Compressor and air conditioner

Abstract

The present application relates to a compressor and an air conditioner capable of reducing noise generated by a rotating shaft bending vibration. The compressor of the embodiment includes a cylinder, a rotating shaft, a bearing, and a discharge valve mechanism. The cylinder compresses refrigerant. The rotating shaft has an eccentric portion disposed in the cylinder. The bearing has a flange portion defining one face of the rotating shaft in the axial direction in the cylinder, and a boss portion continuous with the flange portion and extending in a tubular shape concentric with the rotating shaft to support the rotating shaft so as to be rotatable. The discharge valve mechanism is disposed in the flange portion and has a discharge valve longer in a defined direction and deformed to open when refrigerant compressed in the cylinder reaches a defined discharge pressure, and a valve pressing member suppressing further deformation of the discharge valve when the discharge valve opens. The valve pressing member has a main body portion longer in the length direction of the discharge valve, and a fixing portion protruding in a direction crossing the length direction of the discharge valve with respect to the main body portion and fixed to the bearing.

Description

[0001] This application is based on Japanese Patent Application No. 2021-140935 (Filing Date: August 31, 2021) and claims priority thereto. The entire contents of the application are incorporated herein by reference. TECHNICAL FIELD

[0002] Embodiments of the present application relate to a compressor and an air conditioner provided with the same. BACKGROUND

[0003] A compressor that compresses refrigerant is mounted in a refrigeration cycle device such as an air conditioner. The compressor is provided with, as main elements, a motor portion that rotates a rotary shaft, a compression mechanism portion that is linked to the motor portion via the rotary shaft, and a hermetic container that houses the motor portion and the compression mechanism portion. The motor portion includes, for example, a so-called inner rotor type motor, and is provided with a rotor that is fixedly attached to the rotary shaft and a stator that is fixed to an inner peripheral portion of the hermetic container. The rotary shaft has a crank portion (eccentric portion). The compression mechanism portion is provided with, for example, a cylinder that forms a cylinder chamber, and a roller that is fitted to the eccentric portion of the rotary shaft and eccentrically rotates in the cylinder chamber. The cylinder chamber is divided into a suction chamber and a compression chamber for refrigerant by a vane. The rotary shaft is rotatably supported by a bearing. The bearing has a flange portion that defines one face of the rotary shaft in the axial direction of the cylinder chamber, and a boss portion that protrudes in a cylindrical shape from the flange portion. Further, a muffler that suppresses pulsation and noise caused by refrigerant that is discharged into the hermetic container as a result of being compressed in the cylinder of the compression mechanism portion is attached to the bearing.

[0004] An exhaust port that exhausts refrigerant that has been compressed in the cylinder into the hermetic container, and an exhaust valve mechanism that controls opening and closing of the exhaust port are provided in the flange portion. Therefore, the flange portion has a recessed portion (cut-in portion) in which the exhaust valve mechanism is assembled in the vicinity of the exhaust port. The cut-in portion is formed by cutting down one face of the rotary shaft in the axial direction of the bearing, for example, the upper surface of the flange portion, by a prescribed depth. Therefore, the cut-in portion becomes thin-walled compared to other portions of the flange portion, and the rigidity of the bearing tends to decrease relatively. Thus, when the rotary shaft rotates, the cut-in portion may, for example, elastically deform in a manner that inclines the boss portion with respect to the flange portion. Depending on the degree of deformation of the cut-in portion, the support rigidity of the bearing with respect to the rotary shaft may decrease, and the rotary shaft may vibrate in a bent manner, increasing noise. SUMMARY

[0005] An object of the present application is to provide a compressor and an air conditioner provided with the same that can reduce noise generated as a result of the rotary shaft vibrating in a bent manner.

[0006] A compressor of one embodiment includes a cylinder, a rotating shaft, a bearing, and a discharge valve mechanism. The cylinder compresses a refrigerant. The rotating shaft has an eccentric portion disposed in the cylinder. The bearing has a flange portion that defines one face of the rotating shaft in the axial direction of the rotating shaft in the cylinder, and a boss portion that is continuous with the flange portion and extends in a cylindrical shape concentric with the rotating shaft to support the rotating shaft so as to be rotatable. The discharge valve mechanism includes a discharge valve that is longer in a predetermined direction and deforms to open when the refrigerant compressed in the cylinder reaches a predetermined discharge pressure, and a valve presser that suppresses further deformation of the discharge valve when the discharge valve opens. The discharge valve mechanism is disposed in the flange portion. The valve presser has a main body portion that is longer in the length direction of the discharge valve, and a fixing portion that projects from the main body portion in a direction intersecting the length direction of the discharge valve and is fixed to the bearing.

[0007] According to the compressor and the air conditioner including the compressor each having the above structure, noise generated by bending vibration of the rotating shaft can be reduced. BRIEF DESCRIPTION OF DRAWINGS

[0008] Figure 1 FIG. 1 is a circuit diagram schematically illustrating a configuration of an air conditioner of Embodiment 1.

[0009] Figure 2 FIG. 3 is a longitudinal sectional view of a compressor of Embodiment 1.

[0010] Figure 3 FIG. 6 is a perspective view schematically illustrating a bearing (first bearing) provided with a discharge valve mechanism (first discharge valve mechanism) of Embodiment 1.

[0011] Figure 4 FIG. 7 is a perspective view schematically illustrating a state in which only a discharge valve of the discharge valve mechanism (first discharge valve mechanism) is provided in the bearing (first bearing) of Embodiment 1. Figure 3

[0012] Figure 5 FIG. 8 is a view schematically illustrating a cross section of the bearing (first bearing) provided with the discharge valve mechanism (first discharge valve mechanism) of Embodiment 1.

[0013] Figure 6 FIG. 9 is a perspective view schematically illustrating a main body portion (valve presser piece) of a valve presser in the discharge valve mechanism (first discharge valve mechanism) of Embodiment 1.

[0014] Figure 7 FIG. 10 is a perspective view schematically illustrating a fixing portion (fixing piece) of the valve presser in the discharge valve mechanism (first discharge valve mechanism) of Embodiment 1.

[0015] Figure 8 ​is a perspective view schematically showing a bearing (1st bearing) provided with the discharge valve mechanism (1st discharge valve mechanism) of the 2nd embodiment.

[0016] Figure 9 is a perspective view schematically showing a state in which only the discharge valve in the discharge valve mechanism (1st discharge valve mechanism) is provided in Figure 8

[0017] Figure 10 is a view schematically showing a cross section of the bearing (1st bearing) provided with the discharge valve mechanism (1st discharge valve mechanism) of the 2nd embodiment.

[0018] Figure 11 is a perspective view schematically showing a fixing portion (fixing piece) of a valve pressing member in the discharge valve mechanism (1st discharge valve mechanism) of the 2nd embodiment.

[0019] Figure 12 is a perspective view schematically showing a bearing (1st bearing) provided with the discharge valve mechanism (1st discharge valve mechanism) of the 3rd embodiment.

[0020] Figure 13 is a perspective view schematically showing a state in which only the discharge valve in the discharge valve mechanism (1st discharge valve mechanism) is provided in Figure 12

[0021] Figure 14 is a view schematically showing a cross section of the bearing (1st bearing) provided with the discharge valve mechanism (1st discharge valve mechanism) of the 3rd embodiment.

[0022] Figure 15 is a perspective view schematically showing a valve pressing member (main body portion and fixing portion) in the discharge valve mechanism (1st discharge valve mechanism) of the 3rd embodiment. DETAILED DESCRIPTION

[0023] Hereinafter, with reference to Figures 1 to 15 the embodiments will be described.

[0024] (1st Embodiment)

[0025] Figure 1 is a refrigeration cycle circuit diagram of an air conditioner 1 of the present embodiment. The air conditioner 1 is a device that performs air conditioning by the refrigeration cycle, and is an example of a refrigeration cycle device. The air conditioner 1 is provided with a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an outdoor blower fan 40, an expansion device 5, an indoor heat exchanger 6, and an indoor blower fan 60 as main elements.

[0026] As Figure 1 ​​As shown, the discharge side of the compressor 2 is connected to a first port 3a of the four-way valve 3. A second port 3b of the four-way valve 3 is connected to the outdoor heat exchanger 4. The outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 via the expansion device 5. The indoor heat exchanger 6 is connected to a third port 3c of the four-way valve 3. A fourth port 3d of the four-way valve 3 is connected to the suction side of the compressor 2 via the accumulator 8.

[0027] The refrigerant circulates in the circulation circuit 7 from the discharge side of the compressor 2 via the outdoor heat exchanger 4, the expansion device 5, the indoor heat exchanger 6, and the accumulator 8 to the suction side. As the refrigerant, a chlorine-free refrigerant such as R448A, R449A, R449B, R407G, R407H, R449C, R456A, R516A, R406B, R463A, R744, an HC-based refrigerant, or the like is preferable.

[0028] For example, in the case where the air conditioner 1 is operated in a cooling mode, the four-way valve 3 is switched so that the first port 3a communicates with the second port 3b and the third port 3c communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the cooling mode, the high-temperature and high-pressure gas-phase refrigerant compressed by the compressor 2 is discharged to the circulation circuit 7. The discharged gas-phase refrigerant is guided to the outdoor heat exchanger 4 functioning as a condenser (heat sink) via the four-way valve 3.

[0029] The gas-phase refrigerant guided to the outdoor heat exchanger 4 is condensed by heat exchange with air (external air) drawn in by the outdoor blower fan 40 and changes to high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is depressurized in passing through the expansion device 5 and changes to low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 functioning as an evaporator (heat sink) and exchanges heat with air (internal air) drawn in by the indoor blower fan 60 in passing through the indoor heat exchanger 6.

[0030] As a result, the gas-liquid two-phase refrigerant evaporates by taking heat from the air and changes to low-temperature and low-pressure gas-phase refrigerant. The air passing through the indoor heat exchanger 6 is cooled by the latent heat of evaporation of the liquid-phase refrigerant and is sent as cool air to a place where air conditioning (cooling) should be performed by the indoor blower fan 60.

[0031] The low-temperature and low-pressure gas-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the accumulator 8 via the four-way valve 3. In the case where the refrigerant has liquid-phase refrigerant that has not completely evaporated mixed therein, the liquid-phase refrigerant and the gas-phase refrigerant are separated at this point. The low-temperature and low-pressure gas-phase refrigerant separated from the liquid-phase refrigerant is sucked into the compressor 2 from the accumulator 8 and is compressed again to high-temperature and high-pressure gas-phase refrigerant in the compressor 2 and is discharged to the circulation circuit 7.

[0032] On the other hand, when the air conditioner 1 is operating in heating mode, the four-way valve 3 is switched so that port 1 3a is connected to port 3c, and port 2 3b is connected to port 4 3d. When the air conditioner 1 starts operating in heating mode, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3 to exchange heat with the air passing through the indoor heat exchanger 6. In this case, the indoor heat exchanger 6 functions as a condenser.

[0033] As a result, the gaseous refrigerant passing through the indoor heat exchanger 6 condenses and transforms into a high-pressure liquid refrigerant through heat exchange with the air (internal gas) drawn in by the indoor fan 60. The air passing through the indoor heat exchanger 6 is heated through heat exchange with the gaseous refrigerant and is then delivered as warm air by the indoor fan 60 to the areas where air conditioning (heating) is required.

[0034] The high-temperature liquid refrigerant passing through the indoor heat exchanger 6 is guided to the expansion device 5, where it is depressurized and changes into a low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant is then guided to the outdoor heat exchanger 4, which functions as an evaporator, and evaporates by exchanging heat with the air (external gas) drawn in by the outdoor fan 40, changing into a low-temperature, low-pressure gas-phase refrigerant. This low-temperature, low-pressure gas-phase refrigerant, having passed through the outdoor heat exchanger 4, is drawn into the compressor 2 via the four-way valve 3 and the receiver 8, where it is again compressed into a high-temperature, high-pressure gas-phase refrigerant before being discharged into the circulation loop 7.

[0035] In addition, in this embodiment, the air conditioner 1 can be operated in either the cooling mode or the heating mode. However, the air conditioner 1 may also be a dedicated cooling unit or a dedicated heating unit that can only operate in either the cooling mode or the heating mode.

[0036] Next, refer to Figure 2 The specific configuration of the compressor 2 used in the air conditioner 1 will be explained. Figure 2 This is a longitudinal section view of compressor 2. (For example...) Figure 2 As shown, compressor 2 is a so-called vertical rotary compressor, which includes a sealed container 10, a compression mechanism 11, and an electric motor 12 as its main components. In the following description, based on the relative positional relationship between the compression mechanism 11 and the electric motor 12 arranged along the central axis O1 of the sealed container 10 (described later), the side where the compression mechanism 11 is located is designated as "down," and the side where the electric motor 12 is located is designated as "up."

[0037] The closed container 10 has a cylindrical peripheral wall 10a and stands vertically with respect to a setting surface. The setting surface is, for example, a bottom plate of an outdoor unit or the like. An exhaust pipe 10b is provided at an upper end of the closed container 10. The exhaust pipe 10b is connected to the first port 3a of the four-way valve 3 via the circulation circuit 7. A lubricating oil storage portion 10c that stores lubricating oil is provided at a lower portion of the closed container 10.

[0038] The compression mechanism portion 11 is housed in the lower portion of the closed container 10 in a manner of being immersed in the lubricating oil. Figure 2 In the example shown, the compression mechanism portion 11 has a double-cylinder configuration and includes a first cylinder 13, a second cylinder 14, and a rotating shaft 15 as main elements. The first cylinder 13 and the second cylinder 14 each have a roller (rotary piston) and a vane inside. Note that the number of cylinders of the compression mechanism portion is not limited to two and can be one or more than three.

[0039] The first cylinder 13 is fixed to an inner peripheral surface of the peripheral wall 10a of the closed container 10. The second cylinder 14 is fixed to a lower surface of the first cylinder 13 via a partition plate 18.

[0040] A first bearing 20 is fixed above the first cylinder 13. The first bearing 20 covers an inner diameter portion of the first cylinder 13 from above and protrudes toward an upper side of the first cylinder 13. A space surrounded by the inner diameter portion of the first cylinder 13, the partition plate 18, and the first bearing 20 constitutes a first cylinder chamber. The partition plate 18 corresponds to a sealing member that defines a lower surface of the first cylinder chamber, and the first bearing 20 corresponds to a sealing member that defines an upper surface of the first cylinder chamber.

[0041] A second bearing 22 is fixed below the second cylinder 14. The second bearing 22 covers an inner diameter portion of the second cylinder 14 from below and protrudes toward a lower side of the second cylinder 14. A space surrounded by the inner diameter portion of the second cylinder 14, the partition plate 18, and the second bearing 22 constitutes a second cylinder chamber. The partition plate 18 corresponds to a sealing member that defines an upper surface of the second cylinder chamber, and the second bearing 22 corresponds to a sealing member that defines a lower surface of the second cylinder chamber. The first cylinder chamber and the second cylinder chamber are arranged concentrically with respect to a central axis O1 of the closed container 10.

[0042] The first cylinder chamber and the second cylinder chamber are connected to the reservoir 8 via a portion of the circulation circuit 7, namely, a suction pipe (not shown). Gaseous refrigerant separated from liquid-phase refrigerant in the reservoir 8 is guided to the first cylinder chamber and the second cylinder chamber through the suction pipe.

[0043] The axis of the rotating shaft 15 is coaxially provided with the central axis O1 of the closed container 10, and the rotating shaft 15 penetrates the first cylinder chamber, the second cylinder chamber, and the partition plate 18. The rotating shaft 15 has a first journal portion 27a, a second journal portion 27b, and a pair of crank pin portions (eccentric portions) 28a, 28b. That is, the rotating shaft 15 is configured as a crankshaft. The first journal portion 27a is rotatably supported by the first bearing 20. The second journal portion 27b is rotatably supported by the second bearing 22.

[0044] Further, the rotating shaft 15 has an extension portion 27c coaxially extended from the first journal portion 27a. The extension portion 27c protrudes toward the upper side of the compression mechanism portion 11 while penetrating the first bearing 20. The rotor 33 of the motor portion 12 described later is fixed to the extension portion 27c.

[0045] The eccentric portions 28a, 28b are located between the first journal portion 27a and the second journal portion 27b. The eccentric portions 28a, 28b have, for example, a phase difference of 180 degrees, and have the same eccentricity with respect to the central axis O1 of the closed container 10. One eccentric portion (hereinafter referred to as the first eccentric portion) 28a is accommodated in the first cylinder chamber. The other eccentric portion (hereinafter referred to as the second eccentric portion) 28b is accommodated in the second cylinder chamber.

[0046] The rollers 16, 17 are respectively fitted and attached to the outer peripheral surfaces of the first eccentric portion 28a and the second eccentric portion 28b. A slight gap that allows the rollers 16, 17 to rotate with respect to the eccentric portions 28a, 28b is provided between the inner peripheral surfaces of the rollers 16, 17 and the outer peripheral surfaces of the eccentric portions 28a, 28b. Thus, when the rotating shaft 15 rotates, the rollers 16, 17 eccentrically rotate within the cylinder chambers, and a portion of the outer peripheral surfaces of the rollers 16, 17 contact the inner peripheral surfaces of the cylinder chambers via an oil film.

[0047] Vanes (not shown) are respectively arranged in the first cylinder 13 and the second cylinder 14. The vanes are supported to the cylinders 13, 14 in a state in which they are urged radially inward by an urging mechanism. The front end portions of the vanes are slidably pressed against the outer peripheral surfaces of the rollers 16, 17. These vanes and the rollers 16, 17 cooperate to divide the cylinder chambers of the cylinders 13, 14 into suction chambers and compression chambers, respectively, and move (advance and retreat) in a direction in which they protrude toward the cylinder chambers or retreat from the cylinder chambers, along with the eccentric rotation of the respective rollers 16, 17. In this way, by advancing and retreating the vanes with respect to the cylinder chambers, the volumes of the suction chambers and the compression chambers of the cylinder chambers change, and the gaseous refrigerant sucked into the cylinder chambers from the above-described suction pipe is compressed.

[0048] The high-temperature and high-pressure gas-phase refrigerant compressed in each of the cylinder chambers of the first cylinder 13 and the second cylinder 14 is discharged to the inside of the sealed container 10 via the discharge valve mechanisms 21, 23 described later. The discharged gas-phase refrigerant rises in the inside of the sealed container 10. Further, in the operation of the compression mechanism portion 11, the lubricating oil stored in the oil storage portion 10c of the sealed container 10 is stirred. The stirred lubricating oil becomes mist and rises toward the discharge pipe 10b in the inside of the sealed container 10 along with the flow of the gas-phase refrigerant. An oil separator or the like that separates the lubricating oil contained in the gas-phase refrigerant rising in the inside is assembled in the sealed container 10.

[0049] The motor portion 12 is housed in the middle portion along the central axis O1 of the sealed container 10 in a manner positioned between the compression mechanism portion 11 and the discharge pipe 10b. The motor portion 12 includes a so-called inner rotor type motor, and has a rotor 33 fixedly installed to the rotating shaft 15 and a stator 34 fixed to the inner circumferential surface of the peripheral wall 10a of the sealed container 10. By applying a voltage to the motor portion 12 from a power source, the rotor 33 rotates with the central axis O1 as a center with respect to the stator 34, and the rotating shaft 15 rotates together with the rotor 33. The rotating shaft 15 is rotatably supported by the two bearings 20, 22.

[0050] One of the two bearings 20, 22 is a main bearing (hereinafter referred to as a first bearing) 20, and the other is a sub bearing (hereinafter referred to as a second bearing) 22. The first bearing 20 and the second bearing 22 rotatably support the rotating shaft 15, respectively. Further, the first bearing 20 defines the upper surface of the first cylinder chamber in the first cylinder 13, and the second bearing 22 defines the lower surface of the second cylinder chamber in the second cylinder 14. The upper surface is an end surface of one end side of the cylinder 13, 14 in the axial direction of the rotating shaft 15 (the direction along the central axis O1 of the sealed container 10), and the lower surface is an end surface of the other end side of the cylinder 13, 14 in the direction. In other words, the first bearing 20 corresponds to a member that closes the first cylinder chamber from above, and the second bearing 22 corresponds to a member that closes the second cylinder chamber from below.

[0051] The first bearing 20 has a first flange portion 20a that defines the upper surface of the first cylinder chamber in the first cylinder 13, and a first boss portion 20b that is continuous with the first flange portion 20a and extends upward in a cylindrical shape.

[0052] The first flange portion 20a is located at the lower end of the first boss portion 20b, extends toward the radial direction outside of the first boss portion 20b, and is continuous in a circular shape concentric with the axis of the rotating shaft 15 throughout the entire circumference. The discharge hole (hereinafter referred to as a first discharge hole) 20c that discharges the refrigerant from the compression chamber of the first cylinder 13 is formed in the first flange portion 20a (see FIG. 2). Figure 4). The first discharge hole 20c penetrates a portion of the first flange portion 20a upward and downward, and communicates with the compression chamber of the first cylinder 13. The first discharge hole 20c is opened and closed by a prescribed valve mechanism (hereinafter referred to as a first discharge valve mechanism) 21. The first discharge valve mechanism 21 is disposed in the first flange portion 20a, and opens the first discharge hole 20c as the pressure in the compression chamber of the first cylinder 13 rises, discharging the high-temperature, high-pressure gas-phase refrigerant from this compression chamber.

[0053] The first boss portion 20b is a portion of the first bearing 20 through which the rotary shaft 15, specifically the first journal portion 27a, is inserted and rotatably supported. The first boss portion 20b is disposed concentrically with the rotary shaft 15. That is, the first boss portion 20b is disposed perpendicularly to the first flange portion 20a. The first journal portion 27a, in a state of being inserted through the first boss portion 20b, has an outer peripheral surface that slides against an inner peripheral surface of the first boss portion 20b.

[0054] The second bearing 22 has a second flange portion 22a that defines a lower surface of a second cylinder chamber in the second cylinder 14, and a second boss portion 22b that is continuous with the second flange portion 22a and extends downward in a cylindrical shape.

[0055] The second flange portion 22a is located at an upper end of the second boss portion 22b, extends toward a radial outer side of the second boss portion 22b, and is continuous in a circular shape concentric with an axis of the rotary shaft 15, throughout the entire circumference. A discharge hole (not shown, hereinafter referred to as a second discharge hole) that discharges refrigerant from the compression chamber of the second cylinder 14 is formed in the second flange portion 22a. The second discharge hole penetrates a portion of the second flange portion 22a upward and downward, and communicates with the compression chamber of the second cylinder 14. The second discharge hole is opened and closed by a prescribed valve mechanism (hereinafter referred to as a second discharge valve mechanism) 23. The second discharge valve mechanism 23 opens the second discharge hole as the pressure in the compression chamber of the second cylinder 14 rises, discharging the high-temperature, high-pressure gas-phase refrigerant from this compression chamber.

[0056] The second boss portion 22b is a portion of the second bearing 22 through which the rotary shaft 15, specifically the second journal portion 27b, is inserted and rotatably supported. The second boss portion 22b is disposed concentrically with the rotary shaft 15. That is, the second boss portion 22b is disposed perpendicularly to the second flange portion 22a. The second journal portion 27b, in a state of being inserted through the second boss portion 22b, has an outer peripheral surface that slides against an inner peripheral surface of the second boss portion 22b.

[0057] A muffler (hereinafter referred to as the first muffler) 41 is provided above the first bearing 20, covering the first bearing 20. The first muffler 41, for example, suppresses pulsation and noise caused by refrigerant discharged from the compression chamber of the first cylinder 13 into the sealed container 10. The first muffler 41 covers the first bearing 20 in a manner that surrounds the area between the first flange portion 20a and the first boss portion 20b, and a first muffler chamber 43 is formed between the first flange portion 20a and the first boss portion 20b. The first muffler chamber 43 is the space into which the high-temperature and high-pressure refrigerant, compressed in the compression chamber of the first cylinder 13, is first discharged from the first discharge port 20c. The first muffler 41 has a connecting port 41a that connects the inside and outside (top and bottom) of the first muffler 41. The high-temperature and high-pressure gaseous refrigerant discharged into the first muffler chamber 43 through the first discharge port 20c is discharged into the sealed container 10 through the connecting port 41a.

[0058] A muffler (hereinafter referred to as the second muffler) 42 is provided below the second bearing 22, covering the second bearing 22. The second muffler 42 suppresses, for example, the pulsation and noise caused by the refrigerant discharged from the compression chamber of the second cylinder 14 into the sealed container 10. The second muffler 42 covers the second bearing 22 in a manner that surrounds the area between the second flange portion 22a and the second boss portion 22b, and a second muffler chamber 44 is formed between the second flange portion 22a and the second boss portion 22b. The second muffler chamber 44 is the space into which the high-temperature and high-pressure refrigerant, compressed in the compression chamber of the second cylinder 14, is first discharged from the second discharge port. The second muffler chamber 44 communicates with the first muffler chamber 43 through a through hole provided in the compression mechanism portion 11. The through holes pass through the second flange 22a, the second cylinder 14, the partition plate 18, the first cylinder 13, and the first flange 20a, and open in the second muffler chamber 44 and the first muffler chamber 43. The high-temperature and high-pressure gaseous refrigerant discharged into the second muffler chamber 44 through the second discharge hole reaches the first muffler chamber 43 through the aforementioned through holes, and then is discharged into the sealed container 10 through the connecting hole 41a.

[0059] Figures 3 to 5 The diagram shows the configuration of the first discharge valve mechanism 21. Figure 3 This is a perspective view showing the first bearing 20 having the first discharge valve mechanism 21. Figure 4 It is a summary representation in Figure 3 The perspective view shows only the state of the discharge valve 21a, which will be described later, in the first discharge valve mechanism 21. Figure 5 This is a cross-sectional view that represents the first bearing 20 in summary.

[0060] like Figures 3 to 5As shown, the first discharge valve mechanism 21 is provided to the first flange portion 20a of the first bearing 20, and appropriately opens the first discharge hole 20c to discharge refrigerant compressed in the compression chamber of the first cylinder 13 from the compression chamber. The first discharge valve mechanism 21 includes a discharge valve 21a and a valve presser 21b.

[0061] The first discharge hole 20c is opened at the bottom of a recess (hereinafter referred to as a cutout portion) 20d formed in the first flange portion 20a. The cutout portion 20d is formed by cutting the upper surface (end surface on the one end side in the axial direction of the rotation shaft 15) 20e of the first flange portion 20a at a prescribed depth. In other words, the cutout portion 20d is formed in the first flange portion 20a as a recess for assembling the first discharge valve mechanism 21.

[0062] The cutout portion 20d has a first portion 24 and a second portion 25 that are each longer in a prescribed direction.

[0063] The first portion 24 is a recess in the cutout portion 20d in which the discharge valve 21a and the later-described main body portion 211 of the valve presser 21b of the first discharge valve mechanism 21 are assembled. Thus, the first portion 24 is formed to a depth and a profile that enable the discharge valve 21a and the main body portion 211 of the first discharge valve mechanism 21 to be assembled. The profile is the shape of the outer profile of the first portion 24 as viewed from above the first flange portion 20a. In the present embodiment, in a state of being assembled in the first portion 24, the discharge valve 21a and the valve presser 21b become a state of being immersed in the first portion 24. Further, the recess corresponding to the first portion 24 has the bottom of the cutout portion 20d in which the first discharge hole 20c is opened.

[0064] On the other hand, the second portion 25 is a recess in the cutout portion 20d in which the later-described fixing portion 212 of the valve presser 21b of the first discharge valve mechanism 21 is assembled. Thus, the second portion 25 is formed to a depth and a profile that enable the fixing portion 212 of the first discharge valve mechanism 21 to be assembled. The profile is the shape of the outer profile of the second portion 25 as viewed from above the first flange portion 20a. Further, the second portion 25 is disposed adjacently above the first portion 24.

[0065] The first portion 24 and the second portion 25 are disposed in a manner that the length directions thereof cross each other. Figures 3 to 5 In the example shown, the first portion 24 and the second portion 25 make the length directions thereof orthogonal to each other. The length direction of the second portion 25 is the radial direction of the first flange portion 20a, in other words, a direction orthogonal to the axis in a plane including the axis of the rotation shaft 15. The length direction of the first portion 24 is a direction orthogonal to the radial direction of the first flange portion 20a, in other words, a direction orthogonal to the plane including the axis of the rotation shaft 15.

[0066] The discharge valve 21a is a component used to close or open the first discharge port 20c, and is a plate-shaped component that is relatively long in a specified direction. The discharge valve 21a is formed into a rectangle, for example, from a resiliently deformable material such as spring steel. One end of the discharge valve 21a in the longitudinal direction is fixed to the first flange portion 20a by a fastener 21c. The fastener 21c can be any fastener such as a bolt, a small screw, or a rivet. Thus, the discharge valve 21a becomes a cantilevered leaf spring structure, with one end fixed in the longitudinal direction as the fixed end and the other end in the longitudinal direction as the free end, allowing it to flex and deform. Specifically, the discharge valve 21a deforms when the high-temperature, high-pressure gaseous refrigerant compressed in the compression chamber of the first cylinder 13 reaches a specified discharge pressure, thereby opening the first discharge port 20c. Hereinafter, this state of the discharge valve 21a will be referred to as the deformed state. In the state before the first discharge port 20c is opened (hereinafter referred to as the normal state), the discharge valve 21a is pressed against the periphery of the first discharge port 20c to close the first discharge port 20c by an elastic force (pressing force) smaller than the specified discharge pressure. Therefore, when the refrigerant exceeds the atmosphere pressure inside the first silencer 41 and reaches the specified discharge pressure, the discharge valve 21a deforms against the aforementioned elastic force (pressing force) and opens the first discharge port 20c, allowing the refrigerant to be discharged. When the first discharge port 20c is opened to allow the refrigerant to be discharged and the refrigerant discharge pressure is lower than the specified pressure, the discharge valve 21a elastically recovers from the deformed state and returns to the normal state, closing the first discharge port 20c again.

[0067] Figure 6 as well as Figure 7 The valve pressing member 21b is schematically shown in the diagram. The valve pressing member 21b is a component used to limit the deformation of the discharge valve 21a, and has a main body 211 and a fixing part 212. In this embodiment, as... Figure 6 as well as Figure 7 As shown, the main body 211 and the fixing part 212 of the valve pressing member 21b are configured as different components. That is, the valve pressing member 21b is configured by assembling the main body 211 and the fixing part 212, which are different components. Figure 6 This is a perspective view showing the main body (hereinafter referred to as valve pressing plate) 211 of the valve pressing member 21b. Figure 7 This is a perspective view showing the fixing part (hereinafter referred to as the fixing piece) 212 of the valve pressing member 21b in summary.

[0068] like Figures 3 to 6As shown, the valve pressing piece 211 is long in a prescribed direction and is a plate-shaped member thicker than the discharge valve 21a. The valve pressing piece 211 is an element of the valve pressing member 21b that mainly functions to limit deformation of the discharge valve 21a. The valve pressing piece 211 is formed of, for example, a steel material or the like. The valve pressing piece 211 is disposed with the length direction along the length direction of the discharge valve 21a. That is, the valve pressing piece 211 is formed long along the length direction of the discharge valve 21a. These length directions are directions orthogonal to the radial direction of the first flange portion 20a, in other words, directions orthogonal to a plane containing the axis of the rotation shaft 15. Further, these length directions are parallel to the length direction of the first portion 24 of the cut-in portion 20d. In Figures 3 to 5 In the example shown, the length directions are directions orthogonal to the radial direction of the first flange portion 20a, in other words, directions orthogonal to a plane containing the axis of the rotation shaft 15. That is, the length direction of the valve pressing piece 211 is parallel to a direction orthogonal to the plane containing the axis of the rotation shaft 15. One end of the length direction of the valve pressing piece 211 is fixed to the first flange portion 20a together with the discharge valve 21a by the fixing member 21c. The valve pressing piece 211 has a through-hole 211a through which the fixing member 21c is inserted.

[0069] The valve pressing piece 211 is disposed so as to oppose the discharge valve 21a during displacement of the discharge valve 21a to a position separate from the first discharge hole 20c when the first discharge hole 20c is opened. Figure 3 Further, the valve pressing piece 211 is disposed so as to oppose the discharge valve 21a during displacement of the discharge valve 21a to a position separate from the first discharge hole 20c when the first discharge hole 20c is opened. Figure 5 In the example shown, the valve pressing piece 211 is disposed above the discharge valve 21a so as to cover the discharge valve 21a. The valve pressing piece 211 is formed in a warped shape so as to follow the discharge valve 21a in a state of being flexed (floating) in a manner of opening the first discharge hole 20c, that is, in a deformed state (see FIG. 6). Figure 6 Thus, when the discharge valve 21a is flexed in a manner of opening the first discharge hole 20c to become in a deformed state, the valve pressing piece 211 comes into contact with the deformed discharge valve 21a, and the further deformation (floating) of the discharge valve 21a is suppressed.

[0070] The fixing piece 212 is fixed to the first bearing 20 and supports the valve pressing piece 211, and also reinforces the strength of the first flange portion 20a in the cut-in portion 20d. Figure 7 In the example shown, the fixing piece 212 is a separate member from the valve pressing piece 211. As shown in FIG. 2, Figure 3 , Figure 5 , Figure 7 As shown, the fixing piece 212 is long in a prescribed direction and is a member thicker than the discharge valve 21a, like the valve pressing member 21b. The fixing piece 212 is formed of, for example, the same steel material as the valve pressing piece 211.

[0071] The fixing piece 212 has a first piece portion 30a and a second piece portion 30b. The first piece portion 30a and the second piece portion 30b are continuous at right angles. A reinforcing portion 30c that fills between the first piece portion 30a and the second piece portion 30b obliquely is provided at the continuous portion thereof.

[0072] The first piece portion 30a is a portion of the fixing piece 212 that is fixed to the first flange portion 20a. The first piece portion 30a is formed in a long plate shape along the upper surface 20e of the first flange portion 20a. Further, the first piece portion 30a extends in a direction that is the length direction of the discharge valve 21a, in other words, a direction that intersects the length direction of the valve pressing piece 211, with respect to the valve pressing piece 211. The first piece portion 30a is disposed with the length direction along the radial direction of the first flange portion 20a, in other words, in a direction that is orthogonal to the axis of the rotation shaft 15 in a plane that includes the axis. That is, the length direction of the first piece portion 30a is parallel to the direction that is orthogonal to the axis of the rotation shaft 15 in a plane that includes the axis, that is, the length direction of the second portion 25 of the dug-in portion 20d.

[0073] The first piece portion 30a has a contact surface portion 30d that supports the valve pressing piece 211. The contact surface portion 30d is a flat surface portion that is formed so that a portion that can be opposed to the valve pressing piece 211 has a step with respect to other portions. The contact surface portion 30d contacts the valve pressing piece 211 from above and presses to support the valve pressing piece 211. Further, the first piece portion 30a has a through-hole 30e through which a bolt 31a is inserted. The bolt 31a is an example of a fixing member for fixing the first piece portion 30a with respect to the first flange portion 20a. As shown in Figure 4 , the first flange portion 20a has a through-hole 20f through which the bolt 31a is inserted. The through-hole 20f communicates with the through-hole 30e. In the present embodiment, as shown in Figure 2 , the first piece portion 30a is fastened to the first cylinder 13 together with the first muffler 41 via the first flange portion 20a by the bolt 31a. The first muffler 41 has a through-hole 41b through which the bolt 31a is inserted. Thus, a bolt for fastening the first piece portion 30a is not required in addition to the bolt for fastening the first muffler 41, and a space for fastening the bolt is not required.

[0074] As shown in Figure 3 , Figure 5 , Figure 7 , the second piece portion 30b is a portion of the fixing piece 212 that is fixed to the first boss portion 20b. The second piece portion 30b extends along the outer periphery of the first boss portion 20b. The second piece portion 30b is disposed so as to extend upward along the outer periphery of the first boss portion 20b, in other words, along the axis of the rotation shaft 15. In Figure 3 , Figure 5 , Figure 7In the example shown, the second piece 30b is thicker than the first piece 30a. The second piece 30b has a through hole 30f through which a bolt 31b is inserted. The bolt 31b is an example of a fastener used to fix the second piece 30b relative to the first boss 20b. Furthermore, the first boss 20b has a contact surface 20g that supports the second piece 30b. The contact surface 20g is a flat surface that allows the outer periphery of the first boss 20b, which is opposite the second piece 30b, to be formed with a stepped shape relative to other parts. Figure 4 As shown, the contact surface 20g has a bolt hole 20h for fastening bolt 31b. The bolt hole 20h communicates with the through hole 30f.

[0075] Therefore, such as Figure 5 As shown, the fixing plate 212 is fixed to the first bearing 20 at one location each on the first flange portion 20a and the first boss portion 20b, for a total of two locations. In other words, the fixing plate 212 is fixed to the first flange portion 20a by bolts 31a in the direction along the axis of rotation 15, and fixed to the first boss portion 20b by bolts 31b in the radial direction along the axis of rotation 15. In this fixed state, the fixing plate 212 is arranged orthogonally to the valve pressing plate 211, and supports the valve pressing plate 211 in the radial direction of the first flange portion 20a, in other words, in a direction orthogonal to the axis of rotation 15 on a plane containing the axis of rotation 15.

[0076] Thus, according to this embodiment, when the rotating shaft 15 rotates, for example, the fixing plate 212 can apply a force to the recess 20d to elastically deform the first boss portion 20b relative to the first flange portion 20a in a way that causes it to tilt. That is, the fixing plate 212 functions as a reinforcing member that increases the strength of the first flange portion 20a in the recess 20d. Therefore, elastic deformation of the recess 20d can be suppressed, and deformation such as the tilting of the first boss portion 20b relative to the first flange portion 20a can be suppressed. As a result, for example, noise generated by bending vibration of the rotating shaft 15 can be reduced.

[0077] Here, the configuration of the second discharge valve mechanism 23 is largely the same as that of the first discharge valve mechanism 21, except for the difference that its top and bottom positions are opposite to those of the first discharge valve mechanism 21. However, the second discharge valve mechanism 23 can also be configured such that the component corresponding to the fixing plate 212 is omitted. This is based on the following reasons. Figure 2As shown, the second boss portion 22b of the second bearing 22 has a shorter length in the axial direction of the rotating shaft 15 compared to the first boss portion 20b of the first bearing 20. That is, the second boss portion 22b is less prone to deformation such as tilting relative to the second flange portion 22a, and even if deformation occurs, the deformation will not be as large as that of the first boss portion 20b. Therefore, a component corresponding to the fixing plate 212 can be omitted in the second discharge valve mechanism 23. Taking these factors into consideration, the second discharge valve mechanism 23 can be constructed identically to the first discharge valve mechanism 21, except for the absence of a component corresponding to the fixing plate 212 and the difference in their opposite positions (top and bottom).

[0078] Furthermore, the form of the fixing piece 212 in the first discharge valve mechanism 21 is only one example of the fixing part of the valve pressing member, and is not limited to the first embodiment described above. Figure 3 , Figure 5 , Figure 7 (Example shown). Therefore, even if the fixing part has other forms, it can function as a reinforcing member that strengthens the first flange 20a in the recess 20d. Hereinafter, other forms of such fixing parts will be described as the second and third embodiments. In addition, the basic components of the compressors of the second and third embodiments are the same as those of the compressor 2 of the first embodiment ( Figure 2 Therefore, in the following description, the basic components of the compressor will be omitted or simplified, and the features of the second and third embodiments, i.e., the differences from the first embodiment, will be described in detail. At this time, the same reference numerals will be used for components that are the same as or similar to those in the first embodiment.

[0079] (Second Implementation)

[0080] Figures 8 to 11 The diagram shows the configuration of the discharge valve mechanism in this embodiment. The discharge valve mechanism is a valve mechanism equivalent to the first discharge valve mechanism 21 of the first embodiment (hereinafter referred to as the first discharge valve mechanism 51). Figure 8 This is a perspective view schematically showing the first bearing 50 equipped with the first discharge valve mechanism 51. The first bearing 50 is a main bearing equivalent to the first bearing in the first embodiment. Figure 9 It is a summary representation in Figure 8 A perspective view showing the state of only the discharge valve 21a in the first discharge valve mechanism 51. Figure 10 This is a cross-sectional view that represents the first bearing 50 in summary. Figure 11 This is a perspective view of the fixing part, namely the fixing piece 70, of the valve pressing member 21b in the first discharge valve mechanism 51.

[0081] like Figures 8 to 10As shown, the first discharge valve mechanism 51 is provided to the first flange portion 20a of the first bearing 50, appropriately opens the first discharge hole 20c, and discharges refrigerant compressed in the compression chamber of the first cylinder 13 from the compression chamber. The first discharge valve mechanism 51 includes a discharge valve 21a and a valve presser 21b. The first discharge valve mechanism 51 is assembled in the cutout portion 20d formed in the first flange portion 20a. As in the first embodiment, the cutout portion 20d is formed by cutting the upper surface 20e of the first flange portion 20a at a prescribed depth, and has a first portion 24 and a second portion 25 that are longer in a prescribed direction, respectively. Also, as in the first embodiment, the first discharge hole 20c is opened at the bottom of the cutout portion 20d.

[0082] In the first discharge valve mechanism 51, the discharge valve 21a and the valve presser 211 of the valve presser 21b are shaped as in the first embodiment.

[0083] The fixed piece 70 is a fixed portion of the valve presser 21b in the first discharge valve mechanism 51. The fixed piece 70 is fixed to the first bearing 50 and supports the valve presser 211, and also reinforces the first flange portion 20a in the cutout portion 20d. As shown, Figure 8 Figure 10 Figure 11 As shown, the fixed piece 70 is longer in a prescribed direction, is a thicker-walled member than the discharge valve 21a like the valve presser 211, and is formed separately from the valve presser 211. That is, the valve presser 21b is formed by assembling the valve presser 211 and the fixed piece 70 as separate members. In this regard, the valve presser 21b is the same as in the first embodiment. However, the fixed piece 70 is different from the fixed piece 212, and has only a portion corresponding to the first piece portion 30a, and does not have a portion corresponding to the second piece portion 30b or a portion corresponding to the reinforcing portion 30c.

[0084] The fixed piece 70 is formed in a longer plate shape along the upper surface 20e of the first flange portion 20a. The fixed piece 70 is disposed with the length direction along the radial direction of the first flange portion 20a, in other words, in a direction orthogonal to the axis of the rotary shaft 15 in a plane including the axis. That is, the length direction of the fixed piece 70 is parallel to the length direction of the second portion 25 of the cutout portion 20d, that is, the direction orthogonal to the axis of the rotary shaft 15 in a plane including the axis. The fixed piece 70 has a contact surface portion 70a that supports the valve presser 211. The contact surface portion 70a is a flat surface portion formed with a step difference between a portion that can be opposed to the valve presser 211 and other portions. The contact surface portion 70a contacts the valve presser 211 from above and supports the valve presser 211. Also, the fixed piece 70 has through-holes 70b and 70c through which bolts 71a and 71b are inserted. The bolts 71a and 71b are examples of fixing members for fixing the fixed piece 70 with respect to the first flange portion 20a. As shown,​​Figure 9 As shown, the second part 25 of the excavation section 20d has a through hole 20f for inserting a bolt 71a and a bolt hole 20i for fastening a bolt 71b.

[0085] like Figure 8 , Figure 10 , Figure 11 As shown, the through hole 70b is disposed near one end of the fixing plate 70 along its length, and the through hole 70c is disposed near the other end of the fixing plate 70 along its length. In this embodiment, the through hole 70b is located radially outward of the first flange 20a and communicates with the through hole 20f. The through hole 70c is located radially inward of the first flange 20a and communicates with the bolt hole 20i. Furthermore, in this embodiment, the fixing plate 70 is fastened to the first cylinder 13 via the first flange 20a and the first muffler 41 by bolts 71a. This is the same as the fixing plate 212 in the first embodiment. On the other hand, unlike the first embodiment, the fixing plate 70 is also fixed to the first flange 20a by bolts 71b.

[0086] Therefore, such as Figure 10 As shown, the fixing plate 70 is fixed to the first bearing 20 at two points on the first flange 20a. In other words, the fixing plate 70 is fixed to the first flange 20a by bolts 71a and 71b in the direction along the axis of rotation 15. In this fixed state, the fixing plate 70, like the fixing plate 212, is arranged orthogonally to the valve pressing plate 211, and supports the valve pressing plate 211 in the radial direction of the first flange 20a, in other words, in the direction orthogonal to the axis of rotation 15 on a plane containing the axis of rotation 15.

[0087] Thus, according to this embodiment, when the rotating shaft 15 rotates, for example, the fixing plate 70 can apply a force to the recessed portion 20d to elastically deform the first boss portion 20b relative to the first flange portion 20a. That is, the fixing plate 70 can function as a reinforcing member to increase the strength of the first flange portion 20a in the recessed portion 20d. Therefore, elastic deformation of the recessed portion 20d and tilting deformation of the first boss portion 20b can be suppressed, for example, noise generated due to bending vibration of the rotating shaft 15 can be reduced.

[0088] Furthermore, for the same reasons as in the first embodiment described above, in the valve mechanism of this embodiment, which corresponds to the second discharge valve mechanism 23, the component corresponding to the fixing plate 70 can be omitted. In this case, the valve mechanism can be configured in the same way as the first discharge valve mechanism 51, except that it does not have a component corresponding to the fixing plate 70 and that it is located in opposite positions (top and bottom).

[0089] (Third Implementation)

[0090] Figures 12 to 15 The configuration of the discharge valve mechanism of this embodiment is shown. The discharge valve mechanism is a valve mechanism equivalent to the first discharge valve mechanism 21 of the first embodiment (hereinafter referred to as the first discharge valve mechanism 81). Figure 12 This is a perspective view schematically showing the first bearing 80 equipped with the first discharge valve mechanism 81. The first bearing 80 is a main bearing equivalent to the first bearing in the first embodiment. Figure 13 It is a summary representation in Figure 12 The three-dimensional view shows only the state of the discharge valve 21a in the first discharge valve mechanism 81. Figure 14 This is a cross-sectional view that represents the first bearing 80 in summary. Figure 15 This is a perspective view of the valve pressing element 90 in the first discharge valve mechanism 81.

[0091] like Figures 12 to 15 As shown, a first discharge valve mechanism 81 is provided on the first flange portion 20a of the first bearing 80, appropriately opening the first discharge port 20c to discharge the refrigerant compressed in the compression chamber of the first cylinder 13. The first discharge valve mechanism 81 includes a discharge valve 21a and a valve pressing member 90. The first discharge valve mechanism 81 is assembled in a recessed portion 20d formed in the first flange portion 20a. Similar to the first embodiment, the recessed portion 20d is formed by excavating the upper surface 20e of the first flange portion 20a to a predetermined depth, and has a longer first portion 24 and a longer second portion 26 in a predetermined direction. The first portion 24 and the second portion 26 are arranged so that their length directions intersect each other. Figures 12 to 14 In the example shown, the first part 24 and the second part 26 are orthogonal to each other in their length directions. The length direction of the second part 26 is radial to the first flange 20a, in other words, it is a direction orthogonal to the axis containing the rotation shaft 15 in a plane. The length direction of the first part 24 is orthogonal to the radial direction of the first flange 20a, in other words, it is a direction orthogonal to the plane containing the axis containing the rotation shaft 15. The first discharge hole 20c opens at the bottom of the insertion part 20d.

[0092] In the first discharge valve mechanism 81, the shape of the discharge valve 21a is the same as that in the first embodiment.

[0093] like Figure 15 As shown, the valve pressing member 90 has a main body portion 91 and a fixing portion 92, which are configured as an integral part. That is, both the main body portion 91 and the fixing portion 92 are part of the valve pressing member 90 that constitutes an integral part.

[0094] The main body portion 91 is formed in a long plate shape along the upper surface 20e of the first flange portion 20a. The length direction of the main body portion 91 is a direction along the length direction of the discharge valve 21a. The main body portion 91 is arranged with the length direction in a direction orthogonal to the radial direction of the first flange portion 20a, in other words, in a direction orthogonal to the plane including the axis of the rotation shaft 15. That is, the length direction of the main body portion 91 is parallel to the length direction of the first portion 24 of the cut-in portion 20d, which is orthogonal to the plane including the axis of the rotation shaft 15. One end of the length direction of the main body portion 91 is fixed to the first flange portion 20a by the fixing member 21c together with the discharge valve 21a. Further, the main body portion 91 has a through-hole 91a through which the fixing member 21c is inserted.

[0095] The fixing portion 92 is a portion that extends continuously from the main body portion 91 and is fixed to the first bearing 80. In the example shown in the drawing, the fixing portion 92 is formed in a pair, and extends in opposite directions from the vicinity of the middle portion of the length direction of the main body portion 91. That is, the fixing portion 92 extends in a direction orthogonal to the length direction of the main body portion 91, in other words, in a direction orthogonal to the plane including the axis of the rotation shaft 15. The fixing portions 92a, 92b are each arranged at a right angle to the main body portion 91. The fixing portions 92a, 92b are arranged along the radial direction of the first flange portion 20a, in other words, in a direction orthogonal to the axis of the rotation shaft 15 in the plane including the axis. That is, the extending direction of the fixing portions 92a, 92b, in particular, the length direction of the fixing portion 92, is parallel to the length direction of the second portion 26 of the cut-in portion 20d, which is orthogonal to the axis of the rotation shaft 15 in the plane. Figure 15 Further, the fixing portions 92a, 92b have through-holes 90a, 90b through which bolts 93a, 93b are inserted. The bolts 93a, 93b are examples of fixing members for fixing the fixing portions 92a, 92b with respect to the first flange portion 20a. As shown in the drawing, the second portion 26 of the cut-in portion 20d has bolt holes 20j, 20k for fastening the bolts 93a, 93b. The through-hole 90a is provided in the fixing portion 92a, and the through-hole 90b is provided in the fixing portion 92b. In the present embodiment, the through-hole 90a is located at a position on the outer side in the radial direction of the first flange portion 20a and communicates with the bolt hole 20j. The through-hole 90b is located at a position on the inner side in the radial direction of the first flange portion 20a and communicates with the bolt hole 20k.

[0096] Figure 13 Thus, as shown in the drawing, the fixing portions 92a, 92b are fixed to the first flange portion 20a by the bolts 93a, 93b. The fixing portions 92a, 92b are fixed to the first flange portion 20a in a direction orthogonal to the plane including the axis of the rotation shaft 15, in other words, in a direction orthogonal to the length direction of the main body portion 91. That is, the fixing portions 92a, 92b are fixed to the first flange portion 20a in a direction orthogonal to the length direction of the main body portion 91, in other words, in a direction orthogonal to the plane including the axis of the rotation shaft 15.

[0097] Thus, as shown in the drawing, the fixing portions 92a, 92b are fixed to the first flange portion 20a by the bolts 93a, 93b. The fixing portions 92a, 92b are fixed to the first flange portion 20a in a direction orthogonal to the plane including the axis of the rotation shaft 15, in other words, in a direction orthogonal to the length direction of the main body portion 91. That is, the fixing portions 92a, 92b are fixed to the first flange portion 20a in a direction orthogonal to the length direction of the main body portion 91, in other words, in a direction orthogonal to the plane including the axis of the rotation shaft 15. Figure 14 ​As shown, the fixing portion 92 is fixed with respect to the first flange portion 20a at two places of the first flange portion 20a, respectively. In other words, the fixing portion 92 is fixed with respect to the first flange portion 20a by the bolts 93a, 93b in the direction along the axis of the rotation shaft 15, respectively. In this state of being fixed, the fixing portion 92 is arranged in a direction orthogonal to the main body portion 91, and supports the main body portion 91 in the radial direction of the first flange portion 20a, in other words, in a direction orthogonal to the axis of the rotation shaft 15 in the plane including the axis. That is, the valve presser 90 is supported in the radial direction of the first flange portion 20a, in other words, in a direction orthogonal to the axis of the rotation shaft 15 in the plane including the axis.

[0098] Thus, according to the present embodiment, when the rotation shaft 15 rotates, for example, a force that elastically deforms the fixing portion 92 so as to incline the first boss portion 20b with respect to the first flange portion 20a can be loaded to the dug-in portion 20d. That is, the valve presser 90 can function as a reinforcing member that increases the strength of the first flange portion 20a in the dug-in portion 20d. Therefore, the elastic deformation of the dug-in portion 20d and the inclined deformation of the first boss portion 20b can be suppressed, and for example, noise generated due to the bending vibration of the rotation shaft 15 can be reduced.

[0099] In addition, for the same reason as the above-described first embodiment, in the valve mechanism of the present embodiment corresponding to the second discharge valve mechanism 23, a portion corresponding to the fixing portion 92 of the valve presser 90 can be omitted. In this case, the valve mechanism can be configured similarly to the first discharge valve mechanism 81 except for the point that it does not have a fixing portion corresponding to the fixing portion 92 and the difference that the upper and lower (top and bottom) positions are reversed.

[0100] The above-described embodiments of the present application have been described, but these embodiments are presented as examples and are not intended to limit the scope of the application. These new embodiments can be implemented in various other ways, and various omissions, substitutions, and modifications can be made within the scope of the gist of the application. These embodiments and modifications are included in the scope and gist of the application, and are included in the scope of the application and equivalents thereof described in the claims.

Claims

1. A compressor, comprising: a cylinder that compresses a refrigerant; a rotating shaft having an eccentric portion provided to the cylinder; a bearing having a flange portion that defines one face of the rotating shaft in an axial direction in the cylinder, and a boss portion that is continuous with the flange portion and extends in a tubular shape concentric with the rotating shaft to support the rotating shaft so as to be rotatable; the flange portion extending toward a radially outer side of the boss portion and being continuous in a circular shape concentric with the axis of the rotating shaft over the entire circumference; and a discharge valve mechanism provided to the flange portion, having a discharge valve that is long in a direction orthogonal to the radial direction of the flange portion and that deforms to open when the refrigerant compressed in the cylinder reaches a predetermined discharge pressure, and a valve presser that suppresses further deformation of the discharge valve when the discharge valve opens, the valve presser having a main body portion that is long in a length direction of the discharge valve, and a fixed portion that projects from the main body portion in a direction intersecting the length direction of the discharge valve and is fixed to the bearing, the fixed portion having a first piece portion fixed to the flange portion, and a second piece portion continuously formed with the first piece portion and fixed to the boss portion, a recess portion in which the discharge valve mechanism is assembled is formed in the flange portion, the recess portion has a first portion and a second portion that are arranged with their length directions intersecting each other, the length direction of the first portion is parallel to the length direction of the main body portion, and the length direction of the second portion is parallel to the length direction of the fixed portion.

2. The compressor according to claim 1, further comprising a muffler that is mounted to the bearing, forms a muffler chamber between the flange portion and the boss portion, and discharges the refrigerant compressed in the cylinder, the first piece portion is fastened to the flange portion together with the muffler by a bolt.

3. An air conditioner, comprising: the compressor according to claim 1; a condenser connected to the compressor; an expansion device connected to the condenser; and an evaporator connected to the expansion device. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​

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