Rotary compressor and refrigeration cycle device

Abstract

An injection mechanism (40) includes: a valve chamber (50); a first flow path (42, 43) that allows connection between an injection pipe (39) and the valve chamber (50) and has an outflow port (44) facing the valve chamber (50); and a second flow path (45) that is positioned on one end side of the valve chamber (50) in a first direction and allows connection between the valve chamber (50) and a compression chamber (15b, 25b). An inner surface forming the valve chamber (50) has a first surface (51) that has the outflow port (44) formed therein, and an inner surface forming the first flow path (42, 43) has a first inclined surface (47) that is continuous with the first surface (51) and is inclined toward the one end side in the first direction in a state of approaching the second flow path (45) toward the first surface (51).

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 vane separate from the roller rotates eccentrically 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, 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, and the like.

[0002] The rotary compressor disclosed in Patent Document 1 has an injection mechanism for introducing a 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 through which it opens into the valve chamber, the refrigerant in the injection pipe is introduced into the compression chamber.

[0003] In the rotary compressor disclosed in Patent Document 1, at the outlet portion of the injection flow path, the inner peripheral surface of the injection flow path and the bottom surface of the valve chamber are orthogonal.

[0004] Specification of Chinese Patent Application Publication No. 103557158

[0005] In the configuration of the conventional injection mechanism, after the refrigerant flows out from the injection flow path into the valve chamber, the flow direction is bent by about 90 degrees and then flows toward the cylinder chamber. If it is necessary to bend the flow direction by about 90 degrees, the flow resistance will increase, and the flow rate of the refrigerant into the cylinder chamber may decrease.

[0006] The technology of the present disclosure aims to increase the flow rate of the refrigerant flowing into the cylinder chamber by the injection mechanism.

[0007] The first embodiment relates to a rotary compressor. The rotary compressor comprises a compression mechanism (10) having a drive shaft (7), annular cylinders (11, 21), rollers (12, 22) driven by the drive shaft (7) and rotating eccentrically within the cylinders (11, 21), vanes (13, 23) that divide the cylinder chambers (15, 25) between the cylinders (11, 21) and the rollers (12, 22) 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). 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), first flow paths (42, 43) that connect the injection pipe (39) to the valve chamber (50) and have an outlet (44) facing the valve chamber (50), a reed valve (70) disposed in the valve chamber (50) and opening and closing the outlet (44) of the first flow paths (42, 43), and a valve retainer (6) disposed within the valve chamber (50) that extends in a first direction and has thickness in a second direction and restricts the operation of the reed valve (70). 0) and a second flow path (45) located on one end side of the valve chamber (50) in the first direction, which connects the valve chamber (50) and the compression chambers (15b, 25b), wherein the inner surface forming the valve chamber (50) has a first surface (51) that faces the valve retainer (60) in the second direction with the reed valve (70) in between and forms the outlet (44), and the inner surface forming the first flow path (42, 43) has a first inclined surface (47) that is continuous with the first surface (51) and is inclined toward the one end side in the first direction with respect to the second direction, such that it approaches the second flow path (45) as it approaches the first surface (51).

[0008] In the first embodiment, the refrigerant flowing through the first flow path (42, 43) flows along the first inclined surface (47) towards the second flow path (45). This reduces the flow resistance when moving from the first flow path (42, 43) to the second flow path (45), allowing the refrigerant to flow smoothly from the first flow path (42, 43) to the cylinder chamber (15, 25). Therefore, the compressor can increase the flow rate of refrigerant flowing into the cylinder chamber (15, 25) by the injection mechanism (40).

[0009] In the second embodiment, in the first embodiment, in a cross-section passing through the center line (L) of the reed valve (70) extending in the first direction and including the second direction, the first inclined surface (47) is located on the one end side in the first direction of the inner surface forming the first flow path (42, 43).

[0010] In the second embodiment, the flow area of ​​the first flow path (42, 43) can be increased. This allows the flow rate of refrigerant flowing into the cylinder chamber (15, 25) by the injection mechanism (40) to be increased.

[0011] A third embodiment is, in the first or second embodiment, the reed valve (70) comprises a base (71) formed at the other end of the reed valve (70) in the first direction and fixed to the valve retainer (60), a tip (72) formed at one end of the reed valve (70) in the first direction and opening and closing the outlet (44), and a connecting member that connects the base (71) and the tip (72) and moves toward the valve retainer (60) together with the tip (72). The reed valve (70) has a movable part (73), and in a cross section that passes through the center line (L) extending in the first direction of the reed valve (70) and includes the second direction, the inner surface that forms the first flow path (42, 43) has a second inclined surface (48) on the other end side in the first direction that is continuous with the first surface (51) and moves away from the second flow path (45) as it approaches the first surface (51), with respect to the second direction and inclined toward the other end side in the first direction.

[0012] In the third embodiment, a portion of the refrigerant flowing through the first flow path (42, 43) flows along the second inclined surface (48) to the other end in the first direction, thereby allowing the refrigerant to push up the reed valve (70). This increases the flow rate of refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0013] The fourth aspect is that in any one of the first to third aspects, the reed valve (70) has a tip portion (72) formed at one end of the reed valve (70) in the first direction and opening and closing the outlet (44), and the first surface (51) has a valve seat surface (58) that contacts the tip portion (72) of the reed valve (70) in the closed state, and is formed around the valve seat surface (58) and the tip portion (72) in the second view The inner surface having a groove (59) that overlaps with the outer edge and forming the first flow path (42, 43) has a straight portion (43a) extending along the second direction upstream of the first inclined surface (47), and in the second direction, the distance (D1) between the boundary (B) between the first inclined surface (47) and the straight portion (43a) and the valve seat surface (58) is longer than the distance (D2) between the bottom surface of the groove (59) and the valve seat surface (58).

[0014] In the fourth embodiment, the first inclined surface (47) can be made longer, making it easier to form a flow of refrigerant from the first flow path (42, 43) to the second flow path (45). This makes it possible to increase the flow rate of refrigerant that flows into the cylinder chambers (15, 25) by the injection mechanism (40).

[0015] A fifth aspect is the first aspect, wherein the first flow path (42, 43) includes the first inclined surface (47) and has an inclined flow path (249) that is inclined toward one end in the first direction with respect to the second direction, such that the center line (CL) of the first flow path (42, 43) approaches the second flow path (45) as it approaches the first surface (51).

[0016] In the fifth embodiment, the inclined flow path (249) facilitates the formation of a flow toward the second flow path (45) in the refrigerant flowing through the first flow path (42, 43). This allows for a larger flow rate of refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0017] The sixth embodiment relates to a refrigeration cycle device. The refrigeration cycle device comprises a refrigerant circuit (101) having a rotary compressor (1) as described in any one of the first to fifth embodiments.

[0018] Figure 1 is a piping diagram showing the configuration of the refrigeration cycle device of the embodiment. Figure 2 is a longitudinal cross-sectional view of the compressor of the embodiment. Figure 3 is an enlarged view of the compression mechanism of Figure 2. Figure 4 is a cross-sectional view of the compression mechanism of 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 of 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 cross-sectional view of the injection element in a third direction view. In Figure 9, the reed valve is in the closed state. 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 open state. Figure 11 is a plan view in a second direction view, showing an enlarged view of the area around the valve body. Figure 12 is a cross-sectional view in a third direction, showing an enlarged view of the area around the outlet of the injection element. In Figure 12, the reed valve is in the open position. Figure 13 is a plan view in a second direction, showing an enlarged view of the area around the valve body of the injection element of Modification 1. Figure 14 is a plan view in a second direction, showing an enlarged view of the area around the valve body of the injection element of Modification 2. Figure 15 is a cross-sectional view in a third direction, showing an enlarged view of the area around the outlet of the injection element of Modification 2. Figure 16 is a cross-sectional view in a third direction of the injection element of Modification 3.

[0019] 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.

[0020] -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.

[0021] 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).

[0022] 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.

[0023] <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.

[0024] 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.

[0025] 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).

[0026] - 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.

[0027] 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.

[0028] 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).

[0029] <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).

[0030] 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).

[0031] <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).

[0032] 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).

[0033] <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.

[0034] 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).

[0035] 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.

[0036] <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).

[0037] 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.

[0038] -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).

[0039] 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.

[0040] As shown in Figures 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. Inside the space of the first cylinder (11), a first roller (12), a first vane (13), and a pair of first bushes (14) are arranged. Inside the space of 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 pairs of bushes is merely an example and is not limited to two.

[0041] The compression mechanism (10) is fixed directly or indirectly to the body (2a) of the casing (2). In this embodiment, the first bearing (30) is fixed directly to the body (2a) of the casing (2) by welding. The first cylinder (11), intermediate plate (34), second cylinder (21), and second bearing (35) are fixed to the first bearing (30) by bolts (not shown). The first bearing (30) may also be indirectly welded to the body (2a) of the casing (2) via other members fixed to the first bearing (30).

[0042] <Cylinders> The first cylinder (11) and the second cylinder (21) are each annular members. As shown in Figure 4, the first cylinder (11) has a first circular hole (11a), a first vane housing hole (16), and a first intake port (17). As shown in Figure 5, the second cylinder (21) has a second circular hole (21a), a second vane housing hole (26), and a second intake port (27).

[0043] 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).

[0044] 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).

[0045] 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.

[0046] 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.

[0047] The first suction port (17) is disposed near the first vane accommodation hole (16). The first suction port (17) radially penetrates the first cylinder (11). The first suction port (17) communicates with the first cylinder chamber (15). The first suction pipe (5) is connected to the first suction port (17). The second suction port (27) is disposed near the second vane accommodation hole (26). The second suction port (27) radially penetrates the second cylinder (21). The second suction port (27) communicates with the second cylinder chamber (25). The second suction pipe (6) is connected to the second suction port (27).

[0048] 〈First bearing〉 As shown in FIG. 3, the first bearing (30) is disposed 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 integrally formed. The first bearing (30) constitutes a closing member that axially closes the first cylinder chamber (15).

[0049] An insertion hole that axially penetrates the first boss portion (30a) is formed in the first bearing (30). The main shaft portion (7a) is inserted through the insertion hole. The inner peripheral surface that forms the insertion hole in the first bearing (30) constitutes a first sliding surface (30c) that the drive shaft (7) contacts.

[0050] As shown in FIG. 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 its thickness direction. The first discharge port (31) is located on the opposite side of the first suction port (17) with the first vane accommodation hole (16) interposed therebetween in the axial view.

[0051] 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) periodically opens and closes according to the pressure in the first compression chamber (15b) described later.

[0052] As shown in Figure 3, 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)).

[0053] <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).

[0054] 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.

[0055] 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).

[0056] 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.

[0057] As shown in Figure 3, 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).

[0058] <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).

[0059] 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).

[0060] <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.

[0061] 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°).

[0062] <Vanes> As shown in Figures 4 and 5, 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).

[0063] 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).

[0064] 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).

[0065] <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.

[0066] 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).

[0067] 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).

[0068] - 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).

[0069] 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).

[0070] 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).

[0071] The refrigerant compressed in the first compression chamber (15b) is discharged from the first compression chamber (15b) to the first muffler space (MS1) via the first discharge port (31). The refrigerant compressed in the second compression chamber (25b) is discharged from the second compression chamber (25b) to the second muffler space (MS2) via the second discharge port (36). The refrigerant in the second muffler space (MS2) flows through an internal flow path and 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).

[0072] -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).

[0073] -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 the high pressure in the refrigerant circuit (101). In other words, the intermediate pressure corresponds to the pressure between the suction pressure and the discharge pressure of the compressor (1). 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. The injection mechanism (40) is provided in the compression mechanism (10).

[0074] 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).

[0075] <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.

[0076] 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).

[0077] 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).

[0078] 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).

[0079] -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).

[0080] In the following description, the first direction is the longitudinal direction of the reed valve (70), the second direction is the thickness direction of the reed valve (70), and the third direction is the width direction of the reed valve (70) perpendicular to the first and second directions. The first direction corresponds to the longitudinal direction of the valve retainer (60). The second direction corresponds to the thickness direction of the valve retainer (60). The third direction corresponds to the width direction of the valve retainer (60). One end in the first direction corresponds to the movable side (tip (72) side) of the reed valve (70). The other end in the first direction corresponds to the fixed side (base (71) side) of the reed valve (70). One end in the second direction corresponds to the bottom surface (51) side in the second direction with respect to the reed valve (70). The other end in the second direction corresponds to the valve retainer (60) side in the second direction with respect to the reed valve (70).

[0081] <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 bottom surface (51) faces the valve retainer (60) in a second direction, with the reed valve (70) in between. An outlet (44) facing the valve chamber (50) is formed on the bottom surface (51). The closing surface (52) is the surface of the intermediate plate (34) that faces the inside of the concave groove and faces the bottom surface (51) in a second direction.

[0082] The inner surface forming the valve chamber (50) includes a circumferential surface extending from the bottom surface (51) to the closing surface (52). In this embodiment, the circumferential surface (53) of the valve chamber (50) is formed in an oval shape with the first direction as the longitudinal direction when viewed from a second direction. The circumferential surface 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 the other end of the valve chamber (50) in the first direction. The second inner end surface (56) is formed at one 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.

[0083] 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.

[0084] The bottom surface (51) of the valve chamber (50) has a support surface (51a), a valve seat surface (58), and a groove (59). As shown in Figures 9 and 10, the support surface (51a) is located near the other end in the first direction of the valve chamber (50). The support surface (51a) supports the base (71) of the reed valve (70). The valve seat surface (58) is located near one end in the first direction of the valve chamber (50). The valve seat surface (58) 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 (58) is formed in an annular shape surrounding the outlet (44) in a second view. The support surface (51a) and the valve seat surface (58) are formed on the same plane. The groove (59) is formed in the valve chamber (50) from the middle in the first direction to one end. The groove (59) is formed on the bottom surface (51) such that the support surface (51a) and the valve seat surface (58) remain. The support surface (51a) and the valve seat surface (58) are closer to the closing surface (52) than to the bottom surface of the groove (59).

[0085] As shown in Figures 9 and 10, a stepped portion (57) is formed as a convex portion at one 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 (59) toward the closing surface (52). The convex surface (57a) on the other end side (closed surface (52) side) of the stepped portion (57) in the second direction is closer to the closing surface (52) than the support surface (51a) or the valve seat surface (58). The convex surface (57a) is formed in a fan shape or crescent shape when viewed in the second direction.

[0086] <Valve Retainer> The valve retainer (60) shown in Figures 8 to 10 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.

[0087] The valve retainer (60) is formed in a shape similar to the inner surface of the valve chamber (50) in a second view. The valve retainer (60) is formed in an oval shape extending in the first direction in a second view. The valve retainer (60) 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).

[0088] 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.

[0089] 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 back surface (66) on the side opposite to the reed valve (70) in the second direction.

[0090] The valve retainer (60) has a fixed portion (67) and a contact portion (68). The fixed portion (67) is formed at the other end of the valve retainer (60) in the first direction. The contact portion (68) is formed extending from the middle portion to one 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 (51a) of the reed valve (70). The contact portion (68) extends in the first direction so as to span the tip (72) and movable portion (73) of the reed valve (70).

[0091] The valve retainer (60) is formed in a boat shape in a cross-sectional view perpendicular to the third direction. The contact portion (68) of the valve retainer (60) has a gradually increasing thickness in the second direction from one end to the other in the first direction. 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.

[0092] <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 the other end in the first direction, a tip (72) located at one end in the first direction, and a movable part (73) connecting the base (71) and the tip (72).

[0093] The base (71) is sandwiched between the support surface (51a) 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 the other 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 (51a).

[0094] 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 (58). 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.

[0095] The movable part (73) extends in a first direction from the base (71) to the tip (72). The width of the movable part (73) in a third direction is smaller than the width of the base (71) and the tip (72) in a third direction. The movable part (73) is movable toward the valve retainer (60) together with the tip (72). The movable part (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 (71) side as a pivot point. In a second view, the movable part (73) coincides with the groove (59). In a second view, the groove (59) surrounds the entire circumference of the movable part (73).

[0096] The reed valve (70) opens and closes the outlet (44). The reed valve (70) deforms between the closed state shown in Figure 9 and the open state shown in Figure 10. When the reed valve (70) is in the closed state, the tip (72) comes into contact with the valve seat surface (58). In this state, in a second view, the outer edge of the tip (72) overlaps with the groove (59). As a result, the outlet (44) is blocked by the tip (72). When the reed valve (70) is in the open state, the movable part (73) and the tip (72) come into contact with the contact part (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).

[0097] <Structure of fastening member> The injection mechanism (40) has a fastening member (80) for fastening the valve retainer (60) and the reed valve (70) to the cylinder (11, 21). The fastening member (80) in this embodiment is made of a bolt.

[0098] The fastening member (80) has a head and a shaft. The head is located on one end of the shaft in the second direction. The axes of the head and the shaft are approximately coincident. A threaded portion is formed on the circumferential surface of the tip of the shaft (the other end in the second direction).

[0099] A housing hole (81) is formed in the cylinder (11, 21) through which a fastening member (80) is inserted. The housing hole (81) extends in a second direction toward the valve chamber (50) from the end face on the intermediate plate (34) side of the cylinder (11, 21). A bottom hole (82), which is the opening at the tip of the housing hole (81), is formed in the bottom surface (51). A valve side hole (83) is formed in the base (71) of the reed valve (70). A fastening hole (84) is formed in the fixing portion (67) of the valve retainer (60). The fastening hole (84) penetrates the valve retainer (60) in a second direction. A screw groove corresponding to the threaded portion is formed on the inner circumferential surface that forms the fastening hole (84).

[0100] The housing hole (81), bottom hole (82), valve side hole (83), and fastening hole (84) overlap each other in a second view. The housing hole (81), bottom hole (82), valve side hole (83), and fastening hole (84) are formed in a substantially circular shape in a second view. The axes of the housing hole (81), bottom hole (82), valve side hole (83), and fastening hole (84) are coaxial with each other.

[0101] With the threaded portion of the fastening member (80) fastened into the threaded groove, the valve retainer (60) is fixed to the cylinder (11, 21). Furthermore, the reed valve (70) is fixed between the fixing portion (67) of the valve retainer (60) and the support surface (51a).

[0102] <Introduction passage> The introduction passage (45) extends from the valve chamber (50) toward the inner circumferential surface (18) of the cylinder (11, 21). The introduction passage (45) extends in a direction perpendicular to the axial direction of the drive shaft (7). In this embodiment, the introduction passage (45) extends in the first direction. The cross section perpendicular to the longitudinal direction of the introduction passage (45) is formed in a rectangular shape. The introduction passage (45) is in contact with the intermediate plate (34) at the other end in the second direction. The introduction passage (45) has an opening (46) for discharging refrigerant at an intermediate pressure into the cylinder chamber (15, 25).

[0103] - 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 10, 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).

[0104] 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 9, 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).

[0105] 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).

[0106] <Detailed Configuration of Branching Channel> As shown in Figures 9 to 12, in a cross section (hereinafter referred to as the first cross section) that passes through the center line (L) extending in the first direction of the reed valve (70) and includes the second direction, the inner surface forming the branching channel (43) has a straight section (43a), a first inclined surface (47), and a second inclined surface (48).

[0107] The straight section (43a) is the portion that extends straight along the second direction. The straight section (43a) is located upstream of the first inclined surface (47) and the second inclined surface (48). As shown in Figure 11, the diameter of the branched channel (43) in the straight section (43a) is smaller than the diameter of the outlet (44).

[0108] As shown in Figure 11, the first inclined surface (47) and the second inclined surface (48) are continuously connected. The first inclined surface (47) and the second inclined surface (48) are composed of a single tapered surface. The first inclined surface (47) is the portion on one end of the first direction relative to the first line (e1) in the second direction view, and the second inclined surface (48) is the portion on the other end of the first direction relative to the first line (e1) in the second direction view. The first inclined surface (47) and the second inclined surface (48) do not include the portion on the first line (e1) in the tapered surface. The first line (e1) is a straight line that passes through the center of the straight section (43a) and extends along the third direction in the second direction view. The first line (e1) is perpendicular to the center line (L).

[0109] As shown in Figure 12, the first inclined surface (47) is located at the valve chamber (50) end of the branched flow path (43). The first inclined surface (47) is continuous with the straight section (43a) and the valve seat surface (58). The first inclined surface (47) is inclined toward one end in the first direction with respect to the second direction, such that it approaches the second flow path (45) as it approaches the valve seat surface (58). In the second direction, the distance (D1) between the boundary (B) between the first inclined surface (47) and the straight section (43a) and the valve seat surface (58) is longer than the distance (D2) between the bottom surface of the groove (59) and the valve seat surface (58).

[0110] The first inclined surface (47) is located on the centerline extending in the first direction of the access path (45) in a second view. The centerline extending in the first direction of the access path (45) is the same as the centerline (L) extending in the first direction of the reed valve (70). The center of the first inclined surface (47) in the third direction is the same as the center of the access path (45) in the third direction. The width of the first inclined surface (47) in the third direction is greater than the width (W1) of the access path (45) in the third direction.

[0111] The second inclined surface (48) is located at the valve chamber (50) end of the branched flow path (43). The second inclined surface (48) is continuous with the straight section (43a) and the valve seat surface (58). The second inclined surface (48) is inclined toward the other end in the first direction with respect to the second direction, such that it moves away from the second flow path (45) as it approaches the valve seat surface (58). In the second direction, the position of the boundary (B) between the second inclined surface (48) and the straight section (43a) is the same as the boundary (B) between the first inclined surface (47) and the straight section (43a). Therefore, the distance (D1) between the boundary (B) between the second inclined surface (48) and the straight section (43a) and the valve seat surface (58) is longer than the distance (D2) between the bottom surface of the groove (59) and the valve seat surface (58). In the first cross-section, the acute angle (angle of inclination) of the second inclined surface (48) with respect to the second direction is the same as the angle of inclination of the first inclined surface (47) with respect to the second direction.

[0112] The second inclined surface (48) is located on the center line (L) of the reed valve (70) extending in the first direction when viewed from the second direction. The center of the second inclined surface (48) in the third direction is the same as the center of the movable part (73) in the third direction. The width of the second inclined surface (48) in the third direction is greater than the width (W2) of the movable part (73) in the third direction.

[0113] A portion of the intermediate-pressure refrigerant flowing through the straight section (43a) flows along the first inclined surface (47) towards the inlet passage (45). Because the abrupt angle change of the refrigerant within the valve chamber (50) from the straight section (43a) to the inlet passage (45) is suppressed, the flow resistance of the refrigerant from the branch passage (43) to the inlet passage (45) is reduced. As a result, the intermediate-pressure refrigerant flows smoothly from the branch passage (43) to the cylinder chambers (15, 25). Consequently, the flow rate of intermediate-pressure refrigerant into the cylinder chambers (15, 25) can be increased.

[0114] Furthermore, a portion of the intermediate-pressure refrigerant flowing through the straight section (43a) flows along the second inclined surface (48) toward the movable part (73) of the reed valve (70). As the intermediate-pressure refrigerant is blown onto the movable part (73), the reed valve (70) is pushed upward by the intermediate-pressure refrigerant. This makes it easier to maintain contact between the reed valve (70) and the contact portion (68) of the valve retainer (60). This makes it easier to maintain the reed valve (70) in its fully open state, thereby increasing the flow rate of the intermediate-pressure refrigerant into the cylinder chambers (15, 25).

[0115] -Effects of the Embodiment- In this embodiment, in a cross-section of the reed valve (70) that passes through the center line (L) extending in the first direction and includes the second direction, the inner surface forming the branch passage (43) has a first inclined surface (47) that is continuous with the valve seat surface (58) and approaches the introduction passage (45) as it approaches the valve seat surface (58), and is inclined toward one end in the first direction with respect to the second direction. The intermediate-pressure refrigerant flowing through the branch passage (43) flows along the first inclined surface (47) and approaches the introduction passage (45). Since abrupt angle changes of the refrigerant in the valve chamber (50) from the straight section (43a) to the introduction passage (45) are suppressed, the flow resistance of the refrigerant from the branch passage (43) to the introduction passage (45) is reduced. As a result, the intermediate-pressure refrigerant flows smoothly from the branch passage (43) to the cylinder chambers (15,25). As a result, the compressor (1) can increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0116] In this embodiment, the first inclined surface (47) is located on one end of the inner surface forming the branched flow path (43) in the first direction. This allows for a wider flow area of ​​the branched flow path (43) while facilitating smooth flow toward the introduction passage (45) for the intermediate-pressure refrigerant. As a result, the compressor (1) can increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0117] In this embodiment, the first inclined surface (47) is located on the center line extending in the first direction of the introduction passage (45) in a second view. Therefore, the intermediate-pressure refrigerant flowing along the first inclined surface (47) flows smoothly toward the introduction passage (47). As a result, the compressor (1) can increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0118] In this embodiment, in particular, the width of the first inclined surface (47) in the third direction is wider than the width of the introduction passage (45) in the third direction. Therefore, the amount of refrigerant flowing along the first inclined surface (47) toward the introduction passage (47) can be increased. As a result, the compressor (1) can increase the flow rate of intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0119] In this embodiment, the contact portion (68) of the valve retainer (60) gradually increases in thickness in the second direction as it moves from the other end in the first direction towards the one end. The reed valve (70) has a base portion (71) formed at the other end in the first direction of the reed valve (70) and fixed to the valve retainer (60), a tip portion (72) formed at one end in the first direction of the reed valve (70) and opening and closing the outlet (44), and a movable portion (73) that connects the base portion (71) and the tip portion (72) and is movable toward the valve retainer (60) together with the tip portion (72). Due to the formation of the first inclined surface (47), the position of the one end of the outlet (44) in the first direction is closer to the end of the contact portion (68) in the first direction compared to the case where the first inclined surface (47) is not formed. Therefore, the distance in the second direction between one end of the outlet (44) in the first direction and the contact portion (68) is longer than when the first inclined surface (47) is not formed. When the reed valve (70) has the above configuration, the maximum distance in the second direction between the tip portion (72) of the reed valve (70) and the outlet (44) is longer when the reed valve (70) is open compared to when the first inclined surface (47) is not formed. As a result, the intermediate-pressure refrigerant flows out more easily, and the compressor (1) can increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0120] In this embodiment, in a cross-section of the reed valve (70) that passes through the center line (L) extending in the first direction and includes the second direction, the inner surface forming the branched flow path (43) has a second inclined surface (48) on the other end side in the first direction that is continuous with the valve seat surface (58) and moves away from the second flow path (45) as it approaches the valve seat surface (58), with respect to the second direction. A portion of the refrigerant at intermediate pressure flows along the second inclined surface (48) toward the other end side in the first direction. As a result, the refrigerant at intermediate pressure is blown onto the reed valve (70), and the reed valve (70) is pushed up by the refrigerant at intermediate pressure. This push-up of the reed valve (70) makes it easier to maintain contact between the reed valve (70) and the contact portion (68) of the valve retainer (60). As a result, the reed valve (70) is more easily kept in its fully open state, allowing the compressor (1) to increase the flow rate of intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0121] In particular, in this embodiment, as described above, the reed valve (70) has a base (71), a tip (72), and a movable part (73) that connects the base (71) and the tip (72) and is movable toward the valve retainer (60) together with the tip (72). The refrigerant flowing along the second inclined surface (48) flows toward the base (71) side of the reed valve (70). As a result, the reed valve (70) is more easily maintained in its fully open state by the intermediate-pressure refrigerant pushing the movable part (73) upward from the base (71) side. As a result, the compressor (1) can increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0122] In this embodiment, the second inclined surface (48) is located on the center line (L) of the reed valve (70) extending in the first direction when viewed from the second direction. Therefore, the intermediate-pressure refrigerant flowing along the second inclined surface (48) is likely to interfere with the reed valve (70). As a result, the reed valve (70) is more likely to remain in its fully open state due to the intermediate-pressure refrigerant. Consequently, the compressor (1) can increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0123] In this embodiment, the width of the second inclined surface (48) in the third direction is wider than the width of the movable part (73) in the third direction. Therefore, the intermediate-pressure refrigerant flowing along the second inclined surface (48) is likely to interfere with the entire third direction of the movable part (73). As a result, the reed valve (70) is more likely to maintain its fully open state due to the intermediate-pressure refrigerant. Consequently, the compressor (1) can increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0124] Furthermore, in this embodiment, the first inclined surface (47) and the second inclined surface (48) are composed of a single tapered surface. Therefore, when forming the first inclined surface (47) and the second inclined surface (48), the first inclined surface (47) and the second inclined surface (48) can be formed simultaneously by simply performing the process to form a single tapered surface. This makes it easy to process the first inclined surface (47) and the second inclined surface (48).

[0125] In this embodiment, in the second direction, the distance (D1) between the boundary (B) between the first inclined surface (47) and the straight section (43a) in the branched flow path (43) and the valve seat surface (58) is longer than the distance (D2) between the bottom surface of the groove (51a) and the valve seat surface (58). Therefore, the first inclined surface (47) can be made longer, making it easier to form a flow of refrigerant from the first flow paths (42, 43) to the second flow path (45). As a result, the compressor (1) can increase the flow rate of intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40). Conversely, the depth of the groove (51a) can be made shallower, so the amount of dead volume that does not contribute to the compression of the refrigerant can be reduced. By reducing the dead volume, the amount of intermediate-pressure refrigerant discharged from the outlet (44) that flows into the cylinder chambers (15, 25) can be increased. This also allows the compressor (1) to increase the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0126] <Variations> The above-described embodiment may also have the following variant configuration.

[0127] - Modification 1 - In the injection mechanism (40) of Modification 1 shown in Figure 13, the first inclined surface (47) and the second inclined surface (48) are not continuous. The first inclined surface (47) and the second inclined surface (48) are formed in a crescent shape when viewed from the second direction. The inclination angle of the first inclined surface (47) and the second inclined surface (48) with respect to the second direction is largest on the center line (L) and 0 degrees on the first line (e1). Between the center line (L) and the first line (e1), the inclination angle gradually decreases as it approaches the first line (e1). The outlet (44) is formed in an elliptical shape when viewed from the second direction.

[0128] In this modified configuration 1, the intermediate-pressure refrigerant flowing through the branched passage (43) flows along the first inclined surface (47) towards the inlet passage (45). This reduces the flow resistance of the refrigerant from the branched passage (43) to the inlet passage (45), thereby increasing the flow rate of the intermediate-pressure refrigerant into the cylinder chambers (15, 25). In addition, a portion of the intermediate-pressure refrigerant flowing through the branched passage (43) flows along the second inclined surface (48) towards the reed valve (70). This pushes up the reed valve (70), thereby increasing the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40).

[0129] - Modified Example 2 - In the injection mechanism (40) of Modified Example 2 shown in Figures 14 and 15, the second inclined surface (48) is not formed, and only the first inclined surface (47) is formed. The first inclined surface (47) is formed in a crescent shape when viewed from the second direction. The inclination angle of the first inclined surface (47) with respect to the second direction is largest on the center line (L) and 0 degrees on the first line (e1). Between the center line (L) and the first line (e1), the inclination angle gradually decreases as it approaches the first line (e1). On the inner surface of the branched flow path (43), a straight section (43a) extends to the position of the valve seat surface () on the other end side in the first direction beyond the first line (e1). In a view from the second direction, the outlet (44) is formed in a semicircular shape on the other end in the first direction relative to the first line (e1), and on the one end in the first direction relative to the first line (e1), it is formed in a curved shape that protrudes toward the one end.

[0130] In this modified configuration 2, the intermediate-pressure refrigerant flowing through the branched passage (43) flows along the first inclined surface (47) towards the inlet passage (45). As a result, the flow resistance of the refrigerant from the branched passage (43) to the inlet passage (45) is reduced, allowing the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40) to be increased.

[0131] - Modification 3 - In the injection mechanism (40) of Modification 3 shown in Figure 16, the branched flow path (43) has an inclined flow path (249) that is inclined toward one end in the first direction with respect to the second direction, such that the flow path centerline (CL) approaches the introduction passage (45) as it approaches the bottom surface (51). In a cross section that passes through the centerline (L) extending in the first direction of the reed valve (70) and includes the second direction, the inclined flow path (249) includes a first inclined surface (47). The first inclined surface (47) is formed on both one end and the other end in the first direction relative to the flow path centerline (CL) when viewed from the third direction.

[0132] In this modified configuration 3, the intermediate-pressure refrigerant flowing through the inclined channel (249) flows along the first inclined surface (47) towards the inlet passage (45). In particular, in the inclined channel (249), even in the portion on the other end side in the first direction, the intermediate-pressure refrigerant flows towards the inlet passage (45). As a result, the flow resistance of the refrigerant from the branched channel (43) towards the inlet passage (45) is reduced, and the flow rate of the intermediate-pressure refrigerant flowing into the cylinder chambers (15, 25) by the injection mechanism (40) can be increased.

[0133] <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.

[0134] The compressor (1) may be a rolling piston type rotary compressor. In this case, the roller and vane are formed separately in the compression mechanism. The tip of the vane is pressed against the outer surface of the roller. When the roller rotates eccentrically, the vane moves back and forth in the radial direction of the cylinder.

[0135] The compressor (1) may be a hinge-vane 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.

[0136] 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.

[0137] The valve chamber (50) and valve retainer (60) may be rectangular or elliptical in a second view.

[0138] The width of the first inclined surface (47) in the third direction may be the same as the width (W1) of the access path (45) in the third direction, or it may be smaller than the width (W1). Also, the width of the second inclined surface (48) in the third direction may be the same as the width (W2) of the movable part (73) in the third direction, or it may be smaller than the width (W2).

[0139] In the first cross-section, the inclination angle of the first inclined surface (47) with respect to the second direction may be different from the inclination angle of the second inclined surface (48) with respect to the second direction.

[0140] In the first cross-section, the first inclined surface (47) and the second inclined surface (48) do not necessarily have a constant inclination angle with respect to the second direction. The first inclined surface (47) and the second inclined surface (48) may be configured such that the inclination angle with respect to the second direction gradually increases as they approach the bottom surface (51), or they may be curved inclined surfaces.

[0141] The refrigerant does not have to be carbon dioxide; for example, an HFC-based refrigerant may also be used.

[0142] <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.

[0143] 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.

[0144] As described above, this disclosure is useful for rotary compressors and refrigeration cycle systems.

[0145] 1 Compressor 10 Compression mechanism 11,21 Cylinder 12,22 Roller 13,23 Vane 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 passage (second flow path) 47 First inclined surface 48 Second inclined surface 50 Valve chamber 51 Bottom surface 58 Valve seat surface 59 Groove 60 Valve retainer 70 Reed valve 71 Base 72 Tip 73 Movable part 249 Inclined flow path L Centerline CL Flow path centerline

Claims

1. A compression mechanism (10) having a drive shaft (7), annular cylinders (11, 21), rollers (12, 22) driven by the drive shaft (7) and rotating eccentrically within the cylinders (11, 21), vanes (13, 23) that divide the cylinder chambers (15, 25) between the cylinders (11, 21) and the rollers (12, 22) 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) has a valve chamber (50), The valve chamber (50) is formed by an injection pipe (39) and a valve chamber (50), and includes a first flow path (42, 43) having an outlet (44) facing the valve chamber (50), a reed valve (70) disposed in the valve chamber (50) and opening and closing the outlet (44) of the first flow path (42, 43), a valve retainer (60) disposed within the valve chamber (50), extending in a first direction and having thickness in a second direction, and restricting the operation of the reed valve (70), and a second flow path (45) located on one end of the valve chamber (50) in the first direction and connecting the valve chamber (50) and the compression chambers (15b, 25b), wherein the inner surface forming the valve chamber (50) has a first surface (51) that faces the valve retainer (60) in the second direction with the reed valve (70) in between, and the outlet (44) is formed thereon. A rotary compressor in which the inner surface forming the first flow path (42, 43) has a first inclined surface (47) that is continuous with the first surface (51) and is inclined toward one end in the first direction with respect to the second direction, such that it approaches the second flow path (45) as it approaches the first surface (51).

2. A rotary compressor according to claim 1, wherein, in a cross-section passing through the center line (L) of the reed valve (70) extending in the first direction and including the second direction, the first inclined surface (47) is located on the one end side in the first direction of the inner surface forming the first flow path (42, 43).

3. In the rotary compressor according to claim 1 or 2, the reed valve (70) has: a base (71) formed at the other end of the reed valve (70) in the first direction and fixed to the valve retainer (60); a tip (72) formed at one end of the reed valve (70) in the first direction and opening and closing the outlet (44); and a movable part (73) that connects the base (71) and the tip (72) and is movable toward the valve retainer (60) together with the tip (72), A rotary compressor in which, in a cross-section of the reed valve (70) passing through a center line (L) extending in the first direction and including the second direction, the inner surface forming the first flow path (42, 43) has a second inclined surface (48) on the other end side in the first direction that is continuous with the first surface (51) and moves away from the second flow path (45) as it approaches the first surface (51).

4. A rotary compressor according to any one of claims 1 to 3, wherein the reed valve (70) has a tip portion (72) formed at one end of the reed valve (70) in the first direction and opening and closing the outlet (44), the first surface (51) has a valve seat surface (58) that contacts the tip portion (72) of the reed valve (70) in the closed state, and a groove (51a) formed around the valve seat surface (58) that overlaps with the outer edge of the tip portion (72) in the second view, and the inner surface forming the first flow path (42, 43) has a straight portion (43a) extending along the second direction upstream of the first inclined surface (47), A rotary compressor in which, in the second direction, the distance (D1) between the boundary (B) between the first inclined surface (47) and the straight section (43a) and the valve seat surface (58) is longer than the distance (D2) between the bottom surface of the groove (51a) and the valve seat surface (58).

5. A rotary compressor according to claim 1, wherein the first flow path (42, 43) includes the first inclined surface (47) and has an inclined flow path (249) that is inclined toward one end in the first direction with respect to the second direction such that the center line (CL) of the first flow path (42, 43) approaches the second flow path (45) as it approaches the first surface (51).

6. A refrigeration cycle device comprising a refrigerant circuit (101) having a rotary compressor (1) according to any one of claims 1 to 5.

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