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 is provided with a cylinder, a rotating shaft, a bearing, a discharge valve mechanism, and a muffler. The discharge valve mechanism, which is arranged at a flange portion of the bearing, has a discharge valve that is longer in a prescribed direction and that is deformed to open when refrigerant compressed in the cylinder reaches a prescribed discharge pressure, and a valve pressing member that suppresses further deformation of the discharge valve when the discharge valve is opened. The muffler covers the bearing in a manner surrounding between the flange portion and a boss portion, forms a muffler chamber for discharging the refrigerant compressed in the cylinder, and defines an outer profile of the muffler chamber by a face portion on one end side in an axial direction of the rotating shaft, a flange portion on the other end side in the axial direction of the rotating shaft, and a side face portion that connects the face portion and the flange portion in a cylindrical shape over the entire circumference of the rotating shaft, and has recesses in which the face portion and the side face portion are respectively recessed inward of the muffler chamber.

Description

[0001] This application is based on Japanese Patent Application No. 2021-140934 (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, a discharge valve mechanism, and a muffler. 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 an axial direction 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 rotatably support the rotating shaft. The discharge valve mechanism is disposed in the flange portion and 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 muffler covers the bearing in a manner surrounding between the flange portion and the boss portion, forms a muffler chamber for discharging the refrigerant compressed in the cylinder between the flange portion and the boss portion, and defines an outer profile of the muffler chamber with an end face portion that is a face portion on one end side in the axial direction of the rotating shaft, a flange portion that is a face portion on the other end side in the axial direction of the rotating shaft, and a side face portion that connects the end face portion and the flange portion in a cylindrical shape in a circumferential direction of the rotating shaft, and has recesses into which the end face portion and the side face portion are respectively recessed inward of the muffler chamber.

[0007] According to the compressor and the air conditioner each including the compressor, 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 showing the configuration of an air conditioner of one embodiment.

[0009] Figure 2 FIG. 2 is a longitudinal sectional view of a compressor of one embodiment.

[0010] Figure 3 FIG. 3 is a view schematically showing a bearing (a first bearing) having a discharge valve mechanism of the compressor of one embodiment from above.

[0011] Figure 4 FIG. 4 is a view schematically showing a cross section of the bearing (the first bearing) shown in part of an arrow A3 in FIG. 3. Figure 3

[0012] Figure 5 FIG. 5 is a view schematically showing a state in which a muffler (a first muffler) of the compressor of one embodiment is assembled to the bearing (the first bearing) from above.

[0013] Figure 6 FIG. 6 is a perspective view schematically showing the muffler (the first muffler) of the compressor of one embodiment. DETAILED DESCRIPTION ​

[0014] Hereinafter, referring to Figures 1 to 6 An embodiment will be described.

[0015] 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 has, as main elements, 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.

[0016] As shown in Figure 1 , 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 a reservoir 8.

[0017] A refrigerant circulates in a cycle circuit 7 from the discharge side of the compressor 2 to the suction side via the outdoor heat exchanger 4, the expansion device 5, the indoor heat exchanger 6, and the reservoir 8. 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.

[0018] For example, in a 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 cycle circuit 7. The discharged gas-phase refrigerant is guided to the outdoor heat exchanger 4, which functions as a condenser (heat sink), via the four-way valve 3.

[0019] 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, which functions 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.

[0020] As a result, the gas-liquid two-phase refrigerant takes heat from the air and evaporates, changing to low-temperature, low-pressure gas-phase refrigerant. The air that has passed 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 by the indoor blower fan 60 to a place where air conditioning (cooling) should be performed.

[0021] The low-temperature, 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 liquid-phase refrigerant that has not completely evaporated is mixed in the refrigerant, it is separated here into liquid-phase refrigerant and gas-phase refrigerant. The low-temperature, low-pressure gas-phase refrigerant that has separated from the liquid-phase refrigerant is sucked from the accumulator 8 into the compressor 2, and is again compressed to high-temperature, high-pressure gas-phase refrigerant in the compressor 2 and discharged to the circulation circuit 7.

[0022] On the other hand, in the case where the air conditioner 1 is operated in the heating mode, the four-way valve 3 is switched so that the first port 3a communicates with the third port 3c and the second port 3b communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the heating mode, the high-temperature, high-pressure gas-phase refrigerant that is discharged from the compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3 and exchanges heat with the air that passes through the indoor heat exchanger 6. In this case, the indoor heat exchanger 6 functions as a condenser.

[0023] As a result, the gas-phase refrigerant that has passed through the indoor heat exchanger 6 is condensed by exchanging heat with the air (inside air) that is sucked by the indoor blower fan 60, changing to high-pressure liquid-phase refrigerant. The air that has passed through the indoor heat exchanger 6 is heated by exchanging heat with the gas-phase refrigerant, and is sent as warm air by the indoor blower fan 60 to a place where air conditioning (heating) should be performed.

[0024] The high-temperature liquid-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the expansion device 5, and is depressurized in the process of passing through the expansion device 5, changing to low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 4, which functions as an evaporator, and evaporates by exchanging heat with the air (outside air) that is sucked by the outdoor blower fan 40, changing to low-temperature, low-pressure gas-phase refrigerant. The low-temperature, low-pressure gas-phase refrigerant that has passed through the outdoor heat exchanger 4 is sucked into the compressor 2 via the four-way valve 3 and the accumulator 8, and is again compressed to high-temperature, high-pressure gas-phase refrigerant in the compressor 2 and discharged to the circulation circuit 7.

[0025] In addition, in the present embodiment, the air conditioner 1 is able to be operated in either of the cooling mode and the heating mode, but the air conditioner 1 may, for example, be a cooling-only machine or a heating-only machine that is able to be operated in only one of the cooling mode and the heating mode.

[0026] Next, the operation of the air conditioner 1 will be described with reference to FIG. 2. Figure 2The detailed configuration of the compressor 2 for the air conditioner 1 will be described. Figure 2 is a longitudinal sectional view of the compressor 2. As shown in Figure 2 , the compressor 2 is a so-called vertical rotary compressor, and has, as main elements, a hermetic container 10, a compression mechanism portion 11, and a motor portion 12. In the following description, the side on which the compression mechanism portion 11 is located is set as the lower side, and the side on which the motor portion 12 is located is set as the upper side, with reference to the relative positional relationship between the compression mechanism portion 11 and the motor portion 12 arranged along the central axis O1 of the hermetic container 10 described later.

[0027] The hermetic container 10 has a cylindrical peripheral wall 10a, and stands vertically with respect to a setting surface. The setting surface is, for example, a floor panel of an outdoor unit or the like. An exhaust pipe 10b is provided at the upper end of the hermetic container 10. The exhaust pipe 10b is connected to the first port 3a of the four-way valve 3 via a circulation circuit 7. An oil reservoir portion 10c that accumulates lubricating oil is provided at the lower portion of the hermetic container 10.

[0028] The compression mechanism portion 11 is housed in the lower portion of the hermetic container 10 in a manner to be immersed in the lubricating oil. In the example shown in Figure 2 , the compression mechanism portion 11 has a double-cylinder configuration, and has, as main elements, a first cylinder 13, a second cylinder 14, and a rotary shaft 15. The first cylinder 13 and the second cylinder 14 each have a roller (rotary piston) and a vane inside. The number of cylinders of the compression mechanism portion is not limited to two, and can be one or more than three.

[0029] The first cylinder 13 is fixed to the inner peripheral surface of the peripheral wall 10a of the hermetic container 10. The second cylinder 14 is fixed to the lower surface of the first cylinder 13 via a partition plate 18.

[0030] A first bearing 20 is fixed above the first cylinder 13. The first bearing 20 covers the inner diameter portion of the first cylinder 13 from above, and protrudes toward the upper side of the first cylinder 13. The 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 closing member that defines the lower surface of the first cylinder chamber, and the first bearing 20 corresponds to a closing member that defines the upper surface of the first cylinder chamber.

[0031] A second bearing 22 is fixed below the second cylinder 14. The second bearing 22 covers the inner diameter portion of the second cylinder 14 from below and protrudes toward the 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 the upper surface of the second cylinder chamber, and the second bearing 22 corresponds to a closing member that defines the lower surface of the second cylinder chamber. The first cylinder chamber and the second cylinder chamber are arranged concentrically with the central axis O1 of the sealed container 10.

[0032] 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 refrigerant in the reservoir 8 is guided to the first cylinder chamber and the second cylinder chamber through the suction pipe.

[0033] The axis of the rotating shaft 15 is arranged coaxially with the central axis O1 of the sealed 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.

[0034] Further, the rotating shaft 15 has an extension portion 27c that is 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.

[0035] 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 the amounts of eccentricity with respect to the central axis O1 of the sealed container 10 are the same as each other. One eccentric portion (hereinafter referred to as a first eccentric portion) 28a is accommodated in the first cylinder chamber. The other eccentric portion (hereinafter referred to as a second eccentric portion) 28b is accommodated in the second cylinder chamber.

[0036] The rollers 16, 17 are respectively fitted 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 is brought into contact with the inner peripheral surfaces of the cylinder chambers via an oil film.

[0037] A vane (not shown) is provided in each of the first cylinder 13 and the second cylinder 14. The vane is supported to the cylinder 13, 14 in a state of being urged by an urging mechanism toward the radially inner side. The front end portion of each vane is slidably pressed against the outer peripheral surface of the roller 16, 17. These vanes cooperate with the rollers 16, 17 to divide the cylinder chamber of the cylinder 13, 14 into a suction chamber and a compression chamber, and move (advance and retreat) in a direction of protruding toward the cylinder chamber or retreating from the cylinder chamber with eccentric rotation of each roller 16, 17. Thus, by making the vanes advance and retreat with respect to the cylinder chamber, the volume of the suction chamber and the compression chamber of the cylinder chamber changes, and the gaseous refrigerant sucked into the cylinder chamber from the above-mentioned suction pipe is compressed.

[0038] The high-temperature and high-pressure gaseous refrigerant compressed in each cylinder chamber 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 gaseous 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 gaseous refrigerant. An oil separator or the like that separates the lubricating oil contained in the gaseous refrigerant rising in the inside is assembled in the sealed container 10.

[0039] The motor portion 12 is housed in the middle portion along the central axis O1 of the sealed container 10 in a manner of being located 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 peripheral 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.

[0040] 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.

[0041] The first bearing 20 has a first flange portion 20a that defines an upper surface of a 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 in a cylindrical shape upward.

[0042] The first flange portion 20a is located at a lower end of the first boss portion 20b, extends toward a radial outer side of the first boss portion 20b, and is continuous in a circular shape concentric with an axis of the rotary shaft 15 over the entire circumference. An exhaust hole (hereinafter referred to as a first exhaust hole) 20c that discharges refrigerant from a compression chamber of the first cylinder 13 is formed in the first flange portion 20a (see FIG. 2). Figure 3 The first exhaust 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 exhaust hole 20c is opened and closed by a prescribed valve mechanism (hereinafter referred to as a first exhaust valve mechanism) 21. The first exhaust valve mechanism 21 is disposed in the first flange portion 20a, and opens the first exhaust hole 20c as the pressure in the compression chamber of the first cylinder 13 rises, to discharge high-temperature and high-pressure gas-phase refrigerant from the compression chamber.

[0043] The first boss portion 20b is a portion of the first bearing 20 through which the rotary shaft 15, specifically, a first journal portion 27a is inserted and is 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 slides an outer peripheral surface with respect to an inner peripheral surface of the first boss portion 20b in a state of being inserted into the first boss portion 20b.

[0044] 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 in a cylindrical shape downward.

[0045] 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 over the entire circumference. An exhaust hole (not shown. Hereinafter referred to as a second exhaust hole) that discharges refrigerant from a compression chamber of the second cylinder 14 is formed in the second flange portion 22a. The second exhaust 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 exhaust hole is opened and closed by a prescribed valve mechanism (hereinafter referred to as a second exhaust valve mechanism) 23. The second exhaust valve mechanism 23 opens the second exhaust hole as the pressure in the compression chamber of the second cylinder 14 rises, to discharge high-temperature and high-pressure gas-phase refrigerant from the compression chamber.

[0046] The second boss portion 22b is the part of the second bearing 22 through which the rotating shaft 15, specifically the second journal 27b, is inserted and rotatably supported. The second boss portion 22b is concentrically arranged with the rotating shaft 15. That is, the second boss portion 22b is arranged perpendicularly to the second flange portion 22a. When the second journal 27b is inserted into the second boss portion 22b, its outer peripheral surface slides relative to the inner peripheral surface of the second boss portion 22b.

[0047] Figure 3 as well as Figure 4 The diagram shows the configuration of the first discharge valve mechanism 21. Figure 3 This is a diagram showing, from above, a schematic representation of the first bearing 20 having the first discharge valve mechanism 21. Figure 4 It is a summary representation Figure 3 The diagram shows a cross-sectional view of the first bearing 20 at the point indicated by arrow A3. The configurations of the first discharge valve mechanism 21 and the second discharge valve mechanism 23 are almost identical, except for the difference in their opposite vertical (top and bottom) positions. Therefore, the configuration of the second discharge valve mechanism 23 is... Figure 3 as well as Figure 4 The configuration shown is the basis. Therefore, the configuration example of the first discharge valve mechanism 21 will be described below.

[0048] like Figure 3 as well as Figure 4 As shown, the first discharge valve mechanism 21 is disposed on the first flange portion 20a of the first bearing 20, thereby 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 21 includes a discharge valve 21a and a valve pressing member 21b. The discharge valve 21a and the valve pressing member 21b are fixed to the first flange portion 20a by a predetermined fastener 21c. As the fastener 21c, any fastener such as bolts, small screws, or rivets can be used.

[0049] The first discharge hole 20c is opened at the bottom of a recess (hereinafter referred to as a cut-in portion) 20d formed in the first flange portion 20a. The cut-in portion 20d is formed by recessing 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 by a prescribed depth. The depth of the cut-in portion 20d is substantially the same as the size in the vertical direction of the first discharge valve mechanism 21 (the overlapping discharge valve 21a and valve presser 21b). The profile of the cut-in portion 20d as viewed from above the first flange portion 20a is slightly larger than the profile of the first discharge valve mechanism 21 as viewed from above, so that the first discharge valve mechanism 21 (the discharge valve 21a and valve presser 21b) can be assembled. That is, the lengthwise direction of the cut-in portion 20d is parallel to the lengthwise direction of the discharge valve 21a and valve presser 21b described later. By making the cut-in portion 20d in this form, the first discharge valve mechanism 21 becomes submerged in the cut-in portion 20d in the state of being assembled in the cut-in portion 20d. In other words, the cut-in portion 20d is formed in the first flange portion 20a as a recess for assembling the first discharge valve mechanism 21. Also, in the second flange portion 22a of the second bearing 22, a cut-in portion 22d identical to the cut-in portion 20d is formed as a recess for assembling the second discharge valve mechanism 23 (see FIG. 2). Figure 2 ).

[0050] The discharge valve 21a is a member for occluding or opening the first discharge hole 20c, and is formed in a plate shape that is long in a prescribed direction. The discharge valve 21a is formed in a rectangular shape, for example, from a raw material that can be elastically deformed, such as spring steel. Thus, the discharge valve 21a becomes a plate spring structure that has one end in the lengthwise direction fixed by a fixing member 21c as a fixed end, and the other end in the lengthwise direction as a free end, and can be flexibly deformed. Specifically, the discharge valve 21a deforms when the high-temperature, high-pressure gas-phase refrigerant in the compression chamber of the first cylinder 13 reaches a prescribed discharge pressure, and opens the first discharge hole 20c. Hereinafter, this state of the discharge valve 21a is referred to as a deformed state. In a state before the first discharge hole 20c is opened (hereinafter referred to as a normal state), the discharge valve 21a is in pressure contact with the periphery of the first discharge hole 20c, so as to occlude the first discharge hole 20c by an elastic force (pressing force) that is smaller than the prescribed discharge pressure. Thus, when the refrigerant exceeds the atmospheric pressure in the first muffler 41 and reaches the prescribed discharge pressure, the discharge valve 21a deforms against the above-described elastic force (pressing force) to open the first discharge hole 20c, and the refrigerant is discharged. When the first discharge hole 20c is opened to discharge the refrigerant, and the discharge pressure of the refrigerant falls below the prescribed pressure, the discharge valve 21a elastically returns from the deformed state to the normal state, and again occludes the first discharge hole 20c.

[0051] The valve pressing member 21b is a component used to limit the deformation of the discharge valve 21a. It is longer in a predetermined direction and is formed as a plate with a thicker wall than the discharge valve 21a. The valve pressing member 21b is formed, for example, of steel. The valve pressing member 21b is arranged with its length direction along the length direction of the discharge valve 21a. These length directions are directions that intersect the radial direction of the first flange portion 20a, in other words, directions that intersect the plane containing the axis of rotation 15. Furthermore, these length directions are parallel to the length direction of the recessed portion 20d. Figure 3 In the example shown, the length direction is orthogonal to the radial direction of the first flange 20a, in other words, orthogonal to the plane containing the axis of rotation 15. The valve press member 21b is configured to oppose the discharge valve 21a as the discharge valve 21a displaces to a position separate from the first discharge port 20c when the first discharge port 20c is opened. Figure 3 as well as Figure 4 In the example shown, the valve press member 21b is positioned above the discharge valve 21a, covering it. The valve press member 21b is formed in a warped shape so that the discharge valve 21a is in a deformed state, flexed (lifted) to open the first discharge port 20c. Thus, when the discharge valve 21a is flexed and deformed to open the first discharge port 20c, i.e., in a deformed state, the valve press member 21b contacts the deformed discharge valve 21a, preventing further deformation (lifting) of the discharge valve 21a.

[0052] 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.

[0053] like Figure 2As shown, a muffler (hereinafter referred to as the second muffler) 42 covering the second bearing 22 is provided below 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.

[0054] Figure 5 as well as Figure 6 The diagram shows the configuration of the first muffler 41 in this embodiment. Figure 5 This is a diagram showing, from above, the state in which the first muffler 41 is assembled with the first bearing 20. Figure 6 This is a perspective view that schematically represents the first muffler 41.

[0055] like Figures 4 to 6 As shown, the first muffler 41 is a three-dimensional element having three parts: an end face 45, a side face 46, and a protruding edge 47, all of which are thin-walled. The end face 45, the side face 46, and the protruding edge 47 define the external contour of the first muffler chamber 43. The end face 45 is the face of one end of the first muffler 41 in the axial direction of the rotation shaft 15 (along the direction of the central axis O1 of the sealed container 10), and it is a face that extends radially relative to the axis of the rotation shaft 15. Figure 5 as well as Figure 6 In the example shown, the end portion 45 corresponds to the upper surface portion of the first muffler 41. The end portion 45 is formed as an annular shape with a circular opening 45a through which the first boss portion 20b of the first bearing 20 is inserted. The center of the opening 45a is located on the axis of the rotating shaft 15 (the central axis O1 of the sealed container 10). In other words, the first muffler 41 is configured such that the opening 45a is concentric with the rotating shaft 15. The diameter of the opening 45a is approximately the same as the outer diameter at the insertion portion of the first boss portion 20b.

[0056] The end face 45 has five plates 45b to 45f extending radially relative to the center of the opening 45a. The five plates 45b to 45f are arranged at approximately equal intervals in the circumferential direction of the opening 45a. The five plates 45b to 45f are smoothly continuous with each other, except between plates 45b and 45f, gradually approaching the center line of the opening 45a (the central axis O1 of the sealed container 10). A connecting hole 41a is formed on four of the plates 45b to 45e. Furthermore, the number of plates in the end face is not limited to five; it can be four or fewer, or six or more.

[0057] The side portion 46 extends all the way around the opening 45a, in other words, around the entire circumference of the axis of rotation 15, connecting the end portion 45 (specifically, the five plates 45b to 45f) and the convex edge 47 in a cylindrical shape. That is, the side portion 46 corresponds to the outer periphery of the first muffler 41. The side portion 46 is formed as a cylinder that is thinner on the side continuous with the end portion 45 than on the side continuous with the convex edge 47. In other words, the side portion 46 is inclined in such a way that the closer it is to the center line of the opening 45a (the central axis O1 of the sealed container 10) the further it is from the side continuous with the convex edge 47 toward the side continuous with the end portion 45.

[0058] The convex edge 47 is the face of the other end of the first silencer 41 in the axial direction of the rotation shaft 15 (along the direction of the central axis O1 of the sealed container 10), and is a circular face that extends approximately parallel to the end face 45 and is concentric with the axis of the rotation shaft 15. Figure 5 as well as Figure 6 In the example shown, the protruding edge 47 corresponds to the lower surface portion of the first muffler 41, and is continuous with the side portion 46 at the lower end of the first muffler 41. The protruding edge 47 has a through hole for inserting a bolt. The bolt is an example of a fastener (in this embodiment, a second fastener for fastening the first muffler 41) used to fix the first muffler 41 relative to the first flange portion 20a. Figure 5 as well as Figure 6In the example shown, the convex edge 47 has five through holes 47a to 47e. Each of these through holes 47a to 47e has one bolt 48a to 48e inserted into it, for a total of five bolts. These through holes 47a to 47e are arranged at approximately equal intervals in the circumferential direction of the opening 45a. Viewed from the axial direction of the rotation axis 15, the five through holes 47a to 47e are arranged such that one is positioned between each of the adjacent plates 45b to 45f in the end face 45. In other words, the five through holes 47a to 47e and the five plates 45b to 45f are respectively arranged to be alternately positioned in the circumferential direction of the opening 45a with approximately the same phase difference. Furthermore, the number of through holes in the convex edge is not limited to five; it can be four or less, or six or more. For example, the number of through holes in the convex edge only needs to be the same as the number of plates in the end face.

[0059] Through holes 47a-47e are each connected to one through hole 20f-20j formed in the first flange portion 20a of the first bearing 20. Figures 3 to 6 In the example shown, the first through hole 47a communicates with the first through hole 20f. Bolts 48a are inserted into these communicating through holes 47a and 20f. Similarly, the second through hole 47b communicates with the second through hole 20g. Bolts 48b are inserted into these communicating through holes 47b and 20g. The third through hole 47c communicates with the third through hole 20h. Bolts 48c are inserted into these communicating through holes 47c and 20h. The fourth through hole 47d communicates with the fourth through hole 20i. Bolts 48d are inserted into these communicating through holes 47d and 20i. The fifth through hole 47e communicates with the fifth through hole 20j. Bolts 48e are inserted into these communicating through holes 47e and 20j. These bolts 48a to 48e are respectively fastened to the first cylinder 13. Thus, the first muffler 41 and the first bearing 20 are assembled into the first cylinder 13. In other words, the protruding edge 47 is fixed to the first cylinder 13 via the first flange 20a of the first bearing 20 and by bolts 48a to 48e. That is, bolts 48a to 48e fix the protruding edge 47 to the first cylinder 13 via the first flange 20a.

[0060] The first muffler 41 has a recess 49 formed by recessing a portion that defines the outer contour of the formed first muffler chamber 43 into the interior of the first muffler chamber 43. Hereinafter, refer to... Figures 4 to 6 The structure of the recess 49 will be explained.

[0061] The recess 49 is formed so that the end surface portion 45 and the side surface portion 46 are recessed toward the inside of the first muffler chamber 43, respectively. When viewed from the first muffler chamber 43, the recess 49 is a protrusion toward the first muffler chamber 43, and corresponds to a rib of the first muffler 41. That is, the recess 49 functions as a reinforcement portion that suppresses deformation of the first muffler 41. In the example shown in FIG. 6, the recess 49 is formed so that the portions between the piece portion 45b and the piece portion 45f in the end surface portion 45 and the portions between the piece portion 45b and the piece portion 45f in the side surface portion 46 that are connected to the protruding edge portion 47 are recessed toward the inside of the first muffler chamber 43, respectively. Figures 4 to 6 In the example shown in FIG. 6, the recess 49 is formed so that the portions between the piece portion 45b and the piece portion 45f in the end surface portion 45 and the portions between the piece portion 45b and the piece portion 45f in the side surface portion 46 that are connected to the protruding edge portion 47 are recessed toward the inside of the first muffler chamber 43, respectively.

[0062] When the recess 49 is projected toward the upper surface 20e of the first flange portion 20a from the axial direction of the rotation shaft 15, the recess 49 is disposed so as to cross the length direction of the cut-in portion 20d and overlap the cut-in portion 20d. That is, the recess 49 is disposed in the vicinity of the cut-in portion 20d, in other words, the discharge valve 21a and the valve presser 21b.

[0063] The recess 49 is configured to include four surface portions 49a to 49d as main surface portions. The first surface portion 49a and the second surface portion 49b are substantially parallel and opposed in pairs in the circumferential direction of the opening 45a. Further, the first surface portion 49a and the second surface portion 49b are parallel to a prescribed plane (imaginary plane) that includes the axial center of the rotation shaft 15 and that crosses the length direction of the discharge valve 21a. In the present embodiment, as an example, the first surface portion 49a and the second surface portion 49b are parallel to a plane that includes the axial center of the rotation shaft 15 and that is orthogonal to the length direction of the discharge valve 21a. In other words, when the recess 49 is projected toward the upper surface 20e of the first flange portion 20a from the axial direction of the rotation shaft 15, the first surface portion 49a and the second surface portion 49b are disposed so as to cross, here be orthogonal to, the length direction of the cut-in portion 20d and overlap the cut-in portion 20d, in other words, the discharge valve 21a and the valve presser 21b.

[0064] The third face 49c and the fourth face 49d are faces that are continuous with each other and connect between the first face 49a and the second face 49b. The first face 49a and the second face 49b are continuous via the third face 49c and the fourth face 49d. The third face 49c stands up in substantially parallel to the center line of the opening 45a (the center axis O1 of the closed container 10) and connects between the first face 49a and the second face 49b in the upper side. The fourth face 49d stands up obliquely with respect to the center line of the opening 45a (the center axis O1 of the closed container 10) and connects between the first face 49a and the second face 49b in the lower side. The fourth face 49d is oblique in a manner that the closer to the center line of the opening 45a (the center axis O1 of the closed container 10) as it goes toward the side (here, the upper side) continuous with the third face 49c. The third face 49c and the fourth face 49d are continuous perpendicularly with respect to the first face 49a and the second face 49b.

[0065] The third face 49c has a through-hole 49e through which the bolt 50 is inserted. The bolt 50 is an example of a fixing member (in this embodiment, a first fixing member that fixes the first muffler 41) for fixing the first muffler 41, specifically, the side face 46, with respect to the first boss portion 20b. As shown in FIG. 6, a contact face portion 20k having a flat contact face capable of abutting against the third face 49c is provided on the first boss portion 20b. The bolt 50 is fastened in a bolt hole 20l formed in the contact face portion 20k. Further, the first face 49a and the second face 49b are opposed at a separation distance that does not interfere with the head 50a of the bolt 50. Figure 5

[0066] Thus, the first muffler 41 is fixed to the first cylinder 13 with respect to the first bearing 20 by the bolts 48a to 48e and via the first flange portion 20a, and is fixed to the first boss portion 20b by the bolt 50. The first flange portion 20a is arranged to extend toward the radial direction outside of the rotary shaft 15, and the first boss portion 20b is arranged concentrically with the rotary shaft 15. That is, the first flange portion 20a and the first boss portion 20b are arranged orthogonally to each other. Thus, the first muffler 41 can be firmly fixed with respect to the first bearing 20 from both the radial direction and the axial direction of the rotary shaft 15. Thereby, for example, the rigidity of the first boss portion 20b against inclination when the first muffler 41 rotates with respect to the rotary shaft 15 can be improved.

[0067] ​Furthermore, the first muffler 41 has a recess 49 disposed near the recess 20d of the first flange 20a. As described above, the recess 49 functions as a reinforcing portion to suppress deformation of the first muffler 41. Therefore, when the rotating shaft 15 rotates, for example, the recess 49 can load the recess 20d with a force that would cause the first boss 20b to tilt relative to the first flange 20a, thus suppressing elastic deformation of the recess 20d and deformation such as tilting of the first boss 20b relative to the first flange 20a. As a result, noise generated due to bending vibration of the rotating shaft 15 can be reduced, for example.

[0068] Furthermore, the second muffler 42 does not have a portion corresponding to the recess 49 present in the first muffler 41. This is due to the following reasons. Figure 2 As shown, the second boss portion 22b of the second bearing 22 is shorter in the axial direction of the rotation shaft 15 than 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, in this embodiment, the second muffler 42 is configured with the portion corresponding to the recess 49 omitted. That is, the second muffler 42 can be configured identically to the first muffler 41, except for the absence of the portion corresponding to the recess 49 and the difference that its upper and lower (top and bottom) positions are opposite. However, the second muffler 42 may also have the same recess as the first muffler 41.

[0069] The various embodiments of the present invention have been described above, but these embodiments are provided as examples and are not intended to limit the scope of the invention. These new embodiments can be implemented in various other ways, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, and are included in the invention described in the claims and its equivalents.

Claims

1. A compressor having: a cylinder that compresses a refrigerant; a rotating shaft having an eccentric portion disposed in 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 extends toward a radially outer side of the boss portion and is continuous in a circular shape concentric with the axis of the rotating shaft over the entire circumference; a discharge valve mechanism disposed in the flange portion and having: a discharge valve that is long in a direction orthogonal to the radial direction of the flange portion 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; and a muffler that covers the bearing in a manner surrounding between the flange portion and the boss portion, forms a muffler chamber for discharging the refrigerant compressed in the cylinder between the flange portion and the boss portion, defines an outer profile of the muffler chamber by a face portion on one end side in the axial direction of the rotating shaft, a flange portion on the other end side in the axial direction of the rotating shaft, and a side face portion that connects between the face portion and the flange portion in a tubular shape over the entire circumference of the rotating shaft, has recesses in which the face portion and the side face portion are respectively recessed toward the inside of the muffler chamber, the flange portion has a cut-in portion that is recessed by recessing the face on the one end side in the axial direction of the rotating shaft for assembling the discharge valve and the valve presser, the recesses are disposed so as to overlap the cut-in portion and cross the length direction of the discharge valve when the recesses are projected toward the flange portion from the axial direction of the rotating shaft, the recesses are composed of a first face portion, a second face portion, a third face portion, and a fourth face portion, the first face portion and the second face portion are parallel to a predetermined imaginary plane that includes the axis of the rotating shaft and crosses the length direction of the discharge valve, the third face portion and the fourth face portion are continuous with each other, the third face portion connects between the first face portion and the second face portion on one side in the axial direction of the rotating shaft, and the fourth face portion connects between the first face portion and the second face portion on the other side in the axial direction of the rotating shaft.

2. The compressor of claim 1, wherein, The third face portion has a through-hole for a first fixing member that fixes the muffler with respect to the boss portion, and the first face portion and the second face portion are opposed at a separation distance that does not interfere with the first fixing member.

3. The compressor of claim 1, wherein, The flange portion has a plurality of through-holes for a second fixing member that fixes the flange portion to the cylinder via the flange portion.

4. An air conditioner having: 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.

Images