Rotary compressor and refrigeration cycle device

Abstract

A fastening member (80) has a head section (80a) and a shaft section (80b) extending from the head section (80a) in a second direction. A base section (71) of a reed valve (70) is formed having a first hole (83) through which the shaft section (80b) of the fastening member (80) is inserted. A valve guard (60) is formed having a second hole (84) through which the shaft section (80b) is inserted. A partition member (90) is formed having a first space (81a) which is located outside a valve chamber (50) and which accommodates the head section (80a).

Description

Rotary Compressor and Refrigeration Cycle Device

[0001] The present disclosure relates to a rotary compressor and a refrigeration cycle device including the same. The rotary compressor is a compressor that compresses the gas in the compression chamber formed in the cylinder by eccentrically rotating a roller in the cylinder. The rotary compressor generally has a vane for partitioning the cylinder chamber into a suction chamber and a compression chamber. The rotary compressor includes a so-called rolling piston type in which a roller rotates eccentrically with a vane separate from the roller in contact with the roller, a so-called swing type in which a vane integrally formed with the roller swings as the roller rotates eccentrically, and a so-called hinge vane type in which the outer peripheral surface of the roller and the tip of the vane are rotatably fitted and the roller rotates eccentrically, etc.

[0002] The rotary compressor disclosed in Patent Document 1 has an injection mechanism for introducing refrigerant into the compressor. The injection mechanism includes a flow path for sending the refrigerant flowing through the injection pipe to the compression chamber, a valve chamber formed in the middle of the flow path, a reed valve disposed in the valve chamber, and a valve retainer for regulating the operation of the reed valve. When the reed valve opens the outlet opening into the valve chamber, the refrigerant in the injection pipe is introduced into the compression chamber.

[0003] Specification of Chinese Patent Application Publication No. 103557158

[0004] In the injection mechanism of Patent Document 1, the valve retainer is fixed to the cylinder by a fastening member. A space for arranging the head of the fastening member is formed in the valve retainer. Since this space is located in the valve chamber, the dead volume that does not contribute to the compression of the refrigerant increases due to this space.

[0005] An object of the present disclosure is to suppress an increase in the dead volume of the valve chamber due to the fastening member.

[0006] The first embodiment relates to a rotary compressor. The rotary compressor comprises a drive shaft (7), a compression mechanism (10), and an injection pipe (39). The compression mechanism (10) includes rollers (12, 22) that are rotationally driven by the drive shaft (7), a partition member (90) that houses the rollers (12, 22) and forms cylinder chambers (15, 25), vanes (13, 23) that divide the cylinder chambers (15, 25) into suction chambers (15a, 25a) and compression chambers (15b, 25b), and suction ports (17, 27) for supplying low-pressure refrigerant to the suction chambers (15a, 25a). The compression mechanism (10) is provided with an injection mechanism (40) for introducing refrigerant into the compression chambers (15b, 25b). The injection mechanism (40) includes a valve chamber (50) formed in a partition member (90), a first flow path (42, 43) that connects the injection pipe (39) and the valve chamber (50) and has an outlet (44) facing the valve chamber (50), and a component disposed in the valve chamber (50) that extends in a first direction, has thickness in a second direction, has a base (71) at one end in the first direction, and opens and closes the outlet (44) at the other end in the first direction. The system includes a reed valve (70) having a tip portion (72), a valve retainer (60) positioned in the valve chamber (50) to restrict the operation of the reed valve (70), a second flow path (45) connecting the valve chamber (50) and the compression chambers (15b, 25b), and a fastening member (80) that fixes the valve retainer (60) and the reed valve (70) with the base portion (71) of the reed valve (70) sandwiched between the partition member (90) and the valve retainer (60). The fastening member (80) has a head portion (80a) and a shaft portion (80b) extending from the head portion (80a) in a second direction. A first hole (83) is formed in the base portion (71) of the reed valve (70) through which the shaft portion (80b) of the fastening member (80) is inserted. A second hole (84) is formed in the valve retainer (60) through which the shaft portion (80b) is inserted. A first space (81a) is formed in the partition member (90) which is located outside the valve chamber (50) and accommodates the head portion (80a).

[0007] In the first embodiment, the shaft portion (80b) of the fastening member (80) passes through the first hole (83) of the reed valve (70) and the second hole (84) of the valve retainer (60), thereby fixing the reed valve (70) and the valve retainer (60) within the valve chamber (50). The head portion (80a) of the fastening member (80) is housed in a first space (81a) outside the valve chamber, so that the increase in dead volume due to the first space (81a) can be suppressed. The shaft portion (80b) passes through the second hole (84) of the valve retainer (60), but the inner diameter of the second hole (84) can be made smaller than the inner diameter of the first space (81a) that houses the head portion (80a). Therefore, compared to a structure in which the first space (81a) is formed in the valve retainer (60), dead volume caused by the fastening member (80) can be reduced.

[0008] In the second embodiment, a threaded portion (80c) is provided on the outer circumferential surface of the shaft portion (80b) in the first embodiment. A threaded groove (84a) corresponding to the threaded portion (80c) is provided on the inner circumferential surface that forms the second hole (84).

[0009] In the second embodiment, the threaded portion (80c) of the fastening member (80) is tightened into the threaded groove (84a) of the second hole (84), thereby fixing the valve retainer (60) and the reed valve (70) within the valve chamber (50).

[0010] In the third embodiment, in the first or second embodiment, a second space (81b) is formed in the partition member (90) through which the shaft portion (80b) is inserted. The first space (81a) is formed in the partition member (90) on the side opposite to the valve chamber (50) with the second space (81b) in between.

[0011] In the third embodiment, the shaft portion (80b) of the fastening member (80) passes through the second space (81b), the first hole (83), and the second hole (84).

[0012] The fourth embodiment is such that, in any one of the first to third embodiments, a portion of the head (80a) is located outside the inner circumferential surface (CS1) that forms the valve chamber (50) when viewed from a second direction.

[0013] In the fourth embodiment, a portion of the head (80a) is located outside the inner circumferential surface (CS1) that forms the valve chamber (50) in the second view, but the head (80a) is positioned in the first space (81a) outside the valve chamber (50). Therefore, the influence of the head (80a) can suppress the enlargement of the valve chamber (50) in the second view, thereby reducing dead volume.

[0014] A fifth aspect is that, in the fourth aspect, the diameter of the head (80a) is greater than the width in the third direction perpendicular to the first and second directions in the valve chamber (50).

[0015] In the fifth embodiment, the diameter of the head (80a) is greater than the width of the valve chamber (50) in the third direction, but the head (80a) is positioned in the first space (81a) outside the valve chamber (50). Therefore, the influence of the head (80a) can suppress the enlargement of the valve chamber (50) in the second view, thereby reducing dead volume.

[0016] In the sixth embodiment, in the fourth or fifth embodiment, a portion of the head (80a) is located outside the end on one side in the first direction of the valve chamber (50) in the second view.

[0017] In the sixth embodiment, the first hole (83) and further the base (71) of the reed valve (70) can be brought closer to one end of the valve chamber (50). As a result, the distance from the base (71) to the tip (72) of the reed valve (70) can be increased, and the stress acting on the base (71) when the reed valve (70) is in the open state can be reduced.

[0018] The seventh embodiment is one of the first to sixth embodiments in which the first distance (L1) from the axis (C1) of the shaft portion (80b) to the other end in the first direction of the base portion (71) of the reed valve (70) is greater than the second distance (L2) from the axis (C1) of the shaft portion (80b) to the one end in the first direction of the base portion (71) of the reed valve (70).

[0019] In the seventh embodiment, the distance from the first hole (83) to the tip end (72) of the base (71) of the reed valve (70) is increased. This suppresses the concentration of stress acting on the base (71) when the reed valve (70) is in the open state.

[0020] The eighth aspect is that, in any one of the first to seventh aspects, the rotary compressor compresses a carbon dioxide refrigerant.

[0021] In the eighth embodiment, the refrigerant pressure in the valve chamber (50) becomes relatively high, and the effect of the decrease in compression efficiency due to dead volume becomes greater. In contrast, in this embodiment, the dead volume caused by the fastening member (80) can be reduced, so the decrease in compression efficiency can be effectively suppressed.

[0022] The ninth embodiment relates to a refrigeration cycle device. The refrigeration cycle device comprises a refrigerant circuit (101) having a rotary compressor (1) according to any one of the first to eighth embodiments.

[0023] Figure 1 is a piping diagram showing the configuration of a refrigeration cycle device according to an embodiment. Figure 2 is a longitudinal cross-sectional view of the compressor according to an embodiment. Figure 3 is an enlarged view of the compression mechanism in Figure 2. Figure 4 is a cross-sectional view of the compression mechanism in Figure 3 along line IV-IV. In Figure 4, the rotation angle of the first roller is 90°. Figure 5 is a cross-sectional view of the compression mechanism in Figure 3 along line VV. In Figure 5, the rotation angle of the second roller is 270°. Figure 6 is an enlarged longitudinal cross-sectional view of the main part of the injection mechanism. Figure 7 is a plan view of the cylinder and injection element in an axial view. Figure 8 is an exploded perspective view of the main part of the injection element. Figure 9 is a plan view of the valve retainer, reed valve, and the valve retainer in a second direction view. Figure 10 is a cross-sectional view of the injection element in a third direction view. In Figure 10, the reed valve is in the closed state. Figure 11 is a cross-sectional view of the injection element in a third direction view. In Figure 11, the reed valve is in the open state. Figure 12 is a second-direction plan view showing the valve chamber, reed valve, and head of the fastening member.

[0024] The embodiments will now be described. The compressor (1) of this embodiment is applied to an air conditioner (100). The air conditioner (100) is an example of a refrigeration cycle device that performs a vapor compression refrigeration cycle.

[0025] -Air Conditioner- As shown in Figure 1, the air conditioner (100) is equipped with a refrigerant circuit (101). The refrigerant circuit (101) includes a compressor (1), an outdoor heat exchanger (102), an expansion valve (103), an indoor heat exchanger (104), a four-way switching valve (105), an accumulator (106), an internal heat exchanger (107), an intermediate flow path (108), and a control valve (109). The expansion valve (103) is an example of a pressure reducing mechanism. The pressure reducing mechanism may be a capillary tube.

[0026] The internal heat exchanger (107) exchanges heat between the refrigerant that has passed through the outdoor heat exchanger (102) and the refrigerant that has passed through the control valve (109) in the intermediate flow path (108). The inlet end of the intermediate flow path (108) is connected between the internal heat exchanger (107) and the expansion valve (103). The outlet end of the intermediate flow path (108) is in communication with the compression chamber of the compressor (1).

[0027] The four-way directional control valve (105) switches between a first state, shown by the solid line in Figure 1, and a second state, shown by the dashed line in Figure 1, thereby switching between cooling and heating operation of the air conditioner (100). In the first state, the four-way directional control valve (105) connects the discharge side of the compressor (1) to the outdoor heat exchanger (102) and simultaneously connects the suction side of the compressor (1) to the indoor heat exchanger (104) during cooling operation. In the second state, the four-way directional control valve (105) connects the discharge side of the compressor (1) to the indoor heat exchanger (104) and connects the suction side of the compressor (1) to the outdoor heat exchanger (102) during heating operation.

[0028] <Air Conditioner Operation> The air conditioner (100) performs both cooling and heating operations. In cooling operation, the four-way switching valve (105) is set to the first state, and the refrigerant circulates in the refrigerant circuit (101). In the refrigerant circuit (101), the outdoor heat exchanger (102) functions as a radiator, and the indoor heat exchanger (104) functions as an evaporator. The air cooled by the indoor heat exchanger (104) is supplied to the indoor space.

[0029] During heating operation, the four-way switching valve (105) is set to the second state, and the refrigerant circulates in the refrigerant circuit (101). In the refrigerant circuit (101), the indoor heat exchanger (104) functions as a radiator, and the outdoor heat exchanger (102) functions as an evaporator. The air heated by the indoor heat exchanger (104) is supplied to the indoor space.

[0030] During cooling operation, the refrigerant diverted to the intermediate flow path (108) is reduced to an intermediate pressure by the control valve (109). After passing through the control valve (109), the refrigerant passes through the internal heat exchanger (107) and is then introduced into the compression chamber of the compressor (1).

[0031] - Compressor Configuration - The details of the compressor (1) are described below. In the following description, "axial direction" means the direction in which the axis of the drive shaft (7) extends, "radial direction" means the direction perpendicular to the axial direction and extending radially from the axis of the drive shaft (7), and "rotational direction" means the direction in which the drive shaft (7) rotates.

[0032] The compressor (1) is a rotary compressor. The compressor (1) in this embodiment is a so-called swing-type rotary compressor in which vanes formed integrally with the rollers oscillate in accordance with the eccentric rotation of the rollers.

[0033] As shown in Figures 2 and 3, the compressor (1) includes a casing (2), a drive shaft (7), and a compression mechanism (10). The motor (3), the drive shaft (7), and the compression mechanism (10) are housed within the casing (2). The compression mechanism (10) is positioned below the motor (3).

[0034] <Casing> As shown in Figure 2, the casing (2) is a vertically elongated cylindrical sealed container. The casing (2) has a cylindrical body (2a), a top (2b) that closes the upper end of the body (2a), and a bottom (2c) that closes the lower end of the body (2a). An oil reservoir space (S0) is formed in the lower part of the casing (2). The oil reservoir space (S0) is formed between the bottom (2c) and the lower part of the body (2a). Oil (refrigerant oil) for lubricating the sliding parts of the compressor (1) is stored in the oil reservoir space (S0).

[0035] The compressor (1) is a so-called high-pressure dome type. In other words, the internal space of the casing (2) is filled with discharged refrigerant discharged from the compression mechanism (10). The internal space of the casing (2) includes a primary space (S1) between the compression mechanism (10) and the motor (3), and a secondary space (S2) above the motor (3).

[0036] <Motor> The motor (3) rotates the drive shaft (7). The motor (3) is located in the upper part of the internal space of the casing (2). The motor (3) has a stator (3a) and a rotor (3b) located inside the stator (3a). The stator (3a) is fixed to the inner circumferential surface of the body (2a) of the casing (2) by shrink fitting or welding. The rotor (3b) is attached to the drive shaft (7). The compressor (1) is a so-called inverter compressor. The motor (3) is configured to have a variable operating frequency (rotational speed).

[0037] A stator groove (3c) (so-called core cut) is formed on the outer circumferential surface of the stator (3a) from one end to the other in the axial direction. The primary space (S1) and the secondary space (S2) communicate with each other through the stator groove (3c) and the gap between the stator (3a) and the rotor (3b). The stator groove (3c) functions as a passage for returning oil in the secondary space (S2) to the oil reservoir space (S0).

[0038] <Drive Shaft> The drive shaft (7) connects the motor (3) and the compression mechanism (10). The drive shaft (7) rotates around its axis (C). The drive shaft (7) has, in order from its upper end to its lower end, a main shaft portion (7a), a first eccentric portion (7b), an intermediate shaft portion (7c), a second eccentric portion (7d), and a sub-shaft portion (7e). The main shaft portion (7a), the first eccentric portion (7b), the intermediate shaft portion (7c), the second eccentric portion (7d), and the sub-shaft portion (7e) are formed integrally.

[0039] The first eccentric portion (7b) and the second eccentric portion (7d) are each eccentric with respect to the axis (C). The direction of eccentricity of the first eccentric portion (7b) with respect to the axis (C) in the first eccentric portion (7b) and the direction of eccentricity of the second eccentric portion (7d) with respect to the axis (C) in the second eccentric portion (7d) are offset by 180° in the rotational direction of the drive shaft (7).

[0040] An oil supply mechanism (8) is provided on the drive shaft (7). The oil supply mechanism (8) has an internal shaft passage (8a) formed inside the drive shaft (7) and a pump (8b) provided at the lower end of the drive shaft (7). The inlet end of the internal shaft passage (8a) is connected to the pump (8b). The pump (8b) pumps oil from the oil reservoir space (S0) and supplies it to the sliding parts of the compression mechanism (10) through the internal shaft passage (8a). The pump (8b) is a centrifugal pump. The pump (8b) may also be a positive displacement pump.

[0041] <Discharge pipe and suction pipe> The compressor (1) has a discharge pipe (4), a first suction pipe (5), and a second suction pipe (6). The discharge pipe (4) is attached to the top (2b). The discharge pipe (4) passes through the top (2b). The first suction pipe (5) and the second suction pipe (6) are attached to the lower part of the body (2a). The first suction pipe (5) and the second suction pipe (6) pass through the body (2a). The first suction pipe (5) is located above the second suction pipe (6).

[0042] An accumulator (106) is connected to the first suction tube (5) and the second suction tube (6). The accumulator (106) is a cylindrical sealed container. The accumulator (106) separates the incoming refrigerant into gaseous refrigerant and liquid refrigerant.

[0043] -Compression mechanism configuration- The compression mechanism (10) compresses the refrigerant drawn in through the first suction pipe (5) and the second suction pipe (6), and discharges the compressed refrigerant into the space inside the casing (2).

[0044] The compression mechanism (10) includes a first bearing (30), a first cylinder (11), an intermediate plate (34), a second cylinder (21), and a second bearing (35). In the compression mechanism (10), the first bearing (30), the first cylinder (11), the intermediate plate (34), the second cylinder (21), and the second bearing (35) are arranged in order from top to bottom.

[0045] As shown in FIGS. 2 to 5, the compression mechanism (10) is a two-cylinder type having a first cylinder (11) and a second cylinder (21). The compression mechanism (10) is a two-cylinder single-stage compression type that compresses low-pressure refrigerant inside the first cylinder (11) and the second cylinder (21), respectively. In the space inside the first cylinder (11), a first roller (12), a first vane (13), and a pair of first bushes (14) are arranged. In the space inside the second cylinder (21), a second roller (22), a second vane (23), and a pair of second bushes (24) are arranged. The number of cylinders, rollers, vanes, and a pair of bushes is merely an example and is not limited to two.

[0046] The compression mechanism (10) is directly or indirectly fixed to the body portion (2a) of the casing (2). In this embodiment, the first bearing (30) is directly fixed to the body portion (2a) of the casing (2) by welding. The first cylinder (11), the intermediate plate (34), the second cylinder (21), and the second bearing (35) are fixed to the first bearing (30) by bolts (not shown). The first bearing (30) may be indirectly welded to the body portion (2a) of the casing (2) via another member fixed to the first bearing (30).

[0047] 〈Cylinder〉 Each of the first cylinder (11) and the second cylinder (21) is an annular member. As shown in FIG. 4, a first circular hole (11a), a first vane accommodation hole (16), and a first suction port (17) are formed in the first cylinder (11). As shown in FIG. 5, a second circular hole (21a), a second vane accommodation hole (26), and a second suction port (27) are formed in the second cylinder (21).

[0048] The first circular hole (11a) is formed so as to penetrate the first cylinder (11) in the axial direction. The first circular hole (11a) is defined by the inner peripheral surface of the first cylinder (11). The first roller (12) is accommodated in the first circular hole (11a). The first cylinder chamber (15) is defined by the inner peripheral surface of the first cylinder (11), the outer peripheral surface of the first roller (12), the side surface of the first vane (13), the first bearing (30), and the intermediate plate (34).

[0049] The second circular hole (21a) is formed so as to penetrate the second cylinder (21) in the axial direction. The second circular hole (21a) is defined by the inner peripheral surface of the second cylinder (21). The second roller (22) is accommodated in the second circular hole (21a). The second cylinder chamber (25) is defined by the inner peripheral surface of the second cylinder (21), the outer peripheral surface of the second roller (22), the side surface of the second vane (23), the second bearing (35), and the intermediate plate (34).

[0050] The first vane accommodation hole (16) extends from the first circular hole (11a) of the first cylinder (11) toward the outside in the radial direction of the first cylinder (11). The first vane accommodation hole (16) penetrates the first cylinder (11) in the axial direction. The first vane (13) is accommodated in the first vane accommodation hole (16). The first vane accommodation hole (16) includes a first bush hole (16a) into which a pair of first bushes (14) are fitted.

[0051] The second vane accommodation hole (26) extends from the second circular hole (21a) of the second cylinder (21) toward the outside in the radial direction of the second cylinder (21). The second vane accommodation hole (26) penetrates the second cylinder (21) in the axial direction. The second vane (23) is accommodated in the second vane accommodation hole (26). The second vane accommodation hole (26) includes a second bush hole (26a) into which a pair of second bushes (24) are fitted.

[0052] The first inhalation port (17) is located near the first vane housing hole (16). The first inhalation port (17) penetrates the first cylinder (11) radially. The first inhalation port (17) communicates with the first cylinder chamber (15). The first inhalation tube (5) is connected to the first inhalation port (17). The second inhalation port (27) is located near the second vane housing hole (26). The second inhalation port (27) penetrates the second cylinder (21) radially. The second inhalation port (27) communicates with the second cylinder chamber (25). The second inhalation tube (6) is connected to the second inhalation port (27).

[0053] <First Bearing> The first bearing (30) is positioned above the first cylinder (11). The first bearing (30) has a cylindrical first boss portion (30a) and a first flange portion (30b) that extends radially outward from the first boss portion (30a). The first boss portion (30a) and the first flange portion (30b) are formed integrally. The first bearing (30) constitutes a closing member that axially closes the first cylinder chamber (15).

[0054] The first bearing (30) has a through hole that penetrates the first boss portion (30a) in the axial direction. The main shaft portion (7a) is inserted through the through hole. The inner circumferential surface of the first bearing (30) that forms the through hole constitutes the first sliding surface (30c) that the drive shaft (7) contacts.

[0055] As shown in Figure 4, a first discharge port (31) is formed in the first flange portion (30b). The first discharge port (31) penetrates the first flange portion (30b) in the thickness direction. In an axial view, the first discharge port (31) is located on the opposite side of the first suction port (17) from the first vane housing hole (16).

[0056] A first discharge valve (32) for opening and closing the first discharge port (31) is provided in the first flange portion (30b). The first discharge valve (32) is composed of a reed valve. The first discharge valve (32) opens and closes periodically in accordance with the pressure in the first compression chamber (15b), which will be described later.

[0057] As shown in Figure 2, the compression mechanism (10) is provided with a first muffler (33). A first muffler space (MS1) is formed between the first muffler (33) and the first bearing (30). The first muffler space (MS1) communicates with the first discharge port (31). The first muffler (33) has a first muffler opening (33a) that connects the first muffler space (MS1) with the space outside the first muffler (33) (primary space (S1)).

[0058] <Second Bearing> The second bearing (35) is positioned below the second cylinder (21). The second bearing (35) has a cylindrical second boss portion (35a) and a second flange portion (35b) that extends radially outward from the second boss portion (35a). The second boss portion (35a) and the second flange portion (35b) are formed integrally. The second bearing (35) constitutes a closing member that axially closes the second cylinder chamber (25).

[0059] The second bearing (35) has a through hole that penetrates the second boss portion (35a) in the axial direction. The sub-shaft portion (7e) is inserted through the through hole. The inner circumferential surface of the second bearing (35) that forms the through hole constitutes the second sliding surface (35c) that the drive shaft (7) contacts.

[0060] As shown in Figure 5, a second discharge port (36) is formed in the second flange portion (35b). The second discharge port (36) penetrates the second flange portion (35b) in the thickness direction. In an axial view, the second discharge port (36) is located on the opposite side of the second vane housing hole (26) from the second suction port (27).

[0061] A second discharge valve (37) is provided in the second flange portion (35b) for opening and closing the second discharge port (36). The second discharge valve (37) is composed of a reed valve. The second discharge valve (37) opens and closes periodically in accordance with the pressure in the second compression chamber (25b), which will be described later.

[0062] As shown in Figure 2, the compression mechanism (10) is provided with a second muffler (38). A second muffler space (MS2) is formed between the second muffler (38) and the second bearing (35). The second muffler space (MS2) communicates with the second discharge port (36). The second muffler space (MS2) communicates with the first muffler space (MS1) through an internal flow path formed in the compression mechanism (10).

[0063] <Intermediate Plate> The intermediate plate (34) is positioned between the first cylinder (11) and the second cylinder (21). The intermediate plate (34) covers the other end (lower end) of the first cylinder chamber (15) and the other end (upper end) of the second cylinder chamber (25). The intermediate plate (34) constitutes a closing member that axially closes the first cylinder chamber (15) and the second cylinder chamber (25).

[0064] A circular hole is formed in the center of the intermediate plate (34), passing through it axially. The drive shaft (7) is inserted through the circular hole in the intermediate plate (34).

[0065] <Rollers> The first roller (12) and the second roller (22) are each annular members. The first eccentric portion (7b) of the drive shaft (7) is inserted through the inner space of the first roller (12). The first roller (12) rotates eccentrically when driven by the drive shaft (7). The outer surface of the first roller (12) and the inner surface of the first cylinder (11) are in contact. The second eccentric portion (7d) of the drive shaft (7) is inserted through the inner space of the second roller (22). The second roller (22) rotates eccentrically when driven by the drive shaft (7). The outer surface of the second roller (22) and the inner surface of the second cylinder (21) are in contact.

[0066] When each roller (12,22) rotates eccentrically, the rotation angle of each roller (12,22) changes. In an axial view, the rotation angle when each roller (12,22) is closest to each vane housing hole (16,26) is defined as the reference angle (rotation angle = 0°).

[0067] <Vanes> The first vane (13) and the second vane (23) are plate-shaped members. The first vane (13) is formed integrally with the first roller (12). The first vane (13) extends radially outward from the outer circumferential surface of the first roller (12) toward the first cylinder (11). The second vane (23) is formed integrally with the second roller (22). The second vane (23) extends radially outward from the outer circumferential surface of the second roller (22) toward the second cylinder (21).

[0068] The first vane (13) fits into the first vane housing hole (16) of the first cylinder (11). The first vane (13) divides the first cylinder chamber (15) into a first compression chamber (15b) and a first intake chamber (15a). In an axial view, the first intake chamber (15a) is formed on the side of the first intake port (17), and the first compression chamber (15b) is formed on the side of the first discharge port (31).

[0069] The second vane (23) fits into the second vane housing hole (26) of the second cylinder (21). The second vane (23) divides the second cylinder chamber (25) into a second intake chamber (25a) and a second compression chamber (25b). In an axial view, the second intake chamber (25a) is formed on the side of the second intake port (27), and the second compression chamber (25b) is formed on the side of the second discharge port (36).

[0070] <Bushings> The pair of first bushings (14) and the pair of second bushings (24) are approximately semi-cylindrical members. The flat surfaces of the pair of first bushings (14) are arranged to face each other. The flat surfaces of the pair of second bushings (24) are arranged to face each other.

[0071] The pair of first bushes (14) are fitted into the first bush hole (16a) with the first vane (13) in between. The first vane (13) oscillates back and forth together with the first bush (14). At the same time, the first vane (13) moves back and forth along the flat surface of the pair of first bushes (14).

[0072] The pair of second bushes (24) fit into the second bush hole (26a) with the second vane (23) in between. The second vane (23) oscillates back and forth together with the second bush (24). At the same time, the second vane (23) moves back and forth along the flat surface of the pair of second bushes (24).

[0073] - Compressor Operation - When the motor (3) is energized, the motor (3) drives the drive shaft (7). The drive shaft (7) rotates in the direction indicated by the arrow R in Figures 4 and 5. As the drive shaft (7) rotates, the first roller (12) rotates eccentrically along the inner surface of the first cylinder (11), and at the same time, the second roller (22) rotates eccentrically along the inner surface of the second cylinder (21).

[0074] The gaseous refrigerant that has passed through the first suction pipe (5) is drawn into the first suction chamber (15a) from the first suction port (17). When the first roller (12) rotates eccentrically and the first suction chamber (15a) is blocked from the first suction port (17), a first compression chamber (15b) is formed. As the first roller (12) rotates further eccentrically, the refrigerant is compressed in the first compression chamber (15b).

[0075] The gaseous refrigerant that has passed through the second suction pipe (6) is drawn into the second suction chamber (25a) from the second suction port (27). When the second roller (22) rotates eccentrically and the second suction chamber (25a) is blocked from the second suction port (27), a second compression chamber (25b) is formed. As the second roller (22) rotates further eccentrically, the refrigerant is compressed in the second compression chamber (25b).

[0076] The refrigerant compressed in the first compression chamber (15b) is discharged from the first discharge port (31) into the first muffler space (MS1). The refrigerant compressed in the second compression chamber (25b) is discharged from the second discharge port (36) into the second muffler space (MS2). The refrigerant in the second muffler space (MS2) passes through an internal flow path and flows into the first muffler space (MS1). The refrigerant in the first muffler space (MS1) flows out into the primary space (S1), passes through the motor (3), and then flows into the secondary space (S2). The refrigerant in the secondary space (S2) is discharged to the outside of the casing (2) through the discharge pipe (4).

[0077] -Injection Tube- As shown in Figure 6, the compressor (1) has an injection tube (39). The injection tube (39) is attached to the lower part of the body (2a). The injection tube (39) penetrates the body (2a) radially. The outlet end of the injection tube (39) is connected to the compression mechanism (10). In this example, the injection tube (39) is connected to the second flange portion (35b) of the second bearing (35). The inlet end of the injection tube (39) is connected to the intermediate flow path (108) of the refrigerant circuit (101) shown in Figure 1. The outlet end of the injection tube (39) is connected to the injection flow path (41) formed in the compression mechanism (10).

[0078] -Injection Mechanism- As shown in Figure 6, the compressor (1) is equipped with an injection mechanism (40) for introducing refrigerant at an intermediate pressure into the compression chambers (15b, 25b). The refrigerant circuit (101) is filled with carbon dioxide as the refrigerant. In the refrigerant circuit (101), a refrigeration cycle (so-called supercritical cycle) is performed in which the high pressure is equal to or greater than the critical pressure. The intermediate pressure corresponds to the pressure between the low pressure and high pressure of the refrigerant circuit (101). The refrigerant at the intermediate pressure is a gas-liquid two-phase refrigerant. The refrigerant at the intermediate pressure may also be a liquid refrigerant or a gaseous refrigerant. In other words, the intermediate pressure corresponds to the pressure between the suction pressure and discharge pressure of the compressor (1). The injection mechanism (40) is provided in the compression mechanism (10).

[0079] The injection mechanism (40) of this embodiment includes a first injection element (I1) and a second injection element (I2). The first injection element (I1) introduces refrigerant at an intermediate pressure into the first compression chamber (15b) of the first cylinder chamber (15). The second injection element (I2) introduces refrigerant at an intermediate pressure into the second compression chamber (25b) of the second cylinder chamber (25). The first injection element (I1) has a first valve chamber (50A), a first reed valve (70A), a first valve retainer (60A), a first branch passage (43A), and a first introduction passage (45A). The second injection element (I2) includes a second valve chamber (50B), a second reed valve (70B), a second valve retainer (60B), a second branch passage (43B), and a second introduction passage (45B).

[0080] <Injection Flow Channel> The injection flow channel (41) is a flow channel for sending the refrigerant at intermediate pressure in the injection pipe (39) to the compression chambers (15b, 25b). As shown in Figure 6, the injection flow channel (41) in this embodiment branches into two and communicates with both the first compression chamber (15b) and the second compression chamber (25b). The injection flow channel (41) includes a main flow channel (42), a first branch flow channel (43A), a second branch flow channel (43B), a first valve chamber (50A), a second valve chamber (50B), a first inlet passage (45A), and a second inlet passage (45B). The inlet end of the main flow channel (42) is connected to the injection pipe (39). The first branch flow channel (43A) connects the main flow channel (42) and the first valve chamber (50A). The second branch passage (43B) connects the main passage (42) and the second valve chamber (50B). The first inlet passage (45A) connects the first valve chamber (50A) and the first compression chamber (15b). The second inlet passage (45B) connects the second valve chamber (50B) and the second compression chamber (25b). In this embodiment, the main passage (42), the first branch passage (43A), and the second branch passage (43B) constitute the first passage, and the first inlet passage (45A) and the second inlet passage (45B) constitute the second passage.

[0081] The main passage (42) is formed in the second bearing (35). The main passage (42) extends from the injection pipe (39) toward the drive shaft (7) and further extends axially across the second bearing (35) and the second cylinder (21). The first branch passage (43A) extends axially from the outlet end of the main passage (42) toward the second cylinder (21), the intermediate plate (34), and the first cylinder (11). Furthermore, the first branch passage (43A) extends toward the drive shaft (7) in the first cylinder (11) and then axially to the first valve chamber (50A). The second branch passage (43B) extends toward the drive shaft (7) in the second cylinder (21) and then axially to the second valve chamber (50B).

[0082] The first valve chamber (50A) is formed in the first cylinder (11). Specifically, the first valve chamber (50A) is formed in a concave groove formed on the end face on the intermediate plate (34) side (lower side) in the axial direction. The first valve chamber (50A) houses the first valve retainer (60A) and the first reed valve (70A). The second valve chamber (50B) is formed in the second cylinder (21). Specifically, the second valve chamber (50B) is formed in a concave groove formed on the end face on the intermediate plate (34) side (upper side) in the axial direction. The second valve chamber (50B) houses the second valve retainer (60B) and the second reed valve (70B).

[0083] The first intake passage (45A) extends from the first valve chamber (50A) toward the inner surface of the first cylinder (11). The outlet end of the first intake passage (45A) opens toward the first cylinder chamber (15). The second intake passage (45B) extends from the second valve chamber (50B) toward the inner surface of the second cylinder (21). The outlet end of the second intake passage (45B) opens toward the second cylinder chamber (25).

[0084] -Details of Injection Elements- Details of the injection elements (I1, I2) will be explained with reference to Figures 6 to 11. The first injection element (I1) and the second injection element (I2) have the same basic configuration. Therefore, in the following explanation, the first valve chamber (50A) and the second valve chamber (50B) may be referred to as the valve chamber (50), the first valve retainer (60A) and the second valve retainer (60B) as the valve retainer (60), the first reed valve (70A) and the second reed valve (70B) as the reed valve (70), the first branch passage (43A) and the second branch passage (43B) as the branch passage (43), and the first introduction passage (45A) and the second introduction passage (45B) as the introduction passage (45).

[0085] In the following description, the first direction is the longitudinal direction of the valve retainer (60), the second direction is the thickness direction of the valve retainer (60), and the third direction is perpendicular to the first and second directions. The first direction corresponds to the longitudinal direction of the reed valve (70). The second direction corresponds to the thickness direction of the reed valve (70). The third direction corresponds to the width direction of the valve retainer (60). One end in the first direction corresponds to the side of the valve retainer (60) to which the reed valve (70) is fixed in the first direction. The other end in the first direction corresponds to the side of the valve retainer (60) to which the tip (72) of the open reed valve (70) makes contact in the first direction.

[0086] <Valve Chamber> The valve chamber (50) is formed in the cylinder (11, 21). As shown in Figure 7, the valve chamber (50) is located in an axial view on the opposite side of the suction port (17, 27) from the vane housing holes (16, 26). The valve chamber (50) is located near the discharge port (31, 36). The valve chamber (50) houses the valve retainer (60) and the reed valve (70). The valve chamber (50) extends in a first direction toward the cylinder chamber (15, 25). As shown in Figures 7 to 9, the valve chamber (50) in this embodiment is formed in an oval shape in a second view. The valve chamber (50) in this embodiment is defined by an inner surface that forms a concave groove and an intermediate plate (34) that closes the opening of the concave groove. The inner surface that forms the valve chamber (50) includes a third surface, which is the bottom surface (51), and a second surface, which is the closing surface (52). The bottom surface (51) is the surface formed at the bottom of the concave groove. The closing surface (52) is the surface of the intermediate plate (34) that faces the inside of the concave groove and is opposite the bottom surface (51) in the second direction.

[0087] The inner surface forming the valve chamber (50) includes an inner circumferential surface (CS1) that extends from the bottom surface (51) to the closing surface (52). In this embodiment, the inner circumferential surface (CS1) is formed in an oval shape with the first direction as the longitudinal direction when viewed from a second direction. The inner circumferential surface (CS1) includes a first inner surface (53), a second inner surface (54), a first inner end surface (55), and a second inner end surface (56). The first inner surface (53) and the second inner surface (54) face each other in a third direction. The first inner surface (53) and the second inner surface (54) are formed in a planar shape extending in the first direction. In other words, the first inner surface (53) and the second inner surface (54) are formed in a linear shape parallel to each other when viewed from a second direction. The first inner end surface (55) is formed at one end of the valve chamber (50) in the first direction. The second inner end surface (56) is formed at the other end of the valve chamber (50) in the first direction. The first inner end surface (55) and the second inner end surface (56) are formed in an arc shape that widens outward when viewed in the second direction.

[0088] The entirety of the first inner surface (53) and the second inner surface (54) are smoothly continuous in a second viewing direction. "Smoothly continuous" means continuous without any steps or tangential continuity. In this embodiment, the entire inner surface of the valve chamber (50) is smoothly continuous.

[0089] A groove (51a) is formed on the bottom surface (51) of the valve chamber (50) in this embodiment. As shown in Figure 9, the groove (51a) is formed in the valve chamber (50) from the middle part in the first direction to the other end. The groove (51a) is formed on the bottom surface (51) such that the support surface (51b) and the valve seat surface (51c) remain.

[0090] The support surface (51b) is located near one end in the first direction of the valve chamber (50). The support surface (51b) supports the base (71) of the reed valve (70). The valve seat surface (51c) is located near the other end in the first direction of the valve chamber (50). The valve seat surface (51c) is formed around the outlet (44) of the branched flow path (43). The outlet (44) is formed in a circular shape in a second view. The valve seat surface (51c) is formed in an annular shape surrounding the outlet (44) in a second view. The support surface (51b) and the valve seat surface (51c) are formed on the same plane. The support surface (51b) and the valve seat surface (51c) are closer to the closure surface (52) than to the bottom surface of the groove (51a).

[0091] As shown in Figures 10 and 11, a stepped portion (57) is formed at the other end of the bottom surface (51) in the first direction. The stepped portion (57) protrudes in a second direction from the bottom surface of the groove (51a) toward the closing surface (52). The convex surface (57a) on one end of the stepped portion (57) in the second direction (the side toward the closing surface (52)) is closer to the closing surface (52) than the support surface (51b) or the valve seat surface (51c). The convex surface (57a) is formed in a fan shape or crescent shape when viewed in the second direction.

[0092] <Valve Retainer> The valve retainer (60) shown in Figures 8 to 12 is positioned in the valve chamber (50) and extends in the first direction. The valve retainer (60) restricts the operation of the reed valve (70). In a second view, the valve retainer (60) fits into the valve chamber (50). Here, "fitting" means that the valve retainer (60) fits into the valve chamber (50) substantially without gaps, or with a small gap in between. Here, the "gap" is 1 mm or less, preferably 0.1 mm or less.

[0093] The valve retainer (60) is formed in a shape similar to the inner surface of the valve chamber (50) when viewed from a second direction. The valve retainer (60) is formed in an oval shape extending in the first direction when viewed from a second direction. Specifically, the valve retainer (60) has a side surface (CS2) corresponding to the inner surface (CS1). The side surface (CS2) includes a first side surface (61), a second side surface (62), a first side end surface (63), and a second side end surface (64). The first side surface (61) is formed in a planar shape along the first inner surface (53). The second side surface (62) is formed in a planar shape along the second inner surface (54). The first side end surface (63) is formed in a curved shape along the first inner end surface (55). The second side end surface (64) is formed in a curved shape along the second inner end surface (56).

[0094] The entirety of the first side surface (61) and the second side surface (62) are smoothly continuous in a second viewing direction. In this embodiment, the entire circumferential surface of the valve retainer (60) is smoothly continuous.

[0095] The valve retainer (60) has a valve side surface (65) on the reed valve (70) side in the second direction. The valve retainer (60) has a first surface, which is the back surface (66), on the side opposite to the reed valve (70) in the second direction.

[0096] The valve retainer (60) has a fixed portion (67) and a contact portion (68). The fixed portion (67) is formed at one end of the valve retainer (60) in the first direction. The contact portion (68) is formed extending from the middle portion to the other end of the valve retainer (60) in the first direction. In a view from the second direction, the fixed portion (67) overlaps with the base (71) and support surface (51b) of the reed valve (70). The contact portion (68) extends in the first direction so as to span the tip (72) and neck (73) of the reed valve (70).

[0097] The valve retainer (60) is formed in a boat shape when viewed from a third direction. The contact portion (68) of the valve retainer (60) has a gradually increasing thickness in the second direction as it moves from the other end in the first direction towards the one end. The fixing portion (67) of the valve retainer (60) has a roughly equal thickness in the second direction. The thickness of the fixing portion (67) in the second direction is greater than the thickness of the contact portion (68) in the second direction.

[0098] <Reed Valve> The reed valve (70) shown in Figures 7 to 11 is positioned between the valve retainer (60) and the bottom surface (51) of the valve chamber (50). The reed valve (70) is formed in a plate shape having thickness in a second direction. The reed valve (70) is made of an elastic metal material. The reed valve (70) extends in a first direction along the valve retainer (60). The reed valve (70) has a base (71) located at one end in the first direction, a tip (72) located at the other end in the first direction, and a neck (73) connecting the base (71) and the tip (72).

[0099] The base (71) is sandwiched between the support surface (51b) and the fixing portion (67) of the valve retainer (60). In other words, the base (71) is fixed within the valve chamber (50). The sides of the base (71) in the third direction and the end face on one end in the first direction engage with the valve chamber (50) in a view from the second direction. The base (71) is sandwiched between the valve side surface (65) of the fixing portion (67) of the valve retainer (60) and the support surface (51b).

[0100] The tip portion (72) constitutes the valve body of the reed valve (70). In a second view, the tip portion (72) overlaps with the valve seat surface (51c). In a second view, the tip portion (72) is formed in a circular shape with a diameter larger than that of the outlet (44). The width of the tip portion (72) in the third direction is smaller than the width of the base portion (71) in the third direction. The length of the tip portion (72) in the first direction is smaller than the length of the base portion (71) in the first direction.

[0101] The neck portion (73) forms a constricted portion. The neck portion (73) extends in a first direction from the base portion (71) to the tip portion (72). The neck portion (73) changes angle between the bottom surface (51) that forms the valve chamber (50) and the valve side surface (65) of the valve retainer (60), with the end on the base portion (71) side as a pivot point. In a second view, the neck portion (73) coincides with the groove (51a). In a second view, the groove (51a) surrounds the entire circumference of the neck portion (73).

[0102] The reed valve (70) deforms between the closed state shown in Figure 10 and the open state shown in Figure 11. When the reed valve (70) is in the closed state, the tip (72) comes into contact with the valve seat surface (51c). As a result, the outlet (44) is blocked by the tip (72). In this state, the neck (73) is close to the bottom surface (51). More precisely, in this state, the neck (73) comes closest to the bottom of the groove (51a) through a gap. When the reed valve (70) is in the open state, the neck (73) and the tip (72) come into contact with the contact portion (68) of the valve retainer (60). As a result, the outlet (44) is opened, and the outlet (44) and the inlet passage (45) are in communication via the valve chamber (50).

[0103] <Fastening Members> The injection mechanism (40) has fastening members (80) for fixing the valve retainer (60) and the reed valve (70) to the cylinders (11, 21). Details of the fastening members (80) and their surrounding structures will be described later.

[0104] - Operation of the Injection Mechanism - The operation of the injection mechanism (40) will now be explained. As shown in Figure 7, when the volume of the compression chambers (15b, 25b) is relatively large and the internal pressure of the compression chambers (15b, 25b) is lower than the intermediate pressure, the pressure in the valve chamber (50) communicating with the compression chambers (15b, 25b) will be lower than the intermediate pressure. In this case, as shown in Figure 11, the reed valve (70) will open and the outlet (44) will be opened. As a result, the refrigerant at the intermediate pressure in the injection pipe (39) will be supplied to the compression chambers (15b, 25b) through the injection passage (41). Specifically, when the first reed valve (70A) is open, the refrigerant in the injection pipe (39) will flow sequentially through the main passage (42), the first branch passage (43A), the first valve chamber (50A), and the first introduction passage (45A), and will be supplied to the first compression chamber (15b). When the second reed valve (70B) is open, the refrigerant in the injection tube (39) flows sequentially through the main passage (42), the second branch passage (43B), the second valve chamber (50B), and the second introduction passage (45B) and is supplied to the second compression chamber (25b).

[0105] Subsequently, as the rollers (12, 22) rotate eccentrically, the volume of the compression chambers (15b, 25b) decreases, and when the internal pressure of the compression chambers (15b, 25b) rises above the intermediate pressure, the pressure in the valve chamber (50) communicating with the compression chambers (15b, 25b) also rises above the intermediate pressure. In this case, as shown in Figure 10, the reed valve (70) closes, and the outlet (44) is blocked. As a result, the refrigerant at the intermediate pressure in the injection pipe (39) is not supplied to the compression chambers (15b, 25b). Specifically, when the first reed valve (70A) closes, the outlet (44) of the first branch passage (43A) is blocked by the tip (72) of the first reed valve (70A). When the second reed valve (70B) is closed, the outlet (44) of the second branch passage (43B) is blocked by the tip (72) of the second reed valve (70B).

[0106] Thus, when the compressor (1) is in operation, the first injection element (I1) repeatedly alternates between supplying refrigerant at an intermediate pressure to the first compression chamber (15b) and stopping the supply of refrigerant at an intermediate pressure to the first compression chamber (15b). Simultaneously, the second injection element (I2) repeatedly alternates between supplying refrigerant at an intermediate pressure to the second compression chamber (25b) and stopping the supply of refrigerant at an intermediate pressure to the second compression chamber (25b).

[0107] -Features of the fastening member- The fastening member (80) of this embodiment and its surrounding structure will be described in detail with reference to Figures 8, 10, and 12.

[0108] <Details of the fastening member> The fastening member (80) in this embodiment is made of a bolt. The fastening member (80) has a head (80a) and a shaft portion (80b) extending from the head (80a) to one end in the second direction. The diameter of the head (80a) is larger than the diameter of the shaft portion (80b). The axes of the head (80a) and the shaft portion (80b) are roughly coincide. The axial length (second direction) of the head (80a) is shorter than the axial length (second direction) of the shaft portion (80b). A threaded portion (80c) is formed on the outer circumferential surface of the tip portion (one end in the second direction) of the shaft portion (80b). The fastening member (80) secures the valve retainer (60) and the reed valve (70) by sandwiching the base (71) of the reed valve (70) between the cylinder (11, 21), which is the partition member (90), and the valve retainer (60).

[0109] <Housing Hole> In this embodiment, a housing hole (81) is formed in the cylinder (11, 21). The cylinder (11, 21) is an example of a partition member (90). The partition member (90) is a member that houses the roller (12, 22) and forms a cylinder chamber (15, 25). The partition member (90) includes a first bearing (30), a first cylinder (11), an intermediate plate (34), a second cylinder (21), and a second bearing (35).

[0110] The housing hole (81) is a hole that accommodates a part of the fastening member (80). The housing hole (81) extends in a second direction toward the valve chamber (50) from the end face on the bearing (30, 35) side of the cylinder (11, 21). The housing hole (81) includes a first space (81a) that accommodates the head (80a) and a second space (81b) through which the shaft (80b) is inserted. The first space (81a) and the second space (81b) are located outside the valve chamber (50). The first space (81a) is formed in the cylinder (11, 21) on the side opposite the valve chamber (50) with the second space (81b) in between.

[0111] The first space (81a) is formed by a cylindrical groove formed on the end face of the cylinder (11, 21). The second space (81b) is formed by a cylindrical through hole. The inner diameter of the first space (81a) is larger than the inner diameter of the second space (81b). The axial length (second direction) of the first space (81a) is shorter than the axial length (second direction) of the second space (81b). The first space (81a) and the second space (81b) have the same axis (first axis (C1)).

[0112] <Bottom hole, valve side hole, fastening hole> A bottom hole (82) is formed in the bottom surface (51) that forms the valve chamber (50). The bottom hole (82) is formed by an opening on one end side in the second direction of the housing hole (81) (strictly speaking, the second space (81b)). The bottom hole (82) is formed in a circular shape. The bottom hole (82) is formed on the support surface (51b) of the bottom surface (51) and faces the base (71) of the reed valve (70).

[0113] A first hole, a valve-side hole (83), is formed in the base (71) of the reed valve (70). The valve-side hole (83) is composed of a circular opening. The valve-side hole (83) is located near one end in the first direction of the base (71). The axis of the valve-side hole (83) coincides with the first axis (C1). The inner diameter of the valve-side hole (83) is smaller than the inner diameter of the second space (81b), in other words, the inner diameter of the bottom hole (82).

[0114] A second fastening hole (84) is formed in the fixing portion (67) of the valve retainer (60). The fastening hole (84) penetrates the fixing portion (67) of the valve retainer (60) in a second direction. A screw groove (84a) corresponding to the threaded portion (80c) is formed on the inner circumferential surface that forms the fastening hole (84). The axis of the fastening hole (84) coincides with the first axis (C1). The inner diameter of the fastening hole (84) is approximately equal to the inner diameter of the valve side hole (83).

[0115] <Configuration in the fastened state> When the threaded portion (80c) of the fastening member (80) is fastened into the thread groove (84a), the head (80a) is located in the first space (81a), and the shaft portion (80b) is located in the second space (81b), the bottom hole (82), the valve side hole (83), and the fastening hole (84). In this state, the axes of the head (80a) and the shaft portion (80b) coincide with the first axis (C1). When the fastening member (80) is fastened, the base portion (71) of the reed valve (70) is sandwiched between the valve retainer (60) and the bottom surface (51). In this state, the elastic base portion (71) is pressed against the bottom surface (51). Therefore, a seal portion (91) is formed around the bottom hole (82) by the base portion (71) and the bottom surface (51). The sealing portion (91) shown in Figure 12 surrounds the entire circumference of the bottom hole (82). The sealing portion (91) prevents the refrigerant from the valve chamber (50) from flowing into the housing hole (81) through the bottom hole (82).

[0116] <Arrangement Relationship Between Fastening Member and Valve Chamber> As shown in Figure 12, in this embodiment, a portion of the head (80a) of the fastening member (80) is located outside the interior circumferential surface (CS1) that forms the valve chamber (50) in a second view. Specifically, the first diameter (D1), which is the diameter of the head (80a), is greater than the first width (W1), which is the width in the third direction of the valve chamber (50). The first axis (C1), which is the axis of the head (80a), lies on the centerline extending in the first direction that passes through the midpoint of the third direction of the valve chamber (50). Therefore, in this embodiment, both ends of the head (80a) in the third direction are located outside the interior circumferential surface (CS1) in a second view.

[0117] The head (80a) is positioned in the housing hole (81) on the outside of the valve chamber (50). In other words, the head (80a) and the valve chamber (50) are offset from each other in the second direction. Therefore, even if the first diameter (D1) of the head (80a) is increased, the head (80a) and the valve chamber (50) do not interfere with each other. Thus, the degree of freedom in the layout of the fastening member (80) can be improved. Furthermore, by increasing the first diameter (D1) of the head (80a), the tightening torque of the fastening member (80) can be increased. In addition, since the first width (W1) of the valve chamber (50) can be shortened compared to the head (80a), the dead volume of the valve chamber (50) can be reduced.

[0118] One end of the head (80a) in the first direction is located outside the first inner end face (55) of the valve chamber (50). This allows the valve side hole (83) and even the base (71) of the reed valve (70) to be brought closer to one end of the valve chamber (50). Consequently, the distance from the base (71) to the tip (72) of the reed valve (70) can be increased, thus reducing the stress acting on the base (71) when the reed valve (70) is in the open state.

[0119] <Dimensional relationship of the base> As shown in Figure 12, the distance from the first axis (C1) of the shaft portion (80b) to the other end of the base portion (71) of the reed valve (70) in the first direction is defined as the first distance (L1), and the distance from the first axis (C1) to the one end of the base portion (71) of the reed valve (70) in the first direction is defined as the second distance (L2). In the base portion (71) of this embodiment, the first distance (L1) is greater than the second distance (L2). In other words, the first axis (C1) is closer to one end of the base portion (71) than to the other end in the first direction. For this reason, the distance from the valve side hole (83) to the tip portion (72) side of the base portion (71) can be made longer. Therefore, the concentration of stress acting on the base portion (71) when the reed valve (70) is in the open state can be suppressed.

[0120] <Regarding dead volume> If a space for accommodating the head is formed in the valve retainer, this space will be located inside the valve chamber. This space is easily connected to the compression chamber. Therefore, the space for accommodating the head becomes dead volume, reducing the compression efficiency.

[0121] In contrast, in this embodiment, as shown in Figure 10, the first space (81a) that accommodates the head (80a) is located outside the valve chamber (50). Therefore, it is possible to suppress the increase in dead volume caused by the provision of the fastening member (80).

[0122] Furthermore, in this embodiment, a fastening hole (84) is formed in the valve retainer (60), so the fastening hole (84) can become dead volume. However, since the inner diameter of the fastening hole (84) is smaller than that of the first space (81a) that accommodates the head (80a), the increase in dead volume can be suppressed.

[0123] The threaded portion (80c) of the shaft portion (80b) is tightened into the threaded groove (84a) of the fastening hole (84). This prevents the refrigerant in the valve chamber (50) from flowing from the back side of the valve retainer (60) through the fastening hole (84) into the housing hole (81). Furthermore, when the fastening member (80) is fastened, the base portion (71) of the reed valve (70) is pressed tightly against the bottom surface (51). This prevents the refrigerant in the valve chamber (50) from flowing through the gap between the base portion (71) and the bottom surface (51) into the bottom hole (82). As a result, it is also possible to prevent the housing hole (81) from becoming dead volume.

[0124] -Effects of the Embodiment- In this embodiment, the fastening member (80) has a head (80a) and a shaft portion (80b) extending in a second direction from the head (80a). A first hole (83) is formed in the base portion (71) of the reed valve (70) through which the shaft portion (80b) of the fastening member (80) is inserted. A second hole (84) is formed in the valve retainer (60) through which the shaft portion (80b) is inserted. A first space (81a) is formed in the cylinder (11, 21), which is a partitioning member (90), located outside the valve chamber (50) and accommodating the head (80a).

[0125] In this configuration, the head (80a) of the fastening member (80) is housed in the first space (81a) outside the valve chamber, so that the increase in dead volume due to the first space (81a) can be suppressed. A fastening hole (84) is formed in the valve retainer (60), but since the inner diameter of the fastening hole (84) is smaller than the inner diameter of the first space (81a), the increase in dead volume due to the fastening hole (84) can be suppressed.

[0126] The fastening member (80) fixes the valve retainer (60) and the reed valve (70) with the base (71) of the reed valve (70) sandwiched between the cylinder (11, 21) and the valve retainer (60). This allows for the formation of a seal portion (91) between the base (71) and the bottom surface (51) that suppresses the flow of refrigerant into the first space (81a). Consequently, the flow of refrigerant into the first space (81a) can be prevented from becoming dead volume.

[0127] Since the head portion (80a) is positioned outside the valve chamber (50), the head portion (80a) of the fastening member (80) and the valve chamber (50) do not interfere with each other in a second viewing direction. Therefore, the degree of freedom in layout can be improved.

[0128] In this embodiment, a threaded portion (80c) is provided on the outer circumferential surface of the shaft portion (80b). A threaded groove (84a) corresponding to the threaded portion (80c) is provided on the inner circumferential surface that forms the second hole (84). This prevents the refrigerant on the back side of the valve retainer (60) from flowing into the first space (81a) through the fastening hole (84).

[0129] In this embodiment, a portion of the head (80a) is located outside the inner circumferential surface (CS1) that forms the valve chamber (50) in a second view. Therefore, the diameter of the head (80a) can be increased, and the tightening torque of the fastening member (80) can be increased. Conversely, the valve chamber (50) can be made smaller relative to the head (80a), and the dead volume of the valve chamber (50) can be reduced.

[0130] In this embodiment, since the first diameter (D1) of the head (80a) is larger than the first width (W1) of the valve chamber (50), the tightening torque of the fastening member (80) can be increased. In addition, by narrowing the first width (W1) of the valve chamber (50), the dead volume of the valve chamber (50) can be reduced.

[0131] In this embodiment, a portion of the head (80a) is located outside the end on one side in the first direction of the valve chamber (50) when viewed from the second direction. Therefore, the distance from the base (71) to the tip (72) of the reed valve (70) can be increased, and the stress acting on the base (71) when the reed valve (70) is in the open state can be reduced.

[0132] In this embodiment, the first distance (L1) from the first axis (C1) of the shaft portion (80b) to the other end of the base portion (71) of the reed valve (70) in the first direction is greater than the second distance (L2) from the axis (C1) of the shaft portion (80b) to the one end of the base portion (71) of the reed valve (70) in the first direction. Therefore, the concentration of stress acting on the base portion (71) when the reed valve (70) is in the open state can be suppressed.

[0133] In this embodiment, the compressor (1) compresses carbon dioxide refrigerant. Carbon dioxide refrigerant is used in refrigeration cycles under higher pressure conditions compared to, for example, HFC-based refrigerants. Therefore, the refrigerant pressure in the valve chamber (50) is also relatively high, and the effect of dead volume on the reduction in compression efficiency becomes greater. In contrast, in this embodiment, the dead volume caused by the fastening member (80) can be reduced, so the reduction in compression efficiency can be effectively suppressed.

[0134] <Other Embodiments> The air conditioner (100) may perform only cooling operation or only heating operation among cooling operation and heating operation. The refrigeration cycle device may be a refrigeration device for cooling the inside of the chamber, a hot water supply unit for generating hot water, a chilling unit for generating cold water, etc.

[0135] The compressor (1) may be a rolling piston type rotary compressor. In this case, the roller and vanes are formed separately in the compression mechanism. The tips of the vanes are pressed against the outer surface of the roller. When the roller rotates eccentrically, the vanes move back and forth in the radial direction of the cylinder.

[0136] The compressor (1) may be a hinge-vane type rotary compressor. In this case, the roller and vane are formed separately in the compression mechanism. The tip of the vane is connected to the roller via a hinge. The vane is displaceable relative to the roller. When the roller rotates eccentrically, the vane moves back and forth radially in the cylinder.

[0137] The compression mechanism (10) may be a single-cylinder type having one cylinder. In this case, the injection mechanism (40) has an injection element corresponding to one cylinder.

[0138] The valve chamber (50) may be formed in the intermediate plate (34), the first bearing (30), or the second bearing (35) instead of the cylinder (11, 21).

[0139] The first space (81a) for housing the head (80a) may be formed in a partition member (90) such as a first bearing (30), an intermediate plate (34), or a second bearing (35).

[0140] The housing hole (81) may not have a second space (81b). Specifically, the partition member (90) may have only a first space (81a) that houses the head (80a) on the outside of the valve chamber (50), and the shaft (80b) may be placed inside the valve chamber (50).

[0141] The inner end faces (55, 56) of the valve chamber (50) and the side end faces (63, 64) of the valve retainer (60) may be straight in a second view.

[0142] The fastening member (80) may be a rivet having a head (80a) and a shaft (80b).

[0143] The refrigerant does not have to be carbon dioxide; for example, an HFC-based refrigerant may also be used.

[0144] <Addendum> Although embodiments and modifications have been described above, it will be understood that various changes in form and details are possible without departing from the spirit and scope of the claims. Furthermore, the above embodiments, modifications, and other embodiments may be combined or substituted as appropriate, as long as they do not impair the functions covered by this disclosure.

[0145] The designations "first," "second," "third," etc., mentioned above are used to distinguish between the terms to which these designations are attached, and do not limit the number or order of those terms.

[0146] As described above, this disclosure is useful for rotary compressors and refrigeration cycle systems.

[0147] 1 Compressor 10 Compression mechanism 12,22 Rollers 13,23 Vanes 15,25 Cylinder chamber 15a,25a Intake chamber 15b,25b Compression chamber 39 Injection tube 40 Injection mechanism 42,43 First flow path 44 Outlet 45 Inlet path (second flow path) 50 Valve chamber 60 Valve retainer 70 Reed valve 71 Base 72 Tip 80 Fastening member 80a Head 80b Shaft 80c Threaded part 81a First space 81b Second space 83 Valve side hole (first hole) 84 Fastening hole (second hole) 84a Thread groove 90 Compartment member (cylinder) 101 Refrigerant circuit CS1 Indoor circumferential surface (inner circumferential surface)

Claims

1. A compression mechanism (10) comprising a drive shaft (7), rollers (12, 22) rotationally driven by the drive shaft (7), a partition member (90) housing the rollers (12, 22) and forming cylinder chambers (15, 25), vanes (13, 23) dividing the cylinder chambers (15, 25) into intake chambers (15a, 25a) and compression chambers (15b, 25b), and intake ports (17, 27) for supplying low-pressure refrigerant to the intake chambers (15a, 25a), and an injection pipe (39), wherein the compression mechanism (10) is provided with an injection mechanism (40) for introducing refrigerant into the compression chambers (15b, 25b), and the injection mechanism (40) comprises a valve chamber (50) formed in the partition member (90), The following are included: a first flow path (42, 43) that connects the injection pipe (39) and the valve chamber (50) and has an outlet (44) facing the valve chamber (50); a reed valve (70) disposed in the valve chamber (50), extending in a first direction and having thickness in a second direction, having a base (71) at one end in the first direction and a tip (72) at the other end in the first direction that opens and closes the outlet (44); a valve retainer (60) disposed in the valve chamber (50) and restricting the operation of the reed valve (70); a second flow path (45) that connects the valve chamber (50) and the compression chambers (15b, 25b); and a fastening member (80) that fixes the valve retainer (60) and the reed valve (70) with the base (71) of the reed valve (70) sandwiched between the partition member (90) and the valve retainer (60), A rotary compressor wherein the fastening member (80) has a head (80a) and a shaft portion (80b) extending from the head (80a) in the second direction, the base portion (71) of the reed valve (70) has a first hole (83) through which the shaft portion (80b) of the fastening member (80) is inserted, the valve retainer (60) has a second hole (84) through which the shaft portion (80b) is inserted, and the partition member (90) has a first space (81a) located outside the valve chamber (50) and accommodating the head (80a).

2. The rotary compressor according to claim 1, wherein a threaded portion (80c) is provided on the outer circumferential surface of the shaft portion (80b), and a threaded groove (84a) corresponding to the threaded portion (80c) is provided on the inner circumferential surface forming the second hole (84).

3. The rotary compressor according to claim 1 or 2, wherein the partition member (90) has a second space (81b) through which the shaft portion (80b) is inserted, and the first space (81a) is formed in the partition member (90) on the side opposite to the valve chamber (50) with the second space (81b) in between.

4. The rotary compressor according to any one of claims 1 to 3, wherein a portion of the head (80a) is located outside the inner circumferential surface (CS1) that forms the valve chamber (50) in the second view.

5. The rotary compressor according to claim 4, wherein the diameter of the head (80a) is greater than the width in the third direction perpendicular to the first and second directions in the valve chamber (50).

6. A portion of the head (80a) is located outside the end of the valve chamber (50) in the first direction, in the second view. The rotary compressor according to claim 4 or 5.

7. The rotary compressor according to any one of claims 1 to 6, wherein the first distance (L1) from the axis (C1) of the shaft portion (80b) to the other end of the base portion (71) of the reed valve (70) in the first direction is greater than the second distance (L2) from the axis (C1) of the shaft portion (80b) to the one end of the base portion (71) of the reed valve (70) in the first direction.

8. A rotary compressor according to any one of claims 1 to 7, for compressing a carbon dioxide refrigerant.

9. A refrigeration cycle device comprising a refrigerant circuit (101) having a rotary compressor (1) according to any one of claims 1 to 8.

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