WO2016111048A1

WO2016111048A1 - Multi-cylinder hermetic compressor

Info

Publication number: WO2016111048A1
Application number: PCT/JP2015/076138
Authority: WO
Inventors: 篤義深谷; 幹一朗杉浦
Original assignee: 三菱電機株式会社
Priority date: 2015-01-08
Filing date: 2015-09-15
Publication date: 2016-07-14
Also published as: JP6257806B2; CN107110160B; WO2016110982A1; CN107110160A; JPWO2016111048A1

Abstract

A multi-cylinder hermetic compressor which comprises a first muffler chamber, a second muffler chamber, and a plurality of coolant channels which connect the first muffler chamber and the second muffler chamber. A check valve having a reed valve structure and comprising a fixed end at one end is provided at the first muffler chamber side in a first discharge port. The first discharge port is disposed so as to be shifted, relative to the fixed end, in one direction of rotation in the circumferential direction centred on a crank shaft. A coolant channel, from among the plurality of coolant channels, that is disposed in the position furthest from the first discharge port in the abovementioned direction of rotation has a smaller cross-sectional area than at least one of the other coolant channels.

Description

Multi-cylinder hermetic compressor

The present invention relates to a multi-cylinder hermetic compressor having a plurality of compression mechanisms.

The hermetic compressor has a hermetic container (hereinafter referred to as “shell”), an electric motor portion (hereinafter referred to as “motor”) disposed in the shell, and a compression portion driven by the motor. Yes.
In such a hermetic compressor, the refrigerant supplied through the suction pipe is compressed in the compression unit, discharged into the shell through the muffler chamber, and discharged from the discharge pipe to the outside of the shell. Since such a hermetic compressor is used in, for example, a refrigerator, a freezer, an air conditioner, a water heater, etc., high efficiency and low cost are required.

By the way, in the case of a single cylinder hermetic compressor having a single cylinder, the compression section is composed of a single compression mechanism. The compression mechanism is arranged in an annular cylinder, an annular rotary piston that is arranged on the inner periphery of the cylinder and rotates eccentrically, and a vane groove formed in the cylinder, and advances and retreats along the radial direction of the cylinder. A free vane and urging means (for example, a coil spring) for pressing the vane in a direction toward the central axis of the cylinder are provided. The compression mechanism further includes a crankshaft formed with an eccentric shaft portion for eccentrically rotating the rotary piston, and a pair of end plates that rotatably support the crankshaft and close both end faces of the cylinder. ing. A space surrounded by the inner peripheral surface of the cylinder, the outer peripheral surface of the rotary piston, and the pair of end plates is a pair of chambers whose volumes are increased or decreased by vanes that can move forward and backward toward the rotary piston that rotates eccentrically ( Hereinafter, it is divided into two (referred to as “compression chambers”). That is, the refrigerant sucked in the phase in which the volume gradually increases is compressed in the phase in which the volume gradually decreases.

On the other hand, in a multi-cylinder hermetic compressor having two cylinders, the compression unit is basically arranged in two layers (two stages) with a partition plate between the compression mechanisms similar to those of the single-cylinder hermetic compressor. It has a configuration. Through these compression mechanisms, the refrigerant passes from the muffler chamber of one compression mechanism (hereinafter referred to as “first muffler chamber”) to the muffler chamber of the other compression mechanism (hereinafter referred to as “second muffler chamber”). A refrigerant flow path is provided.

In this multi-cylinder hermetic compressor, the refrigerant gas discharged from one compression mechanism is once released into the annular first muffler chamber. Thereafter, the refrigerant gas discharged into the first muffler chamber passes through the refrigerant flow path, merges with the refrigerant gas discharged from the other compression mechanism in the annular second muffler chamber, and is discharged into the shell.

In the multi-cylinder hermetic compressor, the refrigerant gas compressed by one compression mechanism and discharged to the first muffler chamber is sent to the second muffler chamber of the other compression mechanism through the refrigerant flow path. Therefore, pressure loss occurs when the refrigerant gas passes through the refrigerant flow path. The pressure loss when this refrigerant gas passes through the refrigerant flow path is reduced by two methods: (1) increasing the diameter of the refrigerant flow path and (2) increasing the number of refrigerant flow paths. Can be made.

However, in both the method (1) and the method (2), it is necessary to install a refrigerant flow path in a limited space of the compression unit. For this reason, there is a limit in enlarging the channel area, and there is a problem that the channel cannot be effectively installed.

For example, a communication hole that is a partition plate passage portion of the refrigerant flow path that communicates the muffler chambers of the compression mechanisms is expanded, and the pressure pulsation of the refrigerant gas is reduced in the middle of the refrigerant flow path by the expanded communication hole. Have been proposed (see, for example, Patent Document 1).

In addition, there has been proposed one in which the refrigerant flow path is divided into a plurality of parts so that the space for installing the refrigerant flow path can be secured and the flow area can be increased (for example, see Patent Document 2).

JP 2013-019370 A (Claim 1, FIG. 1, FIG. 2) JP 2013-204465 A (FIGS. 2 and 3)

However, the techniques described in Patent Documents 1 and 2 have the following problems (a) and (b).
(A) Since the compression mechanism is provided with a suction port, a discharge port, a bolt hole for fastening components, and the like, a refrigerant flow path cannot be effectively provided. Further, since the suction port, the discharge port, and the bolt hole are provided, the strength of the component parts is also limited, so that the refrigerant flow path cannot be freely arranged.
(B) It is difficult to increase the number of flow paths as well as the reason (a).

The present invention has been made to solve the above-described problems, and an object of the present invention is to obtain a multi-cylinder hermetic compressor that can prevent an increase in refrigerant pressure loss and improve the compressor efficiency.

A multi-cylinder hermetic compressor according to the present invention includes a hermetic container, a compression part that is accommodated in the hermetic container and includes a first compression mechanism and a second compression mechanism, and a crankshaft that transmits driving force to the compression part. And an annular first muffler chamber that is disposed on one end side of the compression portion in the axial direction of the crankshaft and in which the refrigerant compressed by the first compression mechanism is discharged through a first discharge port; An annular second muffler chamber that is disposed on the other end side of the compression unit in the axial direction and that is compressed by the second compression mechanism is discharged through a second discharge port; and the first muffler chamber; A plurality of refrigerant flow paths that communicate with the second muffler chamber, guide the refrigerant in the second muffler chamber to the first muffler chamber, and discharge that discharges the refrigerant in the first muffler chamber to the space in the sealed container. An outlet, and the first compression Each of the structure and the second compression mechanism includes a cylinder, a rotary piston that rotates eccentrically along the inner peripheral surface of the cylinder, and a space between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotary piston. A partition vane, and a vane groove that is provided in the cylinder and accommodates the vane so as to freely move back and forth, and the plurality of refrigerant flow paths include the cylinder of the first compression mechanism and the second compression mechanism. A check valve having a reed valve structure and having a fixed end at one end is provided on the first muffler chamber side of the first discharge port. The one discharge port is arranged so as to be shifted in one rotation direction in the circumferential direction around the crankshaft with respect to the fixed end, and among the plurality of refrigerant flow paths, in the rotation direction Serial refrigerant flow path is disposed in a position farthest from the first discharge port, and has a smaller cross-sectional area than the other of the at least one coolant channel.

According to the present invention, an increase in refrigerant pressure loss in a multi-cylinder hermetic compressor can be prevented, and the compressor efficiency can be improved.

It is sectional drawing of the side view which shows the whole structure of the multicylinder hermetic compressor which concerns on Embodiment 1 of this invention. It is a fragmentary sectional view of the side view which shows the compression part of the multi-cylinder hermetic compressor of FIG. FIG. 2 is a cross-sectional view taken along line AA in FIG. 1. FIG. 3 is a cross-sectional view taken along the line BB in FIG. FIG. 5 is a sectional view taken along the line CC in FIG. 4. It is a graph which shows the annual operation efficiency at the time of applying the multi-cylinder closed type compressor which concerns on Embodiment 1 of this invention to an air conditioner. It is sectional drawing equivalent to FIG. 3 which shows the inlet / outlet shape of the refrigerant | coolant flow path of the multicylinder closed compressor which concerns on Embodiment 2 of this invention. FIG. 8 is a cross-sectional view taken along line DD in FIG. 7.

Embodiment 1 FIG.
Embodiments of the present invention will be described below.
FIG. 1 is a side sectional view showing the overall configuration of a multi-cylinder hermetic compressor according to Embodiment 1 of the present invention. FIG. 2 is a partial sectional view in a side view showing a compression portion of the multi-cylinder hermetic compressor of FIG. 3 is a cross-sectional view taken along line AA in FIG. 4 is a cross-sectional view taken along the line BB in FIG. In addition, since each said figure is drawn typically, this invention is not limited to the form shown in figure.

As shown in FIGS. 1 to 4, the multi-cylinder hermetic compressor 100 according to the first embodiment includes a shell 101 that is a hermetic container, and an electric motor unit (hereinafter referred to as a drive source) installed inside the shell 101. 102) (referred to as “motor”) and a compression unit 103 that is also installed inside the shell 101. Hereinafter, the configuration of each unit will be described in more detail.

(shell)
The shell 101 has an upper shell 101a and a central shell 101b. There may also be a lower shell that is substantially the same shape as the upper shell 101a. The upper shell 101a is provided with a glass terminal 104 for supplying power to the motor 102 from the outside, and a discharge pipe 105 for discharging the compressed refrigerant to the outside of the shell 101, that is, the multi-cylinder hermetic compressor 100. It has been.

The central shell 101b includes a motor 102, a first compression mechanism 10a and a second compression mechanism 10b constituting the compression unit 103, a first suction port 16a (see FIG. 4) and a second compression of the first compression mechanism 10a. A first suction pipe 106a and a second suction pipe 106b that guide one refrigerant are fixed to the second suction port 16b (see FIG. 3) of the mechanism 10b. The other ends of the first suction pipe 106 a and the second suction pipe 106 b are connected to the suction muffler 107. In the suction muffler 107, gas-liquid separation of the refrigerant and removal of dust in the refrigerant are performed.

(motor)
The motor 102 has a stator 102a and a rotor 102b. The rotor 102b is attached to the crankshaft 50 (which will be described in detail separately). The rotational torque generated by the motor 102 is transmitted to the first compression mechanism 10a and the second compression mechanism 10b by the crankshaft 50.

(Compression part)
The compression unit 103 includes a first end plate 20a and a second end that support the crankshaft 50 at both ends of the first compression mechanism 10a and the second compression mechanism 10b that are stacked with the partition plate 30 interposed therebetween. The board 20b is arranged. The first compression mechanism 10a, the second compression mechanism 10b, the partition plate 30, the first end plate 20a and the second end plate 20b are integrated by two types of

bolts

71a and 71b having different lengths as shown in FIG. To be concluded.

The first compression mechanism 10a is an annular first cylinder 11a and an annular first rotary piston that is disposed on the inner peripheral portion of the first cylinder 11a and rotates eccentrically along the inner peripheral surface of the first cylinder 11a. (Hereinafter referred to as “first piston”) 12a. The first compression mechanism 10a includes a first vane groove 13a formed in the first cylinder 11a, and a first vane disposed in the first vane groove 13a so as to advance and retract along the radial direction of the first cylinder 11a. 14a and a first spring 15a that presses the first vane 14a against the outer periphery of the first piston 12a. The outer peripheral surface of the first piston 12a contacts the inner peripheral surface of the first cylinder 11a at a linear contact position. With the eccentric rotation of the first piston 12a, the linear contact position moves in the circumferential direction. The open end of the first cylinder 11a is closed by the first end plate 20a.

Similarly, the second compression mechanism 10b is an annular second cylinder 11b and an annular second cylinder 11b disposed on the inner peripheral portion of the second cylinder 11b and rotating eccentrically along the inner peripheral surface of the second cylinder 11b. 2 rotary pistons (hereinafter referred to as “second pistons”) 12b. The second compression mechanism 10b includes a second vane groove 13b formed in the second cylinder 11b, and a second vane disposed in the second vane groove 13b so as to advance and retract along the radial direction of the second cylinder 11b. 14b and a second spring 15b that presses the second vane 14b against the outer periphery of the second piston 12b. The outer peripheral surface of the second piston 12b contacts the inner peripheral surface of the second cylinder 11b at a linear contact position. With the eccentric rotation of the second piston 12b, the linear contact position moves in the circumferential direction. The open end of the second cylinder 11b is closed by the second end plate 20b.
The inner diameter of the first cylinder 11a and the inner diameter of the second cylinder 11b are designed to be equal.

(Crankshaft)
The crankshaft 50 has a configuration in which a first bearing insertion portion 52a, a partition plate insertion portion 53, and a second bearing insertion portion 52b are arranged coaxially. A first eccentric shaft portion 51a that is eccentric toward one side is formed between the first bearing insertion portion 52a and the partition plate insertion portion 53. Between the 2nd bearing insertion part 52b and the partition plate insertion part 53, the 2nd eccentric shaft part 51b eccentric toward the other is formed. The first eccentric shaft portion 51a and the second eccentric shaft portion 51b are eccentric in directions in which the phases are different from each other by 180 °. Each central axis of the first eccentric shaft portion 51 a and the second eccentric shaft portion 51 b is parallel to the axis of the crankshaft 50.

Further, the first bearing insertion portion 52a is rotatably supported by the first bearing 25a provided on the inner peripheral surface of the first end plate 20a. The 2nd bearing insertion part 52b is rotatably supported by the 2nd bearing 25b provided in the internal peripheral surface of the 2nd end plate 20b. The partition plate insertion portion 53 passes through a central through hole 30 a formed at the center of the partition plate 30.

(First muffler chamber and second muffler chamber)
As shown in FIG. 4, the first end plate 20a of the first compression mechanism 10a has a first discharge port 17a communicating with the first compression chamber 40a and a first discharge port 17a at a set pressure from the downstream side of the refrigerant flow. And a first check valve 18a composed of a leaf spring that is closed at the same time. A first cover 19a is fitted to the first end plate 20a so as to cover the first discharge port 17a. The first muffler chamber 60a is formed by the first cover 19a and the first end plate 20a. The first muffler chamber 60 a is formed in an annular shape around the crankshaft 50, and is disposed on the upper end side of the compression portion 103 in the axial direction of the crankshaft 50.
Therefore, the refrigerant compressed by the first compression mechanism 10a and reaching the set pressure is discharged to the first muffler chamber 60a through the first discharge port 17a.

The first cover 19a is provided with two

discharge ports

21a and 21b. The refrigerant in the first muffler chamber 60a is discharged to the space in the shell 101 through the

discharge ports

21a and 21b. Here, in the circumferential direction around the crankshaft 50 (for example, the axis of the crankshaft 50), the position of the vane groove 13a is set to 0 °, and the counterclockwise direction in FIG. (Flow direction) is the positive direction. At this time, the discharge port 21a is provided at a position at an angle θ1 (0 ° ≦ θ1 <360 °), and the discharge port 21b is provided at a position at an angle θ2 (θ1 <θ2 <360 °). The circumferential positions of the

discharge ports

21a and 21b are specified by the center positions of the

discharge ports

21a and 21b. In this example, the

discharge ports

21a and 21b are provided at positions facing each other with the crankshaft 50 interposed therebetween. For example, the angle θ1 is about 90 ° and the angle θ2 is about 270 °.

As shown in FIG. 3, the second end plate 20 b of the second compression mechanism 10 b has a second discharge port 17 b communicating with the second compression chamber 40 b and a second discharge port 17 b at a set pressure from the downstream side of the refrigerant flow. And a second check valve 18b constituted by a leaf spring that is closed at the same time. A second cover 19b is fitted to the second end plate 20b so as to cover the second discharge port 17b. A second muffler chamber 60b is formed by the second cover 19b and the second end plate 20b. The second muffler chamber 60 b is formed in an annular shape around the crankshaft 50, and is disposed on the lower end side of the compression portion 103 in the axial direction of the crankshaft 50.

FIG. 5 is a cross-sectional view taken along the line CC of FIG. 4 and shows the configuration of the first check valve 18a. As shown in FIG. 5, the first check valve 18a has a reed valve structure that opens and closes the opening end 17a2 on the first muffler chamber 60a side of the first discharge port 17a according to the discharge pressure of the refrigerant. The first check valve 18 a includes a leaf spring-like valve body 81 and a valve presser 82 that restricts the deflection of the valve body 81. A fixed end 81 a located at one end of the valve body 81 is fixed to the first end plate 20 a by a rivet 83 together with one end of the valve presser 82. When the pressure difference between the refrigerant pressure in the first compression chamber 40a and the refrigerant pressure in the first muffler chamber 60a is small, the other end side of the valve body 81 is in contact with the opening end 17a2 of the first discharge port 17a. As a result, the first check valve 18a is closed. On the other hand, when the pressure difference between the refrigerant pressure in the first compression chamber 40a and the refrigerant pressure in the first muffler chamber 60a increases, the valve body 81 is bent due to the deflection of the valve body 81 as shown by a two-dot chain line in FIG. The other end side (the free end side) is separated from the opening end 17a2 of the first discharge port 17a. As a result, the first check valve 18a is opened, and the refrigerant in the first compression chamber 40a is discharged into the first muffler chamber 60a through the first discharge port 17a. The valve body 81 at this time is inclined with respect to the first discharge port 17a so as to be away from the opening end 17a2 as it is away from the fixed end 81a. Therefore, the refrigerant flowing into the first muffler chamber 60a from the first discharge port 17a is guided in a direction away from the fixed end 81a by the valve body 81 as shown by a thick arrow in FIG.

As shown in FIG. 4, the fixed end 81 a of the first check valve 18 a and the first discharge port 17 a are arranged at positions shifted in the circumferential direction in the annular first muffler chamber 60 a centering on the crankshaft 50. Has been. As a result, the refrigerant in the first muffler chamber 60a generates a circumferential flow in one rotational direction as a whole. In FIG. 4, the first discharge port 17a is provided at a position shifted in the counterclockwise direction with respect to the fixed end 81a. For this reason, in FIG. 4, the overall flow direction of the refrigerant in the first muffler chamber 60a is the counterclockwise direction.

Like the first check valve 18a, the second check valve 18b has a valve body 81, a valve presser 82, and a rivet 83, and is arranged vertically symmetrically with the first check valve 18a. Therefore, for the same reason as described above, the refrigerant in the second muffler chamber 60b generates a circumferential flow in one rotational direction as a whole. In FIG. 3, the second discharge port 17b is provided at a position shifted in the clockwise direction with respect to the fixed end 81a of the second check valve 18b. For this reason, in FIG. 3, the overall flow direction of the refrigerant in the second muffler chamber 60b is the clockwise direction.

(Refrigerant flow path)
The first muffler chamber 60a and the second muffler chamber 60b communicate with each other via at least one (three in this example)

refrigerant flow paths

33a, 33b, and 33c. In FIG. 1, only one refrigerant channel is shown as the refrigerant channel 33. The

refrigerant flow paths

33a, 33b, and 33c have, for example, a circular cross-sectional shape. The refrigerant discharged to the second muffler chamber 60b is guided to the first muffler chamber 60a via the

refrigerant flow paths

33a, 33b, and 33c. The

refrigerant flow paths

33a, 33b, and 33c are disposed adjacent to the first compression chamber 40a and the second compression chamber 40b. The

refrigerant flow paths

33a, 33b, and 33c extend in a direction parallel to the crankshaft 50. The

refrigerant flow paths

33a, 33b, and 33c penetrate the first end plate 20a, the first cylinder 11a of the first compression mechanism 10a, the partition plate 30, the second cylinder 11b of the second compression mechanism 10b, and the second end plate 20b. Is formed.

The

refrigerant flow paths

33a, 33b, 33c surround the first compression chamber 40a and the second compression chamber 40b, and are arranged in the circumferential direction around the crankshaft 50. When the positions of the

vane grooves

13a and 13b are set to 0 ° in the circumferential direction around the crankshaft 50, the

refrigerant flow paths

33a, 33b, and 33c are clockwise when viewed from the axial direction (lower surface side) of the compression unit 103. It is formed only in the range of 90 ° to 270 ° (or counterclockwise). Further, the

refrigerant flow paths

33a, 33b, and 33c have the

vane grooves

13a and 13b positioned at 0 ° in the circumferential direction centered on the crankshaft 50, and the counterclockwise direction in FIG. When the (direction) is the positive direction, it is formed only in the angle range of θ1 to θ2. Note that the circumferential positions of the

refrigerant flow paths

33a, 33b, and 33c are specified by the respective center positions of the

refrigerant flow paths

33a, 33b, and 33c.

As described above, the overall flow direction of the refrigerant based on the structure of the

check valves

18a and 18b is the clockwise direction in the second muffler chamber 60b shown in FIG. 3, and the first muffler chamber 60a shown in FIG. In the counterclockwise direction. Of the

refrigerant flow paths

33a, 33b, 33c, the refrigerant flow path 33c is disposed at a position farthest from the

discharge ports

17a, 17b in the overall flow direction of the refrigerant based on the structure of the

check valves

18a, 18b. In other words, among the

refrigerant flow paths

33a, 33b, and 33c, the refrigerant flow path 33c is disposed at a position closest to the

discharge ports

17a and 17b in the direction opposite to the flow direction. The refrigerant flow path 33c has a smaller cross-sectional area than the other

refrigerant flow paths

33a and 33b. In this example, since the

refrigerant channels

33a, 33b, and 33c all have a circular cross-sectional shape, the refrigerant channel 33c is formed with a smaller diameter than the

refrigerant channels

33a and 33b. In this example, the

refrigerant flow paths

33a and 33b have the same cross-sectional area, but the refrigerant flow path 33a closest to the

discharge ports

17a and 17b in the overall flow direction of the refrigerant is more than the refrigerant flow path 33b. It may have a large cross-sectional area. In other words, the refrigerant flow path closer to the

discharge ports

17a and 17b may have a larger cross-sectional area in the overall refrigerant flow direction. The cross-sectional area of the refrigerant flow path is an area of the refrigerant flow path in a plane perpendicular to the axial direction assuming that the refrigerant flow path penetrates in the axial direction of the crankshaft 50.

In FIG. 4, since the overall flow direction of the refrigerant based on the structure of the

check valves

18a and 18b is counterclockwise, the refrigerant discharged from the refrigerant flow path 33a and the discharge port 17a into the first muffler chamber 60a. Is mainly discharged from the discharge port 21a into the space in the shell 101. The refrigerant discharged from the

refrigerant flow paths

33b and 33c into the first muffler chamber 60a is mainly discharged from the discharge port 21b into the space in the shell 101. However, a part of the refrigerant discharged from the refrigerant flow path 33b into the first muffler chamber 60a flows in the direction opposite to the overall flow direction and is discharged from the discharge port 21a.

(Push amount)
When the sum of the cross-sectional areas of the

refrigerant flow paths

33a, 33b, and 33c is S [mm ² ] and the displacement per rotation of the second compression mechanism 10b is Vst [cc], the total cross-sectional area S and the displacement Vst Is set to satisfy the relationship of 11 [mm ² / cc] ≦ S / Vst ≦ 20 [mm ² / cc], for example. The reason for this will be described later.

(Compression of refrigerant)
As shown in FIGS. 1 and 2, the first eccentric shaft portion 51a penetrates the inner peripheral portion of the first piston 12a, and the second eccentric shaft portion 51b penetrates the inner peripheral portion of the second piston 12b. Therefore, the rotation of the crankshaft 50 causes the first piston 12a and the second piston 12b to rotate eccentrically in a state where one is 180 ° out of phase with the other.

The volume of one chamber of the first compression chamber 40a divided into two is gradually increased by the first piston 12a that rotates eccentrically with the rotation of the crankshaft 50 and the first vane 14a that can advance and retreat. Accordingly, the volume of the other chamber of the first compression chamber 40a that is divided into two is gradually reduced. The first suction port 16a is formed at a position corresponding to one chamber of the first compression chamber 40a, and the first discharge port 17a is formed at a position corresponding to the other chamber of the first compression chamber 40a ( (See FIG. 4). That is, the first suction port 16a and the first discharge port 17a are arranged so as to sandwich the first vane 14a in the rotation direction of the crankshaft 50 when viewed from the axial direction of the crankshaft 50. That is, the refrigerant is sucked from the first suction port 16a, then compressed, and discharged from the first discharge port 17a into the first muffler chamber 60a.

Further, the volume of one chamber of the second compression chamber 40b that is divided into two is gradually increased by the second piston 12b that rotates eccentrically with the rotation of the crankshaft 50 and the second vane 14b that can advance and retreat. . Accordingly, the volume of the other chamber of the second compression chamber 40b that is divided into two is gradually reduced. The second suction port 16b is formed at a position corresponding to one chamber of the second compression chamber 40b, and the second discharge port 17b is formed at a position corresponding to the other chamber of the second compression chamber 40b ( (See FIG. 3). That is, the second suction port 16b and the second discharge port 17b are arranged so as to sandwich the second vane 14b in the rotational direction of the crankshaft 50 when viewed from the axial direction of the crankshaft 50. That is, the refrigerant is sucked from the second suction port 16b, then compressed and discharged from the second discharge port 17b into the second muffler chamber 60b. And the refrigerant | coolant discharged | emitted in the 2nd muffler chamber 60b is discharged in the 1st muffler chamber 60a via several refrigerant |

coolant flow path

33a, 33b, 33c.

The refrigerant discharged into the first muffler chamber 60a via the

refrigerant flow paths

33a, 33b, 33c and the refrigerant discharged into the first muffler chamber 60a from the discharge port 17a are discharged into the

discharge ports

21a, 21b is discharged into the shell 101. Specifically, the refrigerant discharged from the refrigerant flow path 33a into the first muffler chamber 60a and a part of the refrigerant discharged from the refrigerant flow path 33b into the first muffler chamber 60a reach the discharge port 17a. Without being discharged from the discharge port 21a. The remainder of the refrigerant discharged from the refrigerant flow path 33b into the first muffler chamber 60a and the refrigerant discharged from the refrigerant flow path 33c into the first muffler chamber 60a do not reach the discharge port 17a and are discharged from the discharge port. Released from 21b. The refrigerant discharged from the discharge port 17a is discharged from the discharge port 21a without passing through the

refrigerant flow paths

33a, 33b, 33c.

That is, the

refrigerant flow paths

33a, 33b, 33c, the discharge port 17a, and the

discharge ports

21a, 21b reach the discharge port 17a or are discharged from the discharge port 17a. The refrigerant is arranged so as not to reach the

refrigerant flow paths

33a, 33b, 33c. As a result, the refrigerant discharged into the first muffler chamber 60a is sucked into the

refrigerant flow paths

33a, 33b, 33c or the discharge port 17a and does not flow backward.

FIG. 6 is a graph showing the annual operating efficiency (APF) when the multi-cylinder hermetic compressor 100 of the first embodiment is applied to an air conditioner. FIG. 6 shows the relationship between the ratio S / Vst between the total cross-sectional area S of the

refrigerant flow paths

33a, 33b, and 33c and the displacement Vst of the second compression mechanism 10b, and the annual operating efficiency. The horizontal axis represents S / Vst [mm ² / cc], and the vertical axis represents annual operation efficiency.

A multi-cylinder hermetic compressor 100 shown in FIG. 1 is an internal high-pressure multi-cylinder hermetic compressor. Further, in FIG. 6, the multi-cylinder closed compression according to the first embodiment is based on the annual operation efficiency of the conventional multi-cylinder closed compressor having S / Vst of 8.9 mm ² / cc as a reference (100%). The annual operating efficiency of the machine 100 is shown.

As shown in FIG. 6, the annual operating efficiency of the multi-cylinder hermetic compressor 100 is over 100.5% at the maximum when S / Vst is 11.2 mm ² / cc, and S / Vst is 8.9 mm ^2. When it is larger than / cc and smaller than 24 mm ² / cc, it exceeds 100%. That is, the total cross-sectional area S of the

refrigerant flow paths

33a, 33b, and 33c and the displacement Vst of the second compression mechanism 10b are 8.9 [mm ² / cc] <S / Vst <24 [mm ² / cc]. By setting so as to satisfy the relationship, the annual operating efficiency can be improved as compared with the conventional multi-cylinder hermetic compressor. In the product, the total cross-sectional area S and the displacement amount Vst were set so as to satisfy the relationship of 11 [mm ² / cc] ≦ S / Vst ≦ 20 [mm ² / cc] in consideration of manufacturing variations and the like.

From the above results, the muffler chamber into which the refrigerant is merged is optimized by optimizing the ratio (S / Vst) of the total cross-sectional area S of the

refrigerant flow paths

33a, 33b, and 33c and the displacement Vst of the second compression mechanism 10b. It turns out that the pressure loss at the time of being introduce | transduced into (here the 1st muffler chamber 60a) can be suppressed, and an annual operating efficiency can be improved.

Therefore, in the multi-cylinder hermetic compressor 100 of the first embodiment, the first muffler chamber 60a is compressed by the second compression mechanism 10b and passes through the

refrigerant flow paths

33a, 33b, and 33c from the second muffler chamber 60b. The pulsation accompanying the pressure fluctuation of the refrigerant discharged into the second muffler chamber 60b and the

refrigerant flow paths

33a, 33b, and 33c can be effectively reduced. And the flow of a refrigerant can be led to the 1st muffler room 60a of the 1st compression mechanism 10a in the state where the increase in pressure loss was controlled. Therefore, the compressor efficiency (COP) can be improved.

Further, as described above, the pressure loss can be reduced by optimizing the total sectional area S of the

refrigerant flow paths

33a, 33b, and 33c with respect to the displacement amount Vst of the second compression mechanism 10b. Further, as shown in FIG. 4, in the circumferential direction around the crankshaft 50, when the position of the vane groove 13a is 0 ° and the counterclockwise direction is the positive direction, the discharge port 21a of the first cover 19a is The discharge port 21b is disposed at a position near 270 °. With this arrangement, the refrigerant discharged from the first discharge port 17a into the first muffler chamber 60a and the second muffler chamber 60b to the first muffler chamber 60a via the

refrigerant flow paths

33a, 33b, and 33c. It is possible to efficiently separate the refrigerant that has flowed into the tank. Therefore, the backflow from the first muffler chamber 60a to the second muffler chamber 60b and the backflow from the first muffler chamber 60a to the first compression chamber 40a of the first compression mechanism 10a can be minimized. Thereby, the effect of optimizing the ratio (S / Vst) between the total cross-sectional area S of the

refrigerant flow paths

33a, 33b, and 33c and the displacement amount Vst of the second compression mechanism 10b can be sufficiently exhibited.

Further, as described above, the

refrigerant flow paths

33a, 33b, 33c are formed only in the range of 90 ° to 270 ° clockwise (or counterclockwise) with respect to the

vane grooves

13a, 13b. In addition, in the overall refrigerant flow direction based on the structure of the

check valves

18a and 18b, the refrigerant flow path 33c arranged at the farthest position when viewed from the

discharge ports

17a and 17b is the other

refrigerant flow paths

33a and 33b. Has a smaller cross-sectional area. When viewed from the refrigerant flow path 33c, the distance from the discharge port 17a in the overall flow direction of the refrigerant is shorter than the

refrigerant flow paths

33a and 33b, and thus the refrigerant is discharged from the refrigerant flow path 33c into the first muffler chamber 60a. If the refrigerant is not discharged from the discharge port 21b, the refrigerant may be sucked into the discharge port 17a. When the refrigerant discharged from the refrigerant flow path 33c into the first muffler chamber 60a is sucked into the discharge port 17a, the pressure loss increases. However, in the first embodiment, since the refrigerant flow path 33c has a smaller cross-sectional area than the other

refrigerant flow paths

33a and 33b, the refrigerant discharged from the refrigerant flow path 33c into the first muffler chamber 60a. Can be reduced. Therefore, it is possible to suppress the refrigerant released from the refrigerant flow path 33c into the first muffler chamber 60a from being sucked into the discharge port 17a. On the other hand, since the

refrigerant flow paths

33a and 33b have a larger cross-sectional area than the refrigerant flow path 33c, the pressure loss from the second muffler chamber 60b to the first muffler chamber 60a can be reduced. For this reason, the flow of the refrigerant can be guided to the first muffler chamber 60a of the first compression mechanism 10a while suppressing an increase in pressure loss, and the compressor efficiency can be improved.

When it is assumed that the

refrigerant flow paths

33a, 33b, and 33c are formed in the range of 0 ° to 90 °, 270 ° to 360 ° clockwise (or counterclockwise) with respect to the

vane grooves

13a and 13b, Since the

discharge ports

17a and 17b, the

suction ports

16a and 16b, the

vane grooves

13a and 13b, and the like are arranged, the

refrigerant flow paths

33a, 33b, and 33c cannot be freely arranged. Furthermore, in addition to the hollow structures such as the

discharge ports

17a and 17b, the

suction ports

16a and 16b, and the

vane grooves

13a and 13b, if the hollow

refrigerant channels

33a, 33b, and 33c are intensively provided, the

cylinders

11a and 11b This reduces the strength of the film and tends to cause distortion of the shape.

On the other hand, in the first embodiment, the

refrigerant flow paths

33a, 33b, 33c are formed in the range of 90 ° to 270 ° clockwise (or counterclockwise) with respect to the

vane grooves

13a, 13b. Moreover, the fall of the intensity | strength of

cylinder

11a, 11b can be suppressed. Even if the

refrigerant flow paths

33a, 33b, and 33c are arranged in the range of 90 ° to 270 ° with respect to the

vane grooves

13a and 13b, the

discharge ports

21a and 21b are located in the vicinity of 90 ° and 270 ° with respect to the

vane grooves

13a and 13b. By providing 21b, the refrigerant discharged from the

refrigerant flow paths

33a, 33b, and 33c can be discharged into the shell 101 from the

discharge ports

21a and 21b. Thereby, it can suppress that the refrigerant | coolant discharged | emitted by the 1st muffler chamber 60a is sucked into

refrigerant flow path

33a, 33b, 33c again, or is sucked into discharge port 17a.

Embodiment 2. FIG.
FIG. 7 is a cross-sectional view corresponding to FIG. 3 showing the shape of the inlet and outlet of the refrigerant flow path of the multi-cylinder hermetic compressor according to Embodiment 2 of the present invention. FIG. 8 is a cross-sectional view taken along the line DD in FIG. 7 and shows the configuration of the second end plate 20b. In the figure, the same reference numerals are given to the same functional parts as those of the first embodiment. In the description, reference is made to FIG. 1 and FIG.

In the multi-cylinder hermetic compressor 100 of the second embodiment, as shown in FIGS. 7 and 8, the

refrigerant flow paths

33a, 33b, Openings (which may be tapered or chamfered) 33d, 33e, and 33f having a cross-sectional area larger than that of 33c are provided.

In the multi-cylinder hermetic compressor 100 of the second embodiment, the cross-sectional areas larger than the cross-sectional areas of the

refrigerant flow paths

33a, 33b, and 33c are provided at the inlet and the outlet of the

refrigerant flow paths

33a, 33b, and 33c. Since the

openings

33d, 33e, and 33f having the above are provided, the flow of the refrigerant in the

refrigerant flow paths

33a, 33b, and 33c becomes smooth, and the effect of further reducing the pressure loss can be obtained.

As described above, the multi-cylinder hermetic compressor 100 according to the first and second embodiments is provided with the shell 101 and the compression unit that is housed in the shell 101 and includes the first compression mechanism 10a and the second compression mechanism 10b. 103, the crankshaft 50 that transmits the driving force to the compression portion 103, and the refrigerant that is disposed on one end side of the compression portion 103 in the axial direction of the crankshaft 50 and compressed by the first compression mechanism 10a is the first discharge port. An annular first muffler chamber 60a that is discharged through 17a, and the refrigerant that is disposed on the other end side of the compression unit 103 in the axial direction and compressed by the second compression mechanism 10b passes through the second discharge port 17b. The annular second muffler chamber 60b to be discharged, the first muffler chamber 60a, and the second muffler chamber 60b communicate with each other, and the refrigerant in the second muffler chamber 60b is transferred to the first muffler chamber 60a. And a plurality of

refrigerant flow paths

33a, 33b, 33c, and

discharge ports

21a, 21b for discharging the refrigerant in the first muffler chamber 60a to the space in the shell 101. The first compression mechanism 10a includes a first cylinder 11a, a first rotary piston 12a that rotates eccentrically along the inner peripheral surface of the first cylinder 11a, and a first space that partitions the space between the inner peripheral surface of the first cylinder 11a and the outer peripheral surface of the first rotary piston 12a. A first vane 14a, and a first vane groove 13a that is provided in the first cylinder 11a and accommodates the first vane 14a so as to be capable of moving forward and backward. The second compression mechanism 10b includes a second cylinder 11b, A second rotary piston 12b that rotates eccentrically along the inner peripheral surface of the two cylinders 11b, an inner peripheral surface of the second cylinder 11b, and an outer peripheral surface of the second rotary piston 12b; A second vane 14b that partitions the space between the second vane 14b and a second vane groove 13b that is provided in the second cylinder 11b and accommodates the second vane 14b so that the second vane 14b can be moved forward and backward. , 33c are provided through the first cylinder 11a and the second cylinder 11b, and have a reed valve structure on the first muffler chamber 60a side in the first discharge port 17a, and a fixed end 81a at one end. The first check port 18a is provided in one rotational direction (counterclockwise in FIG. 4) in the circumferential direction around the crankshaft 50 with respect to the fixed end 81a. Among the plurality of

refrigerant flow paths

33a, 33b, and 33c, the refrigerant flow path 33c that is disposed farthest from the first discharge port 17a in the rotational direction is the other small number of

refrigerant flow paths

33a, 33b, and 33c. The cross-sectional area is smaller than that of at least one

refrigerant flow path

33a, 33b.

According to this configuration, since it is possible to suppress the refrigerant discharged from the refrigerant flow path 33c into the first muffler chamber 60a from being sucked into the discharge port 17a, an increase in refrigerant pressure loss in the multi-cylinder hermetic compressor 100 is prevented, Compressor efficiency can be improved.

In the multi-cylinder hermetic compressor 100 according to the first and second embodiments, when the position of the first vane groove 13a is 0 ° and the rotational direction is the positive direction in the circumferential direction around the crankshaft 50 The plurality of

refrigerant flow paths

33a, 33b, and 33c may be provided in an angular range (for example, only the angular range) that is 90 ° or more and 270 ° or less in the circumferential direction around the crankshaft 50.

According to this configuration, the

refrigerant flow paths

33a, 33b, and 33c can be provided while suppressing a decrease in strength of the first cylinder 11a and the second cylinder 11b.

In the multi-cylinder hermetic compressor 100 according to the first and second embodiments, the discharge port includes the first discharge port 21a and the second discharge port 21b, and in the circumferential direction around the crankshaft 50, When the position of the first vane groove 13a is 0 °, the rotational direction is the positive direction, and the angles θ1 and θ2 are 0 ° ≦ θ1 <θ2 <360 °, the first discharge port 21a The second discharge port 21b is provided at a position at an angle θ2 in the circumferential direction around the crankshaft 50, and is provided with a plurality of refrigerant flow paths. 33a, 33b, and 33c may be provided in an angle range (for example, only the angle range) that is θ1 or more and θ2 or less in the circumferential direction around the crankshaft 50.

According to this configuration, the refrigerant released from the

refrigerant flow paths

33a, 33b, 33c into the first muffler chamber 60a can be discharged from the

discharge ports

21a, 21b without passing through the first discharge port 17a. For this reason, it can suppress that the refrigerant | coolant discharged | emitted in the 1st muffler chamber 60a from the refrigerant |

coolant flow paths

33a, 33b, and 33c is inhaled by the 1st discharge port 17a.

In the multi-cylinder hermetic compressor 100 according to the first and second embodiments, the plurality of

refrigerant channels

33a, 33b, and 33c are provided at the inlet and the outlet of the plurality of

refrigerant channels

33a, 33b, and 33c, respectively.

Openings

33d, 33e, 33f having a cross-sectional area larger than the respective cross-sectional areas may be provided.

According to this configuration, the refrigerant flow in the

refrigerant flow paths

33a, 33b, and 33c becomes smooth, and an effect of further reducing pressure loss can be obtained.

Further, the multi-cylinder hermetic compressor 100 according to the first and second embodiments includes a shell 101, a compression unit 103 that is accommodated in the shell 101, and includes a first compression mechanism 10a and a second compression mechanism 10b, and a compression The crankshaft 50 that transmits the driving force to the portion 103, and the refrigerant that is disposed on one end side of the compression portion 103 in the axial direction of the crankshaft 50 and is compressed by the first compression mechanism 10a passes through the first discharge port 17a. The annular first muffler chamber 60a to be discharged and the refrigerant which is disposed on the other end side of the compression unit 103 in the axial direction and is compressed by the second compression mechanism 10b is discharged through the second discharge port 17b. The annular second muffler chamber 60b, the first muffler chamber 60a, and the second muffler chamber 60b communicate with each other, and the refrigerant in the second muffler chamber 60b is guided to the first muffler chamber 60a.

Refrigerant passages

33a, 33b, and 33c, and

discharge ports

21a and 21b that discharge the refrigerant in the first muffler chamber 60a to the space in the shell 101. The first compression mechanism 10a includes the first cylinder 11a and The first vane partitioning the space between the first rotary piston 12a rotating eccentrically along the inner peripheral surface of the first cylinder 11a and the outer peripheral surface of the first rotary piston 12a and the inner peripheral surface of the first cylinder 11a 14a and a first vane groove 13a that is provided in the first cylinder 11a and accommodates the first vane 14a so as to be able to advance and retreat. The second compression mechanism 10b includes a second cylinder 11b and a second cylinder. Between the second rotary piston 12b rotating eccentrically along the inner peripheral surface of 11b and the inner peripheral surface of the second cylinder 11b and the outer peripheral surface of the second rotary piston 12b. A second vane 14b for partitioning, and a second vane groove 13b that is provided in the second cylinder 11b and accommodates the second vane 14b so as to be able to advance and retreat, and has at least one

refrigerant flow path

33a, 33b, 33c is provided through the first cylinder 11a and the second cylinder 11b, and the total cross-sectional area S [mm ² ] of at least one

refrigerant flow path

33a, 33b, 33c and the second compression mechanism 10b. The displacement amount Vst [cc] per rotation satisfies the relationship of 8.9 [mm ² / cc] <S / Vst <24 [mm ² / cc].

According to this configuration, the total cross-sectional area S of the

refrigerant flow paths

33a, 33b, and 33c is optimized according to the displacement amount Vst of the second compression mechanism 10b, so that the refrigerant pressure loss in the multi-cylinder hermetic compressor 100 increases. And the compressor efficiency can be improved.

In the multi-cylinder hermetic compressor 100 according to the first and second embodiments, the first reverse port having a reed valve structure on the first muffler chamber 60a side in the first discharge port 17a and having a fixed end 81a at one end. A stop valve 18a is provided, and the first discharge port 17a is shifted from the fixed end 81a in one circumferential direction around the crankshaft 50 (counterclockwise in FIG. 4). In the circumferential direction around the crankshaft 50, when the position of the first vane groove 13a is 0 ° and the rotational direction is the positive direction, at least one

refrigerant flow path

33a, 33b, 33c You may provide in the angle range (for example, only the said angle range) used as 90 degrees or more and 270 degrees or less in the circumferential direction centering on the crankshaft 50. FIG.

According to this configuration, the

refrigerant flow paths

In the multi-cylinder hermetic compressor 100 according to the first and second embodiments, the first reverse port having a reed valve structure on the first muffler chamber 60a side in the first discharge port 17a and having a fixed end 81a at one end. A stop valve 18a is provided, and the first discharge port 17a is shifted from the fixed end 81a in one circumferential direction around the crankshaft 50 (counterclockwise in FIG. 4). The discharge port includes a first discharge port 21a and a second discharge port 21b. In the circumferential direction around the crankshaft 50, the position of the first vane groove 13a is 0 °, and the rotation When the direction is the positive direction and the angle θ1 and the angle θ2 are 0 ° ≦ θ1 <θ2 <360 °, the first discharge port 21a is provided at a position where the angle θ1 is in the circumferential direction around the crankshaft 50. And second The two discharge ports 21b are provided at a position having an angle θ2 in the circumferential direction centered on the crankshaft, and at least one

refrigerant flow path

33a, 33b, 33c is θ1 in the circumferential direction centered on the crankshaft 50. It may be provided in an angle range that is θ2 or less (for example, only the angle range).

According to this configuration, the refrigerant released from the

refrigerant flow paths

33a, 33b, 33c into the first muffler chamber 60a can be discharged from the

discharge ports

coolant flow paths

33a, 33b, and 33c is inhaled by the 1st discharge port 17a.

In the multi-cylinder hermetic compressor 100 according to the first and second embodiments, at least one

refrigerant flow path

33a, 33b, 33c is provided at the inlet and the outlet of at least one

refrigerant flow path

33a, 33b, 33c.

Openings

33d, 33e, and 33f having a cross-sectional area larger than the cross-sectional area may be provided.

According to this configuration, the refrigerant flow in the

refrigerant flow paths

Other embodiments.
The present invention is not limited to the above embodiment, and various modifications can be made.
For example, in the above embodiment, the configuration in which the three

refrigerant flow paths

33a, 33b, and 33c are provided is illustrated, but the number of refrigerant flow paths may be one, two, or four or more.

In the above embodiment, the

refrigerant flow paths

33a, 33b, and 33c having a circular cross-sectional shape are illustrated, but the refrigerant flow path may have other cross-sectional shapes such as a rectangular shape. Further, the refrigerant channel may be a long hole extending in an arc shape along the circumferential direction of the cylinder.

10a first compression mechanism, 10b second compression mechanism, 11a first cylinder, 11b second cylinder, 12a first piston (first rotary piston), 12b second piston (second rotary piston), 13a first vane groove, 13b 2nd vane groove, 14a 1st vane, 14b 2nd vane, 15a 1st spring, 15b 2nd spring, 16a 1st inlet, 16b 2nd inlet, 17a 1st discharge port, 17a2 open end, 17b 2nd 2 discharge port, 18a first check valve, 18b second check valve, 19a first cover, 19b second cover, 20a first end plate, 20b second end plate, 21a, 21b discharge port, 25a first bearing 25b second bearing, 30 partition plate, 30a central through hole, 33, 33a, 33b, 33c refrigerant flow path, 3d, 33e, 33f opening, 40a first compression chamber, 40b second compression chamber, 50 crankshaft, 51a first eccentric shaft portion, 51b second eccentric shaft portion, 52a first bearing insertion portion, 52b second Bearing insertion portion, 53 partition plate insertion portion, 60a first muffler chamber, 60b second muffler chamber, 71a, 71b bolt, 81 valve body, 81a fixed end, 82 valve presser, 83 rivet, 100 multi-cylinder hermetic compressor, 101 shell (sealed container), 101a upper shell, 101b center shell, 102 motor (motor part), 102a stator, 102b rotor, 103 compression part, 104 glass terminal, 105 discharge pipe, 106a first suction pipe, 106b Second suction pipe, 107 Suction muffler.

Claims

A sealed container;
A compression unit housed in the sealed container and having a first compression mechanism and a second compression mechanism;
A crankshaft for transmitting a driving force to the compression section;
An annular first muffler chamber that is disposed on one end side of the compression portion in the axial direction of the crankshaft and in which the refrigerant compressed by the first compression mechanism is discharged through a first discharge port;
An annular second muffler chamber that is disposed on the other end side of the compression portion in the axial direction and in which the refrigerant compressed by the second compression mechanism is discharged through a second discharge port;
A plurality of refrigerant flow paths that connect the first muffler chamber and the second muffler chamber and guide the refrigerant in the second muffler chamber to the first muffler chamber;
A discharge port for discharging the refrigerant in the first muffler chamber into the space in the sealed container;
With
Each of the first compression mechanism and the second compression mechanism is:
A cylinder,
A rotary piston that rotates eccentrically along the inner circumferential surface of the cylinder;
A vane that partitions a space between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotary piston;
A vane groove that is provided in the cylinder and accommodates the vane so as to freely advance and retract,
The plurality of refrigerant flow paths are provided through the cylinder of the first compression mechanism and the cylinder of the second compression mechanism,
On the first muffler chamber side of the first discharge port, a check valve having a reed valve structure and having a fixed end at one end is provided.
The first discharge port is arranged so as to be shifted in one rotation direction in the circumferential direction around the crankshaft with respect to the fixed end,
Of the plurality of refrigerant channels, the refrigerant channel disposed at a position farthest from the first discharge port in the rotation direction has a smaller cross-sectional area than at least one other refrigerant channel. Compressor.
In the circumferential direction around the crankshaft, when the position of the vane groove of the first compression mechanism is 0 ° and the rotational direction is the positive direction,
2. The multi-cylinder hermetic compressor according to claim 1, wherein the plurality of refrigerant flow paths are provided in an angle range of 90 ° or more and 270 ° or less in a circumferential direction centering on the crankshaft.
The discharge port includes a first discharge port and a second discharge port,
In the circumferential direction around the crankshaft, when the position of the vane groove of the first compression mechanism is 0 ° and the rotational direction is the positive direction,
The first discharge port is provided at a position at an angle θ1 in the circumferential direction around the crankshaft,
The second discharge port is provided at a position at an angle θ2 in the circumferential direction around the crankshaft,
3. The multi-cylinder hermetic compressor according to claim 1, wherein the plurality of refrigerant flow paths are provided in an angle range of θ1 or more and θ2 or less in a circumferential direction around the crankshaft.
The inlet and the outlet of each of the plurality of refrigerant flow paths are provided with openings having a cross-sectional area larger than the cross-sectional area of each of the plurality of refrigerant flow paths. The multi-cylinder hermetic compressor according to any one of the above.
A sealed container;
A compression unit housed in the sealed container and having a first compression mechanism and a second compression mechanism;
A crankshaft for transmitting a driving force to the compression section;
An annular first muffler chamber that is disposed on one end side of the compression portion in the axial direction of the crankshaft and in which the refrigerant compressed by the first compression mechanism is discharged through a first discharge port;
An annular second muffler chamber that is disposed on the other end side of the compression portion in the axial direction and in which the refrigerant compressed by the second compression mechanism is discharged through a second discharge port;
At least one refrigerant flow path communicating the first muffler chamber and the second muffler chamber and guiding the refrigerant in the second muffler chamber to the first muffler chamber;
A discharge port for discharging the refrigerant in the first muffler chamber into the space in the sealed container;
With
Each of the first compression mechanism and the second compression mechanism is:
A cylinder,
A rotary piston that rotates eccentrically along the inner circumferential surface of the cylinder;
A vane that partitions a space between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotary piston;
A vane groove that is provided in the cylinder and accommodates the vane so as to freely advance and retract,
The at least one refrigerant flow path is provided through the cylinder of the first compression mechanism and the cylinder of the second compression mechanism;
The total sectional area S [mm 2 ] of the at least one refrigerant flow path and the displacement amount Vst [cc] per rotation of the second compression mechanism are 8.9 [mm 2 / cc] <S / Vst. A multi-cylinder hermetic compressor satisfying a relationship of <24 [mm 2 / cc].
On the first muffler chamber side of the first discharge port, a check valve having a reed valve structure and having a fixed end at one end is provided.
The first discharge port is arranged so as to be shifted in one rotation direction in the circumferential direction around the crankshaft with respect to the fixed end,
In the circumferential direction around the crankshaft, when the position of the vane groove of the first compression mechanism is 0 ° and the rotational direction is the positive direction,
6. The multi-cylinder hermetic compressor according to claim 5, wherein the at least one refrigerant flow path is provided in an angular range of 90 ° or more and 270 ° or less in a circumferential direction around the crankshaft.
On the first muffler chamber side of the first discharge port, a check valve having a reed valve structure and having a fixed end at one end is provided.
The first discharge port is arranged so as to be shifted in one rotation direction in the circumferential direction around the crankshaft with respect to the fixed end,
The discharge port includes a first discharge port and a second discharge port,
In the circumferential direction around the crankshaft, when the position of the vane groove of the first compression mechanism is 0 ° and the rotational direction is the positive direction,
The first discharge port is provided at a position at an angle θ1 in the circumferential direction around the crankshaft,
The second discharge port is provided at a position at an angle θ2 in the circumferential direction around the crankshaft,
7. The multi-cylinder hermetic compressor according to claim 5, wherein the at least one refrigerant flow path is provided in an angle range of θ1 or more and θ2 or less in a circumferential direction around the crankshaft.
The inlet or outlet of the at least one refrigerant channel is provided with an opening having a cross-sectional area larger than that of the at least one refrigerant channel. The multi-cylinder hermetic compressor according to one item.