CN102312816A - Hermetic type compressor and refrigerating circulatory device - Google Patents

Abstract

The invention provides a hermetic compressor and a refrigeration cycle device, which can improve the performance of the hermetic compressor. The hermetic compressor (2) accommodates a compression mechanism unit (9) and a motor unit (10) in an airtight container (2a), and includes a mechanism for discharging gas refrigerant compressed by the compression mechanism unit (9) into the airtight container (2a). ) The external discharge passage (12), the compression mechanism part (9) includes: a partition (16); a pair of cylinders (17, 18), and the pair of cylinders (17, 18) are located on the upper and lower sides of the partition (16) Both sides and have cylinder chamber (21, 25); discharge chamber (19), this discharge chamber (19) is formed in the partition (16); discharge valve (20a, 20b), this discharge valve (20a, 20b) installs In the discharge chamber (19), discharge holes for discharging gas refrigerant compressed in the cylinder chambers (21, 25) into the discharge chamber (19) are opened and closed. A discharge port (31) communicating the discharge chamber (19) with the discharge passage (12) is formed on the lower side of the discharge chamber (19).

Description

Hermetic compressor and refrigeration cycle device

technical field

The invention relates to a hermetic compressor and a refrigeration cycle device.

Background technique

As a hermetic compressor in which a compression mechanism for compressing gaseous refrigerant and a motor for driving the compression mechanism are housed in an airtight container, and the compression mechanism includes a partition and a pair of cylinders arranged up and down through the partition, for example A hermetic compressor described in Patent Document 1 below is known.

According to the hermetic compressor described in Patent Document 1, the discharge chamber is formed in the separator, and the gas refrigerant compressed in the cylinder chamber of each cylinder is discharged into the discharge chamber. The gas refrigerant discharged from each cylinder into the discharge chamber is discharged to the outside of the airtight container through a discharge port formed in the separator, and is supplied to the heat exchanger.

A discharge hole for discharging gas refrigerant compressed in the cylinder chamber into the discharge chamber is provided on the partition plate, and a discharge valve is provided in the discharge chamber to prevent the gas refrigerant in the discharge chamber from flowing back into the cylinder chamber.

In addition, a discharge port for the gas refrigerant discharged from the discharge chamber is formed on the upper side of the separator.

Patent Document 1: Japanese Patent Laid-Open No. 10-213087

The gas refrigerant compressed in the cylinder chamber contains lubricating oil for lubricating the sliding parts of the cylinder, and the lubricating oil is discharged into the discharge chamber together with the compressed gas refrigerant.

Since the discharge port is formed on the upper side of the partition plate, the lubricating oil discharged into the discharge chamber is less likely to be discharged outside the discharge chamber, and gradually accumulates in the discharge chamber.

Once the lubricating oil accumulates in the discharge chamber, the accumulated lubricating oil hinders the opening and closing of the discharge valve or the flow of the gas refrigerant in the discharge chamber, thereby reducing the performance of the hermetic compressor.

Contents of the invention

An object of the present invention is to improve the discharge performance of gas refrigerant from a cylinder chamber into a discharge chamber formed in a partition, and improve the discharge performance of gas refrigerant from the discharge chamber, thereby improving the performance of a hermetic compressor.

According to the hermetic compressor of the present invention, the compression mechanism part and the motor part connected by the rotating shaft having the shaft center in the vertical direction are accommodated in the airtight container, and the pressure of the space in the above-mentioned airtight container is set so as to be consistent with the pressure of the suction to the above-mentioned compression mechanism part. The suction pressure is the same, and includes a discharge passage for discharging the gas refrigerant compressed by the above-mentioned compression mechanism to the outside of the above-mentioned airtight container. The above-mentioned hermetic compressor is characterized in that the above-mentioned compression mechanism includes: a partition; The pair of cylinders are arranged on the upper and lower sides of the above-mentioned partition, and respectively have a cylinder chamber; a discharge chamber, which is formed in the above-mentioned partition; and a discharge valve, which is installed in the above-mentioned discharge chamber, and is opened and closed by the Gas refrigerant compressed in the cylinder chamber is discharged to a discharge hole in the discharge chamber, and a discharge port communicating the discharge chamber and the discharge passage is formed at a lower side of the discharge chamber.

Description of drawings

FIG. 1 is a schematic diagram showing a refrigeration cycle of an air conditioner as a refrigeration cycle device according to a first embodiment of the present invention.

Fig. 2 is a longitudinal sectional front view showing the internal structure of the hermetic compressor according to the first embodiment of the present invention.

Fig. 3(a) is a plan view showing an upper partition according to the first embodiment of the present invention, and Fig. 3(b) is a plan view showing a lower partition according to the first embodiment of the present invention.

Fig. 4 is a plan view showing a lower partition plate according to a second embodiment of the present invention.

Fig. 5 is a plan view showing a lower partition plate according to a third embodiment of the present invention.

Fig. 6 is a longitudinal sectional front view showing a compression mechanism unit according to a fourth embodiment of the present invention.

Fig. 7 is a longitudinal sectional front view showing a compression mechanism unit according to a fifth embodiment of the present invention.

(Symbol Description)

2 hermetic compressors

2a airtight container

3 oil separator

5 heat source side heat exchanger (outdoor heat exchanger)

6 expansion device

7 Utilization side heat exchanger (indoor heat exchanger)

9 Compression Mechanism Department

10 Motor Department

11 shafts

12 Discharge passage (refrigerant discharge pipe)

16 partitions

17, 18 cylinders

19 discharge chamber

20a, 20b discharge valve

21 cylinder chamber

25 cylinder chamber

29a, 29b discharge holes

31 outlet

41 guide groove

42 valve seat depression

51 depression

61 supply channel

63a upper side supply path

64a lower side supply path

65 thrust bearing

Detailed ways

Embodiments of the present invention will be described below using the drawings.

(first embodiment)

A first embodiment of the present invention will be described based on FIGS. 1 to 3 . The refrigerating cycle device, that is, the air conditioner 1, is a closed compressor 2, an oil separator 3, a four-way valve 4, an outdoor heat exchanger 5, an expansion device 6, and an indoor heat exchanger 7, as shown in the refrigerating cycle diagram in Figure 1. And the storage tank 8 is connected to form a ring, wherein the above-mentioned outdoor heat exchanger 5 is a heat source side heat exchanger that functions as a condenser in cooling operation and an evaporator in heating operation, and the indoor The heat exchanger 7 is a use-side heat exchanger that functions as an evaporator during cooling operation and a condenser during heating operation.

In the air conditioner 1 described above, during cooling operation, the high-pressure gas refrigerant is discharged from the hermetic compressor 2, flows as indicated by the solid arrow, and flows into the outdoor heat exchanger through the oil separator 3 and the four-way valve 4. (condenser) 5, and is condensed after exchanging heat with the outdoor air in the outdoor heat exchanger 5.

The condensed refrigerant flows into the indoor heat exchanger (evaporator) 7 via the expansion device 6, exchanges heat with the indoor air in the indoor heat exchanger 7, and evaporates to cool the indoor air. The evaporated gas refrigerant is sucked into the hermetic compressor 2 via the four-way valve 4 and the accumulator 8 .

On the other hand, during the heating operation, the high-pressure gas refrigerant is discharged from the hermetic compressor 2, flows according to the dotted arrow, and flows into the indoor heat exchanger (condenser) 7 through the oil separator 3 and the four-way valve 4 and condenses after exchanging heat with the indoor air in the indoor heat exchanger 7, thereby heating the indoor air.

The condensed refrigerant flows into the outdoor heat exchanger (evaporator) 5 via the expansion device 6, and exchanges heat with the outdoor air in the outdoor heat exchanger 5 to evaporate. The evaporated gas refrigerant is sucked into the hermetic compressor 2 via the four-way valve 4 and the accumulator 8 .

By continuing the refrigerant circulation as described above, the cooling operation or heating operation of the air conditioner 1 can be continued.

As shown in FIG. 2, the hermetic compressor 2 has a hermetic container 2a, and the compression mechanism part 9 and the motor part 10 are accommodated in this hermetic container 2a. The compression mechanism part 9 and the motor part 10 are arranged so that the compression mechanism part 9 is located on the lower side and the motor part 10 is located on the upper side. The unit 10 drives the compression mechanism unit 9 .

The oil separator 3 is provided midway in the refrigerant discharge pipe 12 , which is a discharge passage for discharging the gas refrigerant compressed by the compression mechanism 9 to the outside of the airtight container 2 a, and separates lubricating oil contained in the gas refrigerant. The lubricating oil separated by the oil separator 3 is supplied to the sliding part of the compression mechanism part 9 via the oil return pipe 13 constituting the oil supply passage.

The motor unit 10 has a rotor 10a and a stator 10b, the stator 10b is fixed to the inner peripheral portion of the airtight container 2a, and the rotor 10a is rotatably arranged inside the stator 10b. A rotating shaft 11 is fixed to a central portion of the rotor 10 a, and the rotating shaft 11 is rotatably supported by a main bearing 14 and a sub bearing 15 . Furthermore, the rotary shaft 11 is formed with a pair of eccentric portions 11a, 11b.

The compression mechanism part 9 is a part that compresses the low-pressure gas refrigerant to become a high-pressure high-temperature gas refrigerant, and includes: a partition 16 having an upper side partition 16 a and a lower side partition 16 b; A pair of upper and lower cylinders 17, 18; a discharge chamber 19 formed in the partition 16; and discharge valves 20a, 20b installed in the discharge chamber 19 to open and close discharge holes 29a, 29b (see FIG. 3).

The cylinder 17 has a cylinder chamber 21 whose upper end side is closed by the support shaft 14 and whose lower end side is closed by the partition plate 16 . In this cylinder chamber 21, the eccentric part 11a of the rotating shaft 11 is arrange|positioned, and the eccentric part 11a is fitted with the cylinder (roller) 22a.

In addition, a plate (not shown) that partitions the interior of the cylinder chamber 21 into a high-pressure side and a low-pressure side is provided in the cylinder 17 . This plate is slidably held and is biased by a biasing body such as a spring so that the front end thereof comes into contact with the outer peripheral surface of the cylinder 22a.

Moreover, the cylinder chamber 21 is connected with the refrigerant|coolant suction pipe 24a which sucks the refrigerant which circulates in the air conditioner 1 into the cylinder chamber 21. This refrigerant suction pipe 24a is connected to the airtight container 2a so that the pressure of the space in the airtight container 2a is set to be the same as the suction pressure into the compression mechanism part 9 .

The cylinder 18 has a cylinder chamber 25 whose upper end side is closed by the partition plate 16 and whose lower end side is closed by the sub bearing 15 . The eccentric part 11b of the rotating shaft 11 is arrange|positioned in this cylinder chamber 25, and the cylinder 22b is fitted in the eccentric part 11b.

In addition, a plate (not shown) that partitions the inside of the cylinder chamber 25 into a high-pressure side and a low-pressure side is provided in the cylinder 18 . This plate is slidably held and is biased by a biasing body such as a spring so that the front end thereof comes into contact with the outer peripheral surface of the cylinder 22b.

Moreover, the cylinder chamber 25 is connected to the refrigerant suction pipe 24b which sucks the refrigerant circulating in the air conditioner 1 into the cylinder chamber 25. As shown in FIG. This refrigerant suction pipe 24b also communicates with the inside of the airtight container 2a similarly to the refrigerant suction pipe 24a.

The partition 16 is formed by joining the upper partition 16a and the lower partition 16b.

Fig. 3 shows the upper side partition 16a and the lower side partition 16b after separating the joined state of the partition 16, Fig. 3 (a) is a plan view showing the upper side partition 16a, Fig. 3 (b) is a top view showing the lower side partition Top view of plate 16b.

The upper side partition plate 16a has a through hole 26a formed in the center portion through which the rotating shaft 11 is inserted, and a concave portion 27a is formed around the through hole 26a. The lower side partition 16b has a through hole 26b formed in the center portion through which the rotation shaft 11 is inserted, and a recessed portion 27b is formed around the through hole 26b.

Moreover, the discharge chamber 19 is formed by the opposing recessed part 27a, 27b by joining the upper part side partition plate 16a and the lower part side partition plate 16b in the direction which makes recessed part 27a, 27b oppose.

A plurality of fixing screw holes 28 through which screws for assembling the compression mechanism part pass are formed in the upper part side partition plate 16a and the lower part side partition plate 16b.

A discharge hole 29 a is formed in the upper partition plate 16 a to communicate the cylinder chamber 21 and the discharge chamber 19 to discharge high-pressure gas refrigerant compressed in the cylinder chamber 21 into the discharge chamber 19 . A discharge valve 20 a that opens and closes a discharge hole 29 a is attached to the upper surface of the discharge chamber 19 , that is, the surface of the recess 27 a.

A discharge hole 29 b is formed in the lower partition plate 16 b to communicate the cylinder chamber 25 with the discharge chamber 19 and discharge the high-pressure gas refrigerant compressed in the cylinder chamber 25 into the discharge chamber 19 .

A discharge valve 20 b that opens and closes a discharge hole 29 b is attached to the lower surface of the discharge chamber 19 , that is, the surface of the recess 27 b. In addition, a discharge port 31 is formed in the lower partition plate 16b, and the discharge chamber 19 communicates with the refrigerant discharge pipe 12 through the discharge port 31 .

In addition, an oil supply groove 32 is formed on the joint surface of the upper side partition plate 16a and the lower part side partition plate 16b. The oil supply groove 32 constitutes an oil supply passage together with the oil return pipe 13, and supplies lubricating oil supplied from the oil separator 3 to the space between the inner peripheral surface of the through holes 26a, 26b and the outer peripheral surface of the rotary shaft 11 through the oil return pipe 13. sliding part.

In the above configuration, when the air conditioner 1 is in operation, the motor unit 10 is driven to rotate the rotating shaft 11, and the cylinder chambers 21, 25 are rolled in the cylinder chambers 22a, 22b fitted with the eccentric portions 11a, 11b.

In addition, by rolling cylinders 22a, 22b in cylinder chambers 21, 25, low-pressure gas refrigerant is sucked into cylinder chambers 21, 25 from refrigerant suction pipes 24a, 24b, and compressed.

Gas refrigerant compressed in the cylinder chambers 21 , 25 is discharged into the discharge chamber 19 by opening the discharge valves 20 a , 20 b , and discharged from the discharge chamber 19 into the refrigerant discharge pipe 12 through the discharge port 31 .

The gas refrigerant discharged into the refrigerant discharge pipe 12 flows into the outdoor heat exchanger 5 or the indoor heat exchanger 7 via the oil separator 3 and the four-way valve 4 .

The gas refrigerant compressed in the cylinder chambers 21 and 25 contains lubricating oil for lubricating sliding parts in the compression mechanism portion 9 , and the lubricating oil is discharged into the discharge chamber 19 together with the gas refrigerant.

Here, a discharge port 31 communicating with the discharge chamber 19 and the refrigerant discharge pipe 12 is formed on the lower side of the discharge chamber 19 . Therefore, the lubricating oil discharged into the discharge chamber 19 together with the gas refrigerant is discharged from the discharge port 31 into the refrigerant discharge pipe 12 together with the gas refrigerant without being accumulated in the discharge chamber 19 .

Therefore, there will be no lubricating oil accumulated in the discharge chamber 19, and the opening and closing of the discharge valves 20a and 20b will not be blocked or the gas in the discharge chamber 19 will not be blocked due to the lubricating oil accumulated in the discharge chamber 19. The flow of the refrigerant is blocked, so that the performance of the hermetic compressor 2 can be maintained in a good state.

In addition, lubricating oil contained in the gas refrigerant for lubricating the sliding parts in the compression mechanism part 9 is discharged into the refrigerant discharge pipe 12 without being accumulated in the discharge chamber 19, and is absorbed by the oil. After being separated by the separator 3 , the oil is supplied to the sliding portion of the compression mechanism unit 9 through the oil return pipe 13 .

Therefore, the lubricating oil for lubricating the sliding portion of the compression mechanism portion 9 does not become insufficient due to the lubricating oil being accumulated in the discharge chamber 19 , and the sliding portion of the compression mechanism portion 9 can be well lubricated.

(second embodiment)

A second embodiment of the present invention will be described based on FIG. 4 . In addition, in this embodiment and other embodiments described below, the same reference numerals are attached to the same components as those in the embodiment described above, and redundant descriptions will be omitted.

The basic structure of the second embodiment is the same as that of the first embodiment. The difference between the second embodiment and the first embodiment is that in the second embodiment, a guide groove 41 is formed in the lower side partition plate 16b.

On the lower surface of the discharge chamber 19 , that is, the bottom surface of the recess 27 b of the lower side partition 16 b, a valve seat recess 42 is formed at a mounting position of the discharge valve 20 b. The valve seat recessed portion 42 is formed to be more recessed than the rest of the bottom surface portion of the recessed portion 27b. In addition, a recessed path connecting the seat recess 42 and the discharge port 31 is formed as a guide groove 41 on the bottom surface of the recess 27b.

In the above structure, lubricating oil tends to accumulate in the valve seat recess 42 located on the lower side inside the discharge chamber 19 . The lubricating oil accumulated in the seat recess 42 flows through the guide groove 41 to the discharge port 31 , and is discharged from the discharge port 31 into the refrigerant discharge pipe 12 .

Therefore, by forming the guide groove 41, it is possible to prevent lubricating oil from accumulating in the valve seat recess 42 and obstructing the opening and closing of the discharge valve 20b, and to maintain the performance of the hermetic compressor 2 in a good state.

(third embodiment)

A third embodiment of the present invention will be described based on FIG. 5 . The basic structure of the third embodiment is the same as that of the first embodiment, and the difference between the third embodiment and the first embodiment is that the third embodiment has a plurality of recessed parts 51 formed on the lower side partition plate 16b and is different from the first embodiment. The guide groove 41 is similarly formed in the second embodiment.

The width dimension of the discharge chamber 19 between the installation position of the discharge valve 20b in the discharge chamber 19 and the discharge port 31 is not constant, but narrows in the region where the fixing screw hole 28 is formed.

On the lower surface of the discharge chamber 19 , that is, on the bottom surface of the recess 27 b of the lower partition plate 16 b , a recessed portion 51 located at a narrower portion of the discharge chamber 19 is formed. The recessed portion 51 is formed to be more recessed than the rest of the bottom surface portion of the recessed portion 27b.

Moreover, the guide groove 41 connects the valve seat recessed part 42 located in the bottom surface part of the recessed part 27b, and the discharge port 31, and connects the several recessed parts 51 together.

In the above structure, the gas refrigerant discharged into the discharge chamber 19 from the discharge hole 29b located at the installation position of the discharge valve 20b flows in the discharge chamber 19 toward the discharge port 31, but from the installation position of the discharge valve 20b to the discharge port 31 The width dimension of the discharge chamber 19 between them is not constant, but narrows in the region where the fixing screw hole 28 is formed. Therefore, unless some measure is taken, the passage resistance when the gas refrigerant flows may become large in this narrowed region.

Therefore, as in the present embodiment, by forming the recessed portion 51 , it is possible to achieve uniformity of the passage area from the mounting position of the discharge valve 20 b to the discharge port 31 .

Thereby, it is possible to eliminate the portion where the passage resistance increases when the gas refrigerant flows in the discharge chamber 19 , so that the performance of the hermetic compressor 2 can be maintained in a good state.

In addition, since the guide groove 41 is formed by linking these recessed parts 51 , it is possible to prevent the lubricating oil from accumulating in the recessed parts 51 and narrowing the passage area.

In addition, in this embodiment, the case where the recessed part 51 is formed in the lower side partition 16b is mentioned as an example and demonstrated, However, You may form it only in the upper surface part of the discharge chamber 19, ie, the upper side partition 16a. The surface part of the recessed part 27a may be formed in both the upper part side partition board 16a and the lower part side partition board 16b.

(fourth embodiment)

A fourth embodiment of the present invention will be described based on FIG. 6 . The basic structure of the fourth embodiment is the same as that of the first embodiment, and the difference between the fourth embodiment and the first embodiment is that a lubricating oil accumulated at the bottom of the airtight container 2a is provided to the suction side of the compression mechanism part 9. The supply path 61.

On the lower end side of the supply passage 61, a suction port 62 immersed in lubricating oil accumulated in the bottom of the airtight container 2a is formed. The supply passage 61 has an upper supply passage 63 connected to the suction side of the cylinder 17 and a lower supply passage 64 branched up and down at its upper end.

The lower end portion of the rotating shaft 11 arranged to have an axis in the vertical direction is supported by the thrust bearing 65 . The suction port 62 of the supply passage 61 is provided at a position higher than the thrust bearing 65 .

In the above structure, when the air conditioner 1 is operated, the gas refrigerant flows through the refrigerant suction pipes 24 a , 24 b and is sucked into the cylinder chambers 21 , 25 . The lubricating oil accumulated at the bottom of the airtight container 2 a is sucked up after passing through the supply passage 61 , the upper supply passage 63 , and the lower supply passage 64 by the injection effect accompanying the flow of the gas refrigerant.

The sucked lubricating oil is sucked into the cylinder chambers 21 and 25 together with the gas refrigerant, and the lubricating oil sucked into the cylinder chambers 21 and 25 is used to lubricate the sliding portion of the compression mechanism unit 9 .

Here, since the suction port 62 of the supply passage 61 is provided at a position higher than the thrust bearing 65 supporting the lower end of the rotary shaft 11, the thrust bearing 65 remains immersed in the lubricating oil accumulated at the bottom of the airtight container 2a. status.

Therefore, the lubricating oil can be reliably supplied to the thrust bearing 65, and it is possible to prevent the thrust bearing 65 from being sintered due to insufficient supply of the lubricating oil. Thereby, the performance of the hermetic compressor 2 can be maintained in a good state.

(fifth embodiment)

A fifth embodiment of the present invention will be described with reference to FIG. 7 . The basic structure of the fifth embodiment is the same as that of the fourth embodiment, and the difference between the fifth embodiment and the fourth embodiment lies in the flow area of the upper supply passage 63a that is located on the upper end side of the supply passage 61 and branches upward and downward. It is different from the flow path area of the lower supply passage 64a.

Specifically, the upper supply passage 63a has a larger flow passage area, and the lower supply passage 64a has a smaller flow passage area.

In the above configuration, when the air conditioner 1 is in operation, lubricating oil accumulated at the bottom of the airtight container 2a is sucked up after passing through the supply passage 61, the upper supply passage 63a, and the lower supply passage 64a.

The sucked lubricating oil is sucked into the cylinder chambers 21 and 25 together with the gas refrigerant, and the lubricating oil sucked into the cylinder chambers 21 and 25 is used to lubricate sliding parts of the compression mechanism unit 9 .

Here, when the lubricating oil accumulated at the bottom of the airtight container 2a is sucked up by the spray effect, the amount of the lubricating oil sucked into the upper cylinder chamber 21 may decrease if some measures are not taken. It is smaller than the amount of lubricating oil sucked into the cylinder chamber 25 located below.

Therefore, as shown in this embodiment, by making the passage diameter of the upper side supply passage 63 larger than the passage diameter of the lower side supply passage 64a, the amount of lubricating oil flowing into the upper cylinder chamber 21 and the amount of lubricating oil flowing into the lower side can be realized. The amount of lubricating oil in the cylinder chamber 25 is made uniform.

Therefore, seizing on the cylinder 17 side due to insufficient supply of lubricating oil into the upper cylinder chamber 21 can be prevented, and oil compression due to oversupply of lubricating oil into the lower cylinder chamber 25 can be prevented. Thereby, the performance of the hermetic compressor 2 can be maintained in a good state.

According to each of the above-described embodiments, since the discharge port 31 communicating with the discharge chamber 19 formed in the partition plate 16 and the refrigerant discharge pipe 12 is formed on the lower side of the discharge chamber 19, the gas refrigerant is discharged together with the refrigerant gas to the discharge end. The lubricating oil in the chamber 19 is not accumulated in the discharge chamber 19 but is discharged from the discharge port 31 into the refrigerant discharge pipe 12 together with the gas refrigerant.

Therefore, the lubricating oil accumulated in the discharge chamber 19 does not hinder the opening and closing operations of the discharge valves 20 a and 20 b or hinder the flow of the gas refrigerant in the discharge chamber 19 .

Some embodiments of the present invention have been described above, but these embodiments are merely examples and do not limit the scope of the present invention. These new embodiments can be implemented in other various forms, and various omissions, substitutions, and changes can also be made without departing from the inventive concept. These embodiments and modifications thereof are included in the scope and concept of the invention, and are included in the invention described in the claims and their equivalents.

Claims (6)

1. A hermetic compressor comprising a compression mechanism part and a motor part connected by a rotating shaft having an axis in an up-and-down direction in a hermetic container, wherein the pressure of the space in said hermetic container is set to be consistent with that of said compression mechanism. The suction pressure of the compressor part is the same, and includes a discharge passage for discharging the gas refrigerant compressed by the compression mechanism part to the outside of the sealed container, and is characterized in that, The compression mechanism part includes: a partition; a pair of cylinders, which are provided on both upper and lower sides of the partition, and respectively have cylinder chambers; a discharge chamber, which is formed in the partition; a valve installed in the discharge chamber to open and close a discharge hole that discharges gas refrigerant compressed in the cylinder chamber into the discharge chamber, A discharge port communicating the discharge chamber and the discharge passage is formed on a lower side of the discharge chamber. 2. The hermetic compressor according to claim 1, wherein a portion where the discharge valve is mounted on the lower surface of the discharge chamber is formed with a lower surface than other parts of the lower surface of the discharge chamber. A recessed valve seat recess, and a concave guide groove connecting the valve seat recess and the discharge port are formed on the lower surface of the discharge chamber. 3. The hermetic compressor according to claim 1, wherein at a portion where the width dimension of the discharge chamber becomes narrow from the installation portion of the discharge valve to the discharge port, the At least one of the lower surface portion and the upper surface portion of the discharge chamber is formed with a concave portion that is more concave than the other portion. 4. The hermetic compressor according to any one of claims 1 to 3, wherein the discharge passage is connected to an oil separator for separating lubricating oil contained in the gas refrigerant, and is provided with a supply passage for supplying the lubricating oil separated by the oil separator to the sliding part of the compression mechanism part and supplying the lubricating oil in the airtight container to the suction side of the compression mechanism part, the supply The suction port of the passage is provided at a position higher than a thrust bearing supporting the lower end of the rotary shaft. 5. The hermetic compressor according to claim 4, wherein the supply passage has an upper supply passage communicating with one of the cylinder chambers located on the upper side and another supply passage communicating with the other cylinder chamber located on the lower side. In the lower supply passage that communicates with the chamber, the passage area of the upper supply passage is formed to be larger than the passage area of the lower supply passage. 6. A refrigeration cycle device comprising the hermetic compressor according to any one of claims 1 to 5, a heat source side heat exchanger, an expansion device, and a utilization side heat exchanger.

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