservoir at the bottom, a cylinder disposed inside the sealed container, a compression mechanism including a piston, and a cylinder chamber is formed between the cylinder and the piston. A bearing member attached to the cylinder; a vane that divides the cylinder chamber into a suction chamber and a discharge chamber; a suction port that guides the refrigerant to be compressed to the suction chamber; and the bearing member. A discharge port that discharges the discharged refrigerant from the discharge chamber and the bearing member, and together with the bearing member, forms a refrigerant discharge space in which the refrigerant discharged from the discharge chamber through the discharge port can stay or stay. A partition member, and the bearing member includes a center of the vane when the vane protrudes most toward a center axis of the cylinder, and the A first recess and a communication path for taking in a part of the oil stored in the oil reservoir are provided on the same side as the suction port as viewed from a reference plane including the central axis of the cylinder, and are stored in the oil reservoir. An oil holding portion is formed by a part of the oil entering the first recess, the upper end surface of the oil holding portion is inclined with respect to the horizontal direction, and the communication path is the outermost portion of the oil holding portion. Provided is a rotary compressor provided at an upper end portion.

  According to the rotary compressor of the present invention, since the oil holding portion is provided with an inclination so that the gas does not accumulate, poor vacuuming at the time of equipment installation or refrigerant gas mixed into the oil at the time of equipment operation accumulates. It is possible to suppress a decrease in reliability due to the inclusion.

1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1 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. The expanded sectional view which shows the position of the communicating path of the rotary compressor Bottom view of lower bearing member of the rotary compressor The expanded sectional view of the lower shaft member of the rotary compressor concerning Embodiment 2 of the present invention. The bottom view of the lower bearing member which shows the structure of the guide groove of the rotary compressor which concerns on Embodiment 3 of this invention.

  According to a first aspect of the present invention, a sealed container having an oil reservoir at a bottom portion, a cylinder disposed inside the sealed container, a compression mechanism including a piston, and a cylinder chamber formed between the cylinder and the piston. A bearing member attached to the cylinder; a vane that divides the cylinder chamber into a suction chamber and a discharge chamber; a suction port that guides the refrigerant to be compressed to the suction chamber; and the bearing member. A discharge port that discharges the discharged refrigerant from the discharge chamber and the bearing member, and together with the bearing member, forms a refrigerant discharge space in which the refrigerant discharged from the discharge chamber through the discharge port can stay or stay. A partition member, and the bearing member includes a center of the vane when the vane protrudes most toward a central axis of the cylinder and the cylinder. The first recess and a communication passage for taking in part of the oil stored in the oil reservoir are provided on the same side as the suction port as viewed from a reference plane including the central axis, and the oil stored in the oil reservoir An oil holding portion is formed by intrusion into a part of the first recess, an upper end surface of the oil holding portion is inclined with respect to a horizontal direction, and the communication path is an uppermost end portion of the oil holding portion. Since the gas existing in the oil space can be guided to the communication path along the inclination of the upper end surface, the equipment reliability is ensured by the residual air remaining in the oil holding part by evacuation when installing the equipment. The oil level is unstable due to the decrease in performance, the refrigerant gas mixed into the oil during operation of the equipment, and the difference due to biting into the sliding part when the accumulated refrigerant gas escapes at once. It is possible to prevent the occurrence of wear.

  In particular, according to the second aspect of the present invention, in the rotary compressor of the first aspect, there are a plurality of communication passages, and at least one is in communication with the uppermost end portion other than the uppermost end portion of the oil holding portion. The communication passage mainly contributes to the action of releasing the gas present in the oil holding portion to the oil reservoir, and the communication passage communicating with other than the uppermost end plays a role of flowing oil into the oil holding portion. For this reason, bubbles and oil do not go back and forth in the same communication path, the gas in the oil holding part flows out reliably, and the oil can surely flow into the oil holding part.

  According to a third aspect of the invention, in particular, in the rotary compressor of the first aspect of the invention, by providing a guide groove on the upper end face of the oil holding part to guide the gas in the oil holding part to the communication path, the generated bubbles are guided. It is taken into the groove and can surely flow out of the oil holding space.

  In a fourth aspect of the invention, in particular, in the rotary compressor according to any one of the first to third aspects of the invention, the bearing member is made of a metal sintered member, so that the shape of the upper end surface, the guide groove, etc. can be machined. Therefore, it can be realized at low cost.

  According to a fifth aspect of the invention, in particular, in the rotary compressor of the fourth aspect of the invention, the surface of the upper end surface of the oil holding part is sealed so that the gas generated in the oil holding part passes through the lower bearing member. Therefore, it is possible to prevent a heat receiving loss that occurs when the gas flows into the cylinder chamber, and a sliding abnormality caused by gas engagement that occurs when the gas flows into the bearing sliding portion.

  In the sixth aspect of the invention, in particular, in the rotary compressor according to any one of the first to fifth aspects, the surface of the upper end face of the oil holding portion is subjected to lipophilic treatment, so that the gas is less likely to stay on the upper end face. The gas in the oil holding part can be surely discharged.

  In the seventh aspect of the invention, in particular, in the rotary compressor according to any one of the first to sixth aspects, the oil and refrigerant are compatible with each other, so that the refrigerant dissolved in the oil is changed by temperature change or pressure change. Since it is easy to foam, the effect which prevents the accumulation of the gas to an oil holding part is exhibited more notably.

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

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a rotary compressor according to a first embodiment of the present invention.

  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 above 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 and rotates together with the shaft 4.

  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.

  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 partition member 9 (a first muffler member or a first closing member). ) And a second partition member (second muffler member or second closing 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 in the vertical direction.

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. Inside the first cylinder 5, a first piston 8 is attached to the first eccentric part 4a. Inside the second cylinder 15, the second piston 28 is connected to the second eccentric portion 4b.
Is attached. 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. ing. 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. ing. 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. A second discharge valve 44 is provided at the second discharge port 41 so as to open and close the second discharge port 41.

  A first vane (blade) 32 is slidably disposed in the first vane groove 34. The first vane 32 partitions the first cylinder chamber 25 along the circumferential direction of the first piston 8. That is, the first cylinder chamber 25 is partitioned into the first suction chamber 25a and the first discharge chamber 25b. A second vane (blade) 33 is arranged in the second vane groove 35 so that it can slide. The second vane 33 partitions the second cylinder chamber 26 along the circumferential direction of the second piston 28. That is, 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. The detailed model of the rotary compressor is not particularly limited, and various models such as a rolling piston type and a swing piston type can be widely adopted.

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 internal 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. Further, the lubricating oil stored in the oil reservoir 22 is supplied to the first vane groove 34 and the second vane groove 35.

  As shown in FIG. 1, the first partition member 9 is a first cylinder as viewed from the upper bearing member 6 in the refrigerant discharge space 51 in which the refrigerant discharged from the first discharge chamber 25 b through the first discharge port 40 can stay or stay. It is attached to the upper bearing member 6 (first end plate member) so as to be formed on the opposite side of the chamber 25. Specifically, the first partition 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 partition member 9 forms a refrigerant discharge space 51 together with the upper bearing member 6. The first discharge valve 43 is covered with the first partition member 9. The first partition 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 second partition member 10 forms a refrigerant discharge space 52 in which the refrigerant discharged from the second discharge chamber 26 b through the second discharge port 41 can stay or stay on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 7. As shown, the lower bearing member 7 (second end plate member) is attached. Specifically, the second partition member 10 is attached to the lower portion of the lower bearing member 7 so that the refrigerant discharge space 52 is formed below the lower bearing member 7. The second partition member 10 forms a refrigerant discharge space 52 together with the lower bearing member 7. The second discharge valve 44 is covered with the second partition 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 partition member 9 and the central portion of the second partition member 10, and is rotatably supported by the upper bearing member 6 and the lower bearing member 7.

  The refrigerant discharge space 52 communicates with the refrigerant discharge space 51 through the through channel 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 in the second compression block 30 merges with the refrigerant compressed in the first compression block 3 in the internal space of the first partition member 9, that is, in 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 partition 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 this specification, the first reference plane H ₁ , the second reference plane H _2, and the third reference plane H ₃ are defined as follows. A plane including the center of the second vane 33 and the center axis O ₁ of the second cylinder 15 when the second vane 33 protrudes most toward the center axis O ₁ of the second cylinder 15 is a first reference plane H ₁ . Define. The first reference plane H ₁ passes through the center of the second vane groove 35. A plane including the central axis O ₁ and perpendicular to the first reference plane H ₁ is defined as a second reference plane H ₂ . A plane including the center of the second inlet 20 and the central axis O ₁ is defined as a third reference plane H ₃ . 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.

The second vane groove 35 has an opening facing the second cylinder chamber 26. In the circumferential direction of the inner peripheral surface of the second cylinder 15, when the position of the center of the opening of the second vane groove 35 is defined as a reference position, a first reference plane H ₁ passes this reference position, the center axis O ₁ It may be a plane including That is, “the center of the second vane groove 35” means the center of the opening of the second vane groove 35. The first reference plane H ₁ includes the center axis O ₁ of the second cylinder 15 and the second cylinder 15 and the second piston 28 when the second vane 33 protrudes most toward the center axis O ₁ of the second cylinder 15. And a contact point (in detail, a tangent line). Further, the central axis O ₁ of the second cylinder 15 means the central axis of the cylindrical inner peripheral surface of the second cylinder 15 in detail.

As shown in FIG. 1, the compression mechanism 102 further includes an oil holding portion 53. Oil holding portion 53 is located on the same side as the second suction port 20 as viewed from the first reference plane H _1, it comprises a first recess 7t provided below the bearing member 7. The oil retaining portion 53 is formed on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 7. 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 formed by a part of the oil stored in the oil reservoir 22 entering the first recess 7t through the first communication path 7p described later. The oil holding part 53 is configured such that the oil flow in the oil holding part 53 is suppressed 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 100, 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 partition member 10 are immersed in the oil in the oil reservoir 22. Accordingly, the oil in the oil reservoir 22 can enter the oil holding portion 53 (first recess 7t) through the first communication passage 7p.

By the way, 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 has a relatively low temperature and the discharge side portion has a relatively high temperature. Suction side portion of the two portions obtained by dividing the lower bearing member 7 in a first reference plane H _1, a portion including a portion just below the second inlet 20. A discharge side part is a part in which the 2nd discharge port 41 is provided among two parts.

In the present embodiment, the oil holding portion 53 on the same side as the second suction port 20 as viewed from the first reference plane H ₁ is formed. 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 (intake refrigerant) sucked into the second cylinder chamber 26 from the refrigerant (compressed refrigerant) in the refrigerant discharge space 52 through the lower bearing member 7. It is possible to suppress the movement of heat. 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 FIG. 1 and the like, in the present embodiment, the oil retaining portion 53 is formed by closing the first recess 7t formed in the lower bearing member 7 by the second partition member 10, and the oil retaining The upper end surface 7 h of the portion 53 is inclined so that the first communication path 7 p is the uppermost portion of the oil holding portion 53. According to such a structure, the gas existing in the oil space can be guided to the first communication path 7p along the inclination of the upper end surface 7h. Deterioration of device reliability due to remaining, coolant level destabilization of the oil reservoir 22 due to accumulation of refrigerant gas mixed in oil during operation of the device, and biting into the sliding portion when the accumulated refrigerant gas escapes at once The occurrence of abnormal wear due to this can be prevented.

  The size of the first 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. For example, when the hydraulic equivalent diameter of the first communication passage 7p is Dp, it is preferable that 1 mm ≦ Dp ≦ 10 mm. For this reason, the oil flow in the oil holding portion 53 is surely 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.

  The lower bearing member 7 may be formed of a metal sintered member. By using a sintered metal member for the lower bearing member 7, the shape of the inclination of the upper end surface 7 h can be manufactured without machining, so that it can be realized at low cost.

  Alternatively, a metal sintered member obtained by sealing the surface of the upper end surface 7h of the oil holding portion 53 may be used. According to such a configuration, it is possible to prevent the gas generated in the oil holding portion 53 from passing through the lower bearing member 7, so that the heat receiving loss generated by flowing into the second cylinder chamber 26 and the bearing slide Sliding abnormalities due to gas biting generated by flowing into the moving part can be prevented.

  Further, the surface of the upper end surface 7 h of the oil holding portion 53 may be subjected to a lipophilic surface treatment. According to such a configuration, it is difficult for the gas to stay on the upper end surface 7h, and the gas in the oil holding portion 53 can be reliably discharged.

  Further, the oil and the refrigerant may be compatible. In the rotary compressor 100 using such a refrigerant and oil, since the refrigerant dissolved in the oil is easily foamed due to a temperature change or a pressure change, accumulation of gas in the oil holding portion 53 according to the present embodiment is prevented. The effect is more remarkable.

(Embodiment 2)
FIG. 6 is an enlarged cross-sectional view of a lower shaft member of the rotary compressor according to the second embodiment of this invention. Hereinafter, configurations having the same functions as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

  In the second embodiment, a plurality of communication paths between the oil reservoir 22 and the oil retaining portion 53 are provided, and at least one of them is provided other than the upper end surface 7h. In FIG. 6, when there are two communication paths, the first communication path 7 p is provided so as to communicate with the upper end surface 7 h of the lower bearing member 7, and the second communication path 7 q is provided in the second partition member 10. According to such a configuration, the first communication path 7p mainly contributes to the action of releasing the gas present in the oil holding part 53 to the oil reservoir 22, and the second communication path flows oil into the oil holding part 53. Take a role. For this reason, bubbles and oil do not go back and forth in the same communication path, the gas in the oil holding part 53 can be surely flowed out, and the oil can surely flow into the oil holding part 53.

(Embodiment 3)
FIG. 7 is a bottom view of the lower bearing member showing the configuration of the guide groove of the rotary compressor according to the third embodiment of the present invention. Hereinafter, configurations having the same functions as those of the first and second embodiments are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 7, in the second embodiment, the rotary compressor 100 has a guide groove that guides the gas in the oil holding part 53 to the first communication path 7p on the upper end surface 7h of the oil holding part 53. 7r is provided. According to such a configuration, the generated bubbles are taken into the guide groove 7 r and can surely flow out from the oil holding portion 53.

  Similar to the above-described embodiment, by using a metal sintered member for the lower bearing member 7, the shape of the guide groove 7r and the like can be manufactured without machining, so that it can be realized at low cost. .

  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.

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 1st communicating path 7q 2nd communicating path 7r Guide groove 7t 1st Concave part 8 First piston 9 First partition member 10 Second partition 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 44 Second discharge valve 46 Through passage 51, 52 Refrigerant discharge space 53 Oil holding part 100 Rotary compressor 102 Compression mechanism H ₁ First reference plane H ₂ Second reference plane H ₃ Third reference plane

Claims (7)

An airtight container having an oil reservoir at the bottom;
A compression mechanism comprising a cylinder and a piston disposed inside the sealed container;
A bearing 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 leading the refrigerant to be compressed to the suction chamber;
A discharge port that is formed in the bearing member and discharges the compressed refrigerant from the discharge chamber;
A partition member which is attached to the bearing member and forms a refrigerant discharge space in which the refrigerant discharged from the discharge chamber through the discharge port can stay or stay together with the bearing member;
The bearing member has a first side on the same side as the inlet as viewed from a reference plane including the center of the vane when the vane protrudes most toward the center axis of the cylinder and the center axis of the cylinder. A recess, and a communication path for taking in part of the oil stored in the oil reservoir,
An oil holding part is formed by a part of the oil stored in the oil reservoir entering the first recess,
The rotary compressor according to claim 1, wherein an upper end surface of the oil holding portion is inclined with respect to a horizontal direction, and the communication path is provided at an uppermost end portion of the oil holding portion. 2. The rotary compressor according to claim 1, wherein there are a plurality of the communication passages, and at least one of the communication passages is located at a portion other than an uppermost end portion of the oil holding portion. The rotary compressor according to claim 1, wherein a guide groove that guides gas in the oil holding portion to the communication path is provided on an upper end surface of the oil holding portion. The rotary compressor according to any one of claims 1 to 3, wherein the bearing member is a sintered metal. The rotary compressor according to claim 4, wherein a surface of the upper end face of the oil holding portion is sealed. The rotary compressor according to any one of claims 1 to 5, wherein a surface of an upper end face of the oil holding portion is subjected to a lipophilic treatment. The rotary compressor according to any one of claims 1 to 5, wherein the oil and the refrigerant are compatible with each other.