Rotary compressor and refrigeration cycle system

Abstract

Reduce the dead volume of the valve chamber. [Solution] The reed valve (70) has a base (71) fixed to a valve retainer (60), a tip (72) that opens and closes an outlet (44), and a constricted portion (73) connecting the base (71) and the tip (72). The width of the constricted portion (73) in a third direction perpendicular to the first and second directions is smaller than the width of the base (71) in the third direction. The inner surfaces (53, 54) that form the valve chamber (50) are formed outward in the third direction from the constricted portion (73) in a second view. The sides (61, 62) of the valve retainer (60) are formed outward in the third direction from the constricted portion (73) in a second view.

Description

Technical Field

[0001] The present disclosure relates to a rotary compressor and a refrigeration cycle apparatus including the same. The rotary compressor is a compressor that compresses gas in a compression chamber formed in a cylinder by eccentrically rotating a roller in the cylinder. The rotary compressor generally has a vane for partitioning a 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 while contacting 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.

Background Art

[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 to the valve chamber, the refrigerant in the injection pipe is introduced into the compression chamber.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] The valve chamber of the injection mechanism communicates with the compression chamber. Therefore, when the space of the valve chamber increases, the volume (dead volume) that does not contribute to the compression of the refrigerant in the compression stroke increases.

[0005] The purpose of this disclosure is to reduce the dead volume of the valve chamber. [Means for solving the problem]

[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) comprises an annular cylinder (11, 21), rollers (12, 22) driven by the drive shaft (7) and rotating eccentrically within the cylinder (11, 21), and a cylinder chamber (15, 25) between the cylinder (11, 21) and the roller (12, 22) divided into an intake chamber (15a, 25a) and a compression chamber (15b, 25b )and The compression mechanism (10) has vanes (13, 23) that divide the chambers and intake ports (17, 27) for sending low-pressure refrigerant to the intake 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), a first flow path (42, 43) that connects the injection pipe (39) to the valve chamber (50) and has an outlet (44) facing the valve chamber (50), a reed valve (70) positioned in the valve chamber (50) that opens and closes the outlet (44) of the first flow path (42, 43), a valve retainer (60) positioned inside 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), and a second flow path (45) that connects the valve chamber (50) to the compression chambers (15b, 25b). The reed valve (70) has a base (71) fixed to the valve retainer (60), a tip (72) that opens and closes the outlet (44), and a constricted portion (73) connecting the base (71) and the tip (72). The width of the constricted portion (73) in the third direction perpendicular to the first and second directions is smaller than the width of the base (71) in the third direction. The inner surfaces (53, 54) that form the valve chamber (50) are formed outward in the third direction from the constricted portion (73) in the second direction view. The sides (61, 62) of the valve retainer (60) are formed outward in the third direction from the constricted portion (73) in the second direction view.

[0007] In the first embodiment, the reed valve (70) is provided with a constriction (73). The constriction (73) has a smaller width in the third direction than the base (71). In contrast, the inner surfaces (53, 54) forming the valve chamber (50) and the sides (61, 62) of the valve retainer (60) are located outside the constriction (73) in the third direction when viewed from the second direction. If the valve retainer (60) and the valve chamber (50) were to have the same shape as the constriction (73), then the sides (61, 62) of the valve retainer (60) and the inner surfaces (53, 54) of the valve chamber would have recessed portions in the third direction, similar to the reed valve (70). In this case, machining the recessed portions would be difficult, and machining errors would be likely to occur. Therefore, due to machining errors, the gap between the inner surfaces (53, 54) of the valve chamber (50) and the sides (61, 62) of the valve retainer (60) becomes larger, increasing the dead volume. In contrast, in this embodiment, since the inner surfaces (53, 54) of the valve chamber (50) and the sides (61, 62) of the valve retainer (60) are located outside the constricted portion (73) in the third direction, the recessed portion can be eliminated or its recess can be reduced. Consequently, it is possible to suppress the increase in dead volume of the valve chamber (50) due to machining errors on the inner surfaces (53, 54) of the valve chamber (50) and the sides (61, 62) of the valve retainer (60).

[0008] In the second embodiment, the valve retainer (60) is fitted into the valve chamber (50) in a second view.

[0009] In the second embodiment, the valve retainer (60) fits into the valve chamber (50) in a second view. As a result, the valve chamber (50) can be filled by the valve retainer (60), and the dead volume can be reduced.

[0010] In the third embodiment, the entire inner surface (53, 54) forming the valve chamber (50) has a smooth, continuous shape in a second viewing direction, as in the first or second embodiment.

[0011] In the third embodiment, the entire inner surface (53, 54) of the valve chamber (50) is smooth and continuous, eliminating any steps on the inner surface (53, 54). This makes it easier to process the inner surface (53, 54). This also prevents an increase in the dead volume of the valve chamber (50) due to processing errors on the inner surface (53, 54) of the valve chamber (50).

[0012] In the fourth embodiment, in any one of the first to third embodiments, the inner surfaces (53, 54) forming the valve chamber (50) are linear in shape and extend in the first direction.

[0013] In the fourth embodiment, the machining error of the inner surface (53, 54) can be reduced by making the inner surface (53, 54) straight.

[0014] A fifth aspect is that, in the fourth aspect, the inner surface forming the valve chamber (50) has inner end surfaces (55, 56) formed at the ends in the first direction. The inner end surfaces (55, 56) are arc-shaped or straight, widening outward when viewed in the second direction.

[0015] In the fifth embodiment, the machining error of the inner end faces (55, 56) of the valve chamber (50) can be reduced by making them arc-shaped or straight. As a result, the gap between the inner end faces (55, 56) of the valve chamber (50) and the end face of the valve retainer (60) can be reduced, and the dead volume can be reduced.

[0016] The sixth aspect is the fifth aspect, wherein the inner surfaces (53, 54) on both sides of the valve chamber (50) in the third direction are straight lines extending in the first direction when viewed in the second direction. The inner end surfaces (55, 56) on both sides of the valve chamber (50) in the first direction are arc-shaped and widening outward when viewed in the second direction.

[0017] In the sixth embodiment, the inner surface of the valve chamber (50) has a pair of straight inner surfaces (53, 54) and a pair of arc-shaped inner end surfaces (55, 56), which reduces the machining error of the inner surface of the valve chamber (50). As a result, the gap between the inner surface of the valve chamber (50) and the valve retainer (60) can be reduced, and the dead volume can be reduced.

[0018] In the seventh aspect, in the fifth or sixth aspect, the length of the inner surface (53, 54) of the valve chamber (50) in the first direction is greater than twice the radius of curvature of the inner end surface (55, 56).

[0019] In the seventh aspect, since the valve chamber (50) is long in the first direction, the lead valve (70) can be made long. Therefore, the stress acting on the base (71) when the lead valve (70) is in the open state can be reduced.

[0020] In the eighth aspect, in any one of the first to seventh aspects, the valve retainer (60) has a fixing portion (67) that fixes the base (71) of the lead valve (70), and a contact portion (68) with which the constricted portion (73) and the tip portion (72) of the lead valve (70) in the open state come into contact. 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.

[0021] In the eighth aspect, by increasing the thickness of the fixing portion (67) in the second direction, the dead volume of the valve chamber (50) can be reduced by the fixing portion (67).

[0022] In the ninth aspect, in any one of the first to eighth aspects, in the lead valve (70), the width of the tip portion (72) in the third direction is smaller than the width of the base (71) in the third direction.

[0023] In the ninth aspect, since the width of the tip portion (72) of the lead valve (70) is small, it is possible to suppress the tip portion (72) from contacting the inner surfaces (53, 54) of the valve chamber (50) when the tip portion (72) of the lead valve (70) moves.

[0024] The tenth aspect is a refrigeration cycle device including a refrigerant circuit (101) having a rotary compressor (1) according to any one of the first to ninth aspects.

Brief Description of the Drawings

[0025] [Figure 1] FIG. 1 is a piping diagram showing the configuration of the refrigeration cycle device of the embodiment. [Figure 2] Figure 2 is a longitudinal sectional view of the compressor of the embodiment. [Figure 3] Figure 3 is an enlarged view showing the compression mechanism of Figure 2. [Figure 4] Figure 4 is a sectional view taken along line IV-IV of the compression mechanism of Figure 3. In Figure 4, the rotation angle of the first roller is 90°. [Figure 5] Figure 5 is a sectional view taken along line V-V of the compression mechanism of Figure 3. In Figure 5, the rotation angle of the second roller is 270°. [Figure 6] Figure 6 is an enlarged longitudinal sectional view of the main part of the injection mechanism. [Figure 7] Figure 7 is a plan view of the cylinder and the injection element in the axial direction view. [Figure 8] Figure 8 is an exploded perspective view of the main part of the injection element. [Figure 9] Figure 9 is a plan view of the valve retainer, the reed valve, and the valve chamber in the second direction view. [[ID=了24]] [Figure 10] Figure 10 is a sectional view of the injection element in the third direction view. In Figure 10, the reed valve is in the closed state. [Figure 11] Figure 11 is a sectional view of the injection element in the third direction view. In Figure 11, the reed valve is in the open state. [Figure 12] Figure 12 is a plan view of the valve retainer and the reed valve in the second direction view. [Figure 13] Figure 13 is a plan view of the valve chamber and the reed valve in the second direction view.

Embodiments for Carrying Out the Invention

[0026] Embodiments will be described. The compressor (1) of the present 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. <00--00126>

[0027] [[ID=--46]] -Air conditioner-<00001--29>As shown in Figure 1, the air conditioner (100) includes 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.

[0028] 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).

[0029] 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.

[0030] <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.

[0031] 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.

[0032] 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).

[0033] -Compressor Configuration- The compressor (1) is described in detail 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.

[0034] 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.

[0035] As shown in Figures 2 and 3, the compressor (1) comprises 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).

[0036] <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).

[0037] 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).

[0038] <Motor> Motor (3) rotates the drive shaft (7). Motor (3) is located in the upper part of the internal space of the casing (2). 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. Motor (3) is configured to have a variable operating frequency (rotational speed).

[0039] 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).

[0040] <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.

[0041] 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).

[0042] 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.

[0043] <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).

[0044] 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.

[0045] -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).

[0046] 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.

[0047] 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 the low-pressure refrigerant inside the first cylinder (11) and the second cylinder (21), respectively. The space inside the first cylinder (11) contains a first roller (12), a first vane (13), and a pair of first bushes (14). The space inside the second cylinder (21) contains a second roller (22), a second vane (23), and a pair of second bushes (24). The number of cylinders, rollers, vanes, and pairs of bushes is merely an example and is not limited to two.

[0048] 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).

[0049] <Cylinder> 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).

[0050] The first circular hole (11a) is formed to penetrate the first cylinder (11) in the axial direction. The first circular hole (11a) is defined by the inner circumferential surface of the first cylinder (11). The first roller (12) is housed in the first circular hole (11a). The first cylinder chamber (15) is defined by the inner circumferential surface of the first cylinder (11), the outer circumferential surface of the first roller (12), the side surface of the first vane (13), the first bearing (30), and the intermediate plate (34).

[0051] The second circular hole (21a) is formed to penetrate the second cylinder (21) in the axial direction. The second circular hole (21a) is defined by the inner circumferential surface of the second cylinder (21). The second roller (22) is housed in the second circular hole (21a). The second cylinder chamber (25) is defined by the inner circumferential surface of the second cylinder (21), the outer circumferential surface of the second roller (22), the side surface of the second vane (23), the second bearing (35), and the intermediate plate (34).

[0052] The first vane housing hole (16) extends radially outward from the first circular hole (11a) of the first cylinder (11). The first vane housing hole (16) penetrates the first cylinder (11) axially. The first vane (13) is housed in the first vane housing hole (16). The first vane housing hole (16) includes a first bushing hole (16a) into which a pair of first bushings (14) are fitted.

[0053] The second vane housing hole (26) extends radially outward from the second circular hole (21a) of the second cylinder (21). The second vane housing hole (26) penetrates the second cylinder (21) axially. The second vane (23) is housed in the second vane housing hole (26). The second vane housing hole (26) includes a second bushing hole (26a) into which a pair of second bushings (24) are fitted.

[0054] 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).

[0055] <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).

[0056] 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.

[0057] 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) with respect to the first vane housing hole (16).

[0058] A first discharge valve (32) is provided in the first flange portion (30b) for opening and closing the first discharge port (31). 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.

[0059] 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)).

[0060] <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).

[0061] 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.

[0062] 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).

[0063] 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.

[0064] 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).

[0065] <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).

[0066] 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).

[0067] <Laura> The first roller (12) and the second roller (22) are both 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.

[0068] 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°).

[0069] <Bane> 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).

[0070] 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).

[0071] 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).

[0072] <Bush> The pair of first bushes (14) and the pair of second bushes (24) are substantially semi-cylindrical members. The flat surfaces of the pair of first bushes (14) are arranged to face each other. The flat surfaces of the pair of second bushes (24) are arranged to face each other.

[0073] 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).

[0074] 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).

[0075] -Compressor operation- When power is supplied to the motor (3), the drive shaft (7) is driven by the motor (3). 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).

[0076] The gaseous refrigerant that has passed through the first intake pipe (5) is drawn into the first intake chamber (15a) from the first intake port (17). When the first roller (12) rotates eccentrically and the first intake chamber (15a) is blocked from the first intake port (17), the first compression chamber (15b) is formed. As the first roller (12) rotates further eccentrically, the refrigerant is compressed in the first compression chamber (15b).

[0077] 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).

[0078] 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) flows through an internal flow path 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).

[0079] -Injection pipe- As shown in Figure 6, the compressor (1) has an injection pipe (39). The injection pipe (39) is attached to the lower part of the body (2a). The injection pipe (39) penetrates the body (2a) radially. The outlet end of the injection pipe (39) is connected to the compression mechanism (10). In this example, the injection pipe (39) is connected to the second flange portion (35b) of the second bearing (35). The inlet end of the injection pipe (39) is connected to the intermediate flow path (108) of the refrigerant circuit (101) shown in Figure 1. The outlet end of the injection pipe (39) is connected to the injection flow path (41) formed in the compression mechanism (10).

[0080] -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 exceeds the critical pressure. The intermediate pressure corresponds to the pressure between the low pressure and high pressure in the refrigerant circuit (101). In other words, the intermediate pressure corresponds to the pressure between the suction pressure and 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).

[0081] 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 inlet passage (45B).

[0082] <Injection channel> The injection passage (41) is a passage for sending the refrigerant at the intermediate pressure of the injection pipe (39) to the compression chambers (15b, 25b). As shown in Figure 6, the injection passage (41) in this embodiment branches into two and communicates with both the first compression chamber (15b) and the second compression chamber (25b). The injection passage (41) includes a main passage (42), a first branch passage (43A), a second branch passage (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 passage (42) is connected to the injection pipe (39). The first branch passage (43A) connects the main passage (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.

[0083] 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).

[0084] 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).

[0085] 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).

[0086] -Details of the injection element- 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).

[0087] 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.

[0088] <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 forming 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.

[0089] 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 in 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 in 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.

[0090] 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.

[0091] 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) so as to leave the support surface (51b) and the valve seat surface (51c).

[0092] The support surface (51b) is located near one end in the first direction within 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 within the valve chamber (50). toThe valve seat surface (51c) is located around the outlet (44) of the branched channel (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).

[0093] 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.

[0094] <Bargaining> The valve retainer (60) shown in Figures 8 to 12 is positioned in the valve chamber (50) and extends in a 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, "fit" means that the valve retainer (60) fits into the valve chamber (50) substantially without gap, or with a small gap. Here, the "gap" is 1 mm or less, preferably 0.1 mm or less.

[0095] 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).

[0096] 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.

[0097] 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, the back surface (66), on the side opposite to the reed valve (70) in the second direction.

[0098] 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).

[0099] 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 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.

[0100] <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 metallic 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).

[0101] 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).

[0102] 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.

[0103] 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).

[0104] 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) communicate through the valve chamber (50).

[0105] <Structure related to fastening members> The injection mechanism (40) has fastening members (80) for fastening the valve retainer (60) and the reed valve (70) to the cylinders (11, 21). In this embodiment, the fastening members (80) are made of bolts.

[0106] The fastening member (80) has a head (80a) and a shaft portion (80b) extending from the head (80a) to one end in a 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 approximately coincident. A threaded portion (80c) is formed on the circumferential surface of the tip portion (one end in the second direction) of the shaft portion (80b).

[0107] The cylinder (11,21) has a housing hole (81) through which the 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 bearing (30,35) side of the cylinder (11,21). The housing hole (81) includes a first space (81a) for housing the head (80a) and a second space (81b) through which the shaft (80b) is inserted. The first space (81a) and the second space (81b) form a cylindrical space. The bottom surface (51) has a housing hole (81) (strictly speaking, 2nd space (81b) A bottom hole (82), which is the opening at the tip of the valve, is formed. 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 (84a) corresponding to the screw portion (80c) is formed on the inner circumferential surface that forms the fastening hole (84).

[0108] 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) have a coaxial axis (first axis (C1)). If the inner diameter of the first space (81a) is b1, the inner diameter of the second space (81b) is b2, the inner diameter of the bottom hole (82) is b3, the inner diameter of the valve side hole (83) is b4, and the inner diameter of the fastening hole (84) is b5, then the relationship b1>b2=b3>b4>b5 is satisfied.

[0109] 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). When the fastening member (80) is fastened, 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 (51b).

[0110] - 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 also 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).

[0111] 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).

[0112] Thus, when the compressor (1) is in operation, the first injection element (I1) and the first compression chamber (15b) toThe operation of supplying refrigerant at an intermediate pressure and the operation of stopping the supply of refrigerant at an intermediate pressure to the first compression chamber (15b) are performed alternately and repeatedly. Simultaneously, in the second injection element (I2), the operation of supplying refrigerant at an intermediate pressure to the second compression chamber (25b) and the operation of stopping the supply of refrigerant at an intermediate pressure to the second compression chamber (25b) are performed alternately and repeatedly.

[0113] -Features related to the valve retainer, valve chamber, and reed valve- The valve chamber (50) communicates with the compression chambers (15b, 25b) through the introduction passage (45). Therefore, during the compression stroke, a space is formed in the valve chamber (50) that does not contribute to the compression of the refrigerant. In this embodiment, the following features are provided in order to reduce the volume of this space (dead volume).

[0114] As shown in Figure 12, in the reed valve (70), the first width (W1) in the third direction at the neck (73) is smaller than the second width (W2) in the third direction at the base (71). The first width (W1) of the neck (73) is smaller than the third width (W3) in the third direction at the tip (72). The third width (W3) of the tip (72) is smaller than the second width (W2) of the base (71). Strictly speaking, all of these widths (W1, W2, W3) represent the maximum width.

[0115] In contrast, as shown in Figure 13, the inner surfaces (53, 54) forming the valve chamber (50) are formed outside the neck portion (73) in the third direction when viewed from the second direction. Specifically, the first inner surface (53) on one side and the second inner surface (54) on the other side in the third direction are located outside the neck portion (73) in the third direction. Furthermore, the shape of the outer edge of the inner circumferential surface (CS1) differs from the shape of the outer edge of the reed valve (70) when viewed from the second direction, with the outer edge of the reed valve (70) located inside the outer edge of the inner circumferential surface (CS1). Therefore, when viewed from the second direction, the inner circumferential surface (CS1) does not have an inward constriction in the third direction like the reed valve (70), making it easy to machine the inner circumferential surface (CS1). When the machining of the interior surface (CS1) becomes complex, machining errors can cause a larger gap between the interior surface (CS1) of the valve chamber (50) and the side surface (CS2) of the valve retainer (60), resulting in a larger dead volume. In contrast, in this embodiment, machining errors can be reduced, thus reducing such gaps and further reducing dead volume.

[0116] In the valve chamber (50), the first inner surface (53) and the second inner surface (54) have a smooth, continuous shape when viewed from a second direction, and do not have any steps. The first inner surface (53) and the second inner surface (54) are straight lines extending in the first direction when viewed from a second direction. For this reason, the first inner surface (53) and the second inner surface (54) can be easily machined.

[0117] The first inner end face (55) and the second inner end face (56) are arc-shaped, widening outward in a second viewing direction. The first inner end face (55) and the second inner end face (56) are smoothly continuous in a second viewing direction. Furthermore, the first inner surface (53), the first inner end face (55), the second inner surface (54), and the second inner end face (56) are smoothly connected. In other words, the interior circumferential surface (CS1) is smoothly continuous around its entire circumference. Therefore, the interior circumferential surface (CS1) can be easily machined.

[0118] As shown in Figure 12, the sides (61, 62) of the valve retainer (60) are formed to be outward in the third direction from the neck portion (73) in a second view. Specifically, the first side (61) on one side and the second side (62) on the other side in the third direction are located outward in the third direction from the neck portion (73). Furthermore, the shape of the outer edge of the side circumferential surface (CS2) differs from the shape of the outer edge of the reed valve (70) in a second view, with the outer edge of the reed valve (70) located inside the outer edge of the side circumferential surface (CS2). Therefore, in a second view, the side circumferential surface (CS2) does not have an inward constriction in the third direction like the reed valve (70), making it easy to machine the side circumferential surface (CS2). When the machining of the side surface (CS2) becomes complex, machining errors can cause a larger gap between the inner surface (CS1) of the valve chamber (50) and the side surface (CS2) of the valve retainer (60), which in turn increases the dead volume. In contrast, in this embodiment, machining errors can be reduced, thus reducing such gaps and further reducing the dead volume.

[0119] The first side surface (61) and the second side surface (62) have a smooth, continuous shape when viewed from a second direction, and do not have any steps. The first side surface (61) and the second side surface (62) are straight lines extending in the first direction when viewed from a second direction. For this reason, the first side surface (61) and the second side surface (62) can be easily machined.

[0120] The first side end face (63) and the second side end face (64) are arc-shaped, widening outward in a second viewing direction. The first side end face (63) and the second side end face (64) are smoothly continuous in a second viewing direction. Furthermore, the first side surface (61), the first side end face (63), the second side surface (62), and the second side end face (64) are connected in a smooth, continuous manner. In other words, the side circumferential surface (CS2) is smoothly continuous around its entire circumference. Therefore, the side circumferential surface (CS2) can be easily machined.

[0121] As shown in Figure 13, the length in the first direction (first length (L1)) of the inner surfaces (53, 54) of the valve chamber (50) is greater than twice the radius of curvature (r1) of the first inner end surface (55). The first length (L1) may also be greater than twice the radius of curvature of the second inner end surface (56). In this embodiment, the radius of curvature (r1) of the first inner end surface (55) and the radius of curvature of the second inner end surface (56) are approximately equal.

[0122] In other words, the length of the side surfaces (61, 62) of the valve retainer (60) in the first direction is greater than twice the radius of curvature of the first side end face (63) and the second side end face (64). Therefore, in this embodiment, the reed valve (70) can be made longer in the first direction. When the reed valve (70) is made longer, the stress acting on the base (71), which is the pivot point of the neck (73) when the reed valve (70) is in the open state, can be reduced. Therefore, the durability of the reed valve (70) can be improved.

[0123] -Effects of the embodiment- In this embodiment, the first width (W1) of the neck portion (73) is smaller than the second width (W2) of the base portion (71). In contrast, the inner surfaces (53, 54) forming the valve chamber (50) are formed to be outward in a third direction from the neck portion (73) in a second view. The side surfaces (61, 62) of the valve retainer (60) are formed to be outward in a third direction from the neck portion (73) in a second view. If the valve retainer (60) and valve chamber (50) were to have the same shape as the neck portion (73), then, similar to the reed valve (70), there would be recessed portions in the third direction on the side surfaces (61, 62) of the valve retainer (60) and the inner surfaces (53, 54) of the valve chamber. In this case, machining the recessed portions would be difficult, and machining errors would be likely to occur. Therefore, due to machining errors, the gap between the inner surfaces (53, 54) of the valve chamber (50) and the sides (61, 62) of the valve retainer (60) may become larger, potentially increasing the dead volume. In contrast, in this embodiment, since the inner surfaces (53, 54) of the valve chamber (50) and the sides (61, 62) of the valve retainer (60) are located outside the neck portion (73) in the third direction, the recessed portion can be eliminated or its recess can be reduced. Consequently, it is possible to suppress the increase in the dead volume of the valve chamber (50) due to machining errors on the inner surfaces (53, 54) of the valve chamber (50) and the sides (61, 62) of the valve retainer (60).

[0124] Furthermore, this method prevents the neck portion (73) of the reed valve (70) from coming into contact with the inner surfaces (53, 54) of the valve chamber (50) when it moves.

[0125] In this embodiment, the valve retainer (60) is fitted into the valve chamber (50) in the second view. Therefore, in the second view, the gap between the inner surface (CS1) and the side surface (CS2) can be reduced, thereby reducing dead volume.

[0126] In this embodiment, the entire inner surface (53, 54) forming the valve chamber (50) has a smoothly continuous shape when viewed from a second direction. Therefore, it is possible to suppress an increase in the dead volume of the valve chamber (50) due to machining errors of the inner surface (53, 54) of the valve chamber (50). Furthermore, the entire side surface (61, 62) of the valve retainer (60) has a smoothly continuous shape when viewed from a second direction. Therefore, it is possible to suppress an increase in the dead volume of the valve chamber (50) due to machining errors of the valve retainer (60).

[0127] In this embodiment, the inner surfaces (53, 54) forming the valve chamber (50) are linear in shape extending in the first direction. This makes it easier to process the inner surfaces (53, 54), and prevents the dead volume from increasing due to processing errors. Furthermore, the side surfaces (61, 62) of the valve retainer (60) are linear in shape extending in the first direction. This makes it easier to process the side surfaces (61, 62), and prevents the dead volume from increasing due to processing errors. Surface contact between the inner surfaces (53, 54) and the side surfaces (61, 62) is facilitated, and the dead volume can be reduced.

[0128] In this embodiment, the interior circumferential surface (CS1) has inner end surfaces (55, 56) formed at the ends in the first direction. The inner end surfaces (55, 56) are arc-shaped, widening outward when viewed from the second direction. This facilitates the machining of the inner end surfaces (55, 56). Furthermore, the side circumferential surface (CS2) has side end surfaces (63, 64) formed at the ends in the first direction. The side end surfaces (63, 64) are arc-shaped, widening outward when viewed from the second direction. This facilitates the machining of the side end surfaces (63, 64).

[0129] In this embodiment, the interior circumferential surface (CS1) has a pair of straight inner surfaces (53, 54) and a pair of arc-shaped inner end surfaces (55, 56) that widen outward, thus reducing the machining error of the interior circumferential surface (CS1). As a result, the gap between the inner surface of the valve chamber (50) and the valve retainer (60) can be reduced, and the dead volume can be reduced. Furthermore, since the side circumferential surface (CS2) has a pair of straight surfaces (61, 62) and a pair of arc-shaped side end surfaces (63, 64), the machining error of the side circumferential surface (CS2) of the valve retainer (60) can be reduced. As a result, the gap between the inner surface of the valve chamber (50) and the valve retainer (60) can be reduced, and the dead volume can be reduced.

[0130] In this embodiment, the first length (L1) of the inner surfaces (53, 54) of the valve chamber (50) in the first direction is greater than twice the radius of curvature (r1) of the inner end faces (55, 56). Therefore, the stress acting on the base (71) can be reduced, and the durability of the reed valve (70) can be improved.

[0131] In this embodiment, the thickness of the fixed portion (67) in the second direction is greater than the thickness of the contact portion (68) in the second direction. As a result, the volume of the fixed portion (67) in the valve chamber (50) is increased, and the dead volume can be reduced. Specifically, it is preferable that the thickness of the fixed portion (67) in the second direction at an intermediate position in the first direction is greater than the thickness of the contact portion (68) in the second direction at an intermediate position in the first direction. The thickness of the fixed portion (67) in the second direction at other positions may also be greater than the thickness of the contact portion (68) in the second direction at other positions.

[0132] Since the third width (W3) of the tip (72) of the reed valve (70) is smaller than the second width (W2) of the base (71), it is possible to prevent the tip (72) of the reed valve (70) from coming into contact with the inner surfaces (53, 54) of the valve chamber (50) when it moves.

[0133] As shown in Figure 13, the base (71) of the reed valve (70) fits into the valve chamber (50) in a second view. Specifically, the side edges on both sides of the base (71) and the end of the base (71) in the first direction fit into the valve chamber (50). This reduces the dead volume around the base (71).

[0134] <Other Embodiments> The air conditioner (100) may perform only cooling operation or only heating operation. The refrigeration cycle device may include 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 an intermediate plate (34), a first bearing (30), or a second bearing (35) rather than in a cylinder (11, 21).

[0139] The inner surface (CS1) of the valve chamber (50) and the side surface (CS2) of the valve retainer (60) do not have to be oval-shaped; they may be elliptical or rectangular. In this case as well, the entire inner surface (53, 54) and side surface (61, 62) are smoothly continuous in a second-direction view. In this case as well, it is preferable that the inner surface (CS1) and side surface (CS2) have a shape that extends in the first direction.

[0140] 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.

[0141] The second passage connecting the valve chamber (50) and the compression chambers (15b, 25b) does not have to be an inlet passage (45) extending toward the inner circumferential surface of the cylinders (11, 21) as a whole, and may have other passages. Other passages may extend in the axial direction, radial direction, rotational direction, etc., and may be formed in the first bearing (30), second bearing (35), intermediate plate (34), etc. The inlet passage (45) may extend in the radial direction.

[0142] The fastening member (80) may be a rivet having a head (80a) and a shaft (80b). The fastening member (80) may be arranged in the opposite direction to that of the embodiment in the second direction. In this case, a first space (81a) is formed in the valve retainer (60) in which the head (80a) of the fastening member (80) is accommodated.

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

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

[0145] The designations "1st," "2nd," "3rd," 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. [Industrial applicability]

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

[0147] 1. Rotary Compressor 3b Rotor 10 Compression mechanism 11,21 cylinders 12,22 Laura 13,23 Bane 15,25 Cylinder chamber 15a,25a Suction chamber 15b, 25b Compression chamber 17. First inhalation port 27 Second inhalation port 39 Injection tubes 40 Injection Mechanism 42,43 First channel 44 Outlet 45. Inlet path (second channel) 50 valve chambers 53, 54 Inner surface 55,56 Inner end surface 60 Valve retainer 61, 62 Side view 67 Fixed part 68 Contact area 70 Reed valve 71 Base 72 Tip 101 Refrigerant Circuit

Claims

1. Drive shaft (7) and A compression mechanism (10) having an annular cylinder (11, 21), rollers (12, 22) driven by the drive shaft (7) and rotating eccentrically within the cylinder (11, 21), vanes (13, 23) that divide the cylinder chamber (15, 25) between the cylinder (11, 21) and the rollers (12, 22) into an intake chamber (15a, 25a) and a compression chamber (15b, 25b), and intake ports (17, 27) for supplying low-pressure refrigerant to the intake chamber (15a, 25a), It comprises an injection tube (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) is Valve chamber (50) and, The injection pipe (39) and the valve chamber (50) are connected, and the first flow path (42, 43) has an outlet (44) facing the valve chamber (50), A reed valve (70) is positioned in the valve chamber (50) and opens and closes the outlet (44) of the first flow path (42, 43), A valve retainer (60) is positioned within the valve chamber (50), extending in a first direction and having thickness in a second direction, and restricts the operation of the reed valve (70), It includes a second flow path (45) that connects the valve chamber (50) and the compression chambers (15b, 25b), The reed valve (70) has a base (71) fixed to the valve retainer (60), a tip (72) that opens and closes the outlet (44), and a constricted portion (73) connecting the base (71) and the tip (72). The width of the constricted portion (73) in the third direction perpendicular to the first and second directions is smaller than the width of the base portion (71) in the third direction. The inner surfaces (53, 54) forming the valve chamber (50) are formed outward in the third direction from the constricted portion (73) in the second view, The side surfaces (61, 62) of the valve retainer (60) are formed to be outward in the third direction from the constricted portion (73) in the second view, The entirety of the side surfaces (61, 62) on both sides in the third direction of the valve retainer (60) are fitted into the valve chamber (50) in the second view, The entire inner surface (53, 54) forming the valve chamber (50) has a smoothly continuous shape in the second viewing direction. Rotary compressor.

2. A drive shaft (7) and A compression mechanism (10) having an annular cylinder (11, 21), rollers (12, 22) driven by the drive shaft (7) and rotating eccentrically within the cylinder (11, 21), vanes (13, 23) that divide the cylinder chamber (15, 25) between the cylinder (11, 21) and the rollers (12, 22) into an intake chamber (15a, 25a) and a compression chamber (15b, 25b), and intake ports (17, 27) for supplying low-pressure refrigerant to the intake chamber (15a, 25a), It comprises an injection tube (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) is Valve chamber (50) and, The injection pipe (39) and the valve chamber (50) are connected, and the first flow path (42, 43) has an outlet (44) facing the valve chamber (50), A reed valve (70) is positioned in the valve chamber (50) and opens and closes the outlet (44) of the first flow path (42, 43), A valve retainer (60) is positioned within the valve chamber (50), extending in a first direction and having thickness in a second direction, and restricts the operation of the reed valve (70), It includes a second flow path (45) that connects the valve chamber (50) and the compression chambers (15b, 25b), The reed valve (70) has a base (71) fixed to the valve retainer (60), a tip (72) that opens and closes the outlet (44), and a constricted portion (73) connecting the base (71) and the tip (72). The width of the constricted portion (73) in the third direction perpendicular to the first and second directions is smaller than the width of the base portion (71) in the third direction. The inner surfaces (53, 54) forming the valve chamber (50) are formed outward in the third direction from the constricted portion (73) in the second view, The side surfaces (61, 62) of the valve retainer (60) are formed to be outward in the third direction from the constricted portion (73) in the second view, The entirety of the side surfaces (61, 62) on both sides in the third direction of the valve retainer (60) are fitted into the valve chamber (50) in the second view, The inner surfaces (53, 54) that form the valve chamber (50) are linear in shape and extend in the first direction. Rotary compressor.

3. The inner surface forming the valve chamber (50) has inner end surfaces (55, 56) formed at the end in the first direction, The inner end faces (55, 56) are, in the second view, arc-shaped or linear in shape that widens outward. The rotary compressor according to claim 2.

4. The inner surfaces (53, 54) on both sides in the third direction of the valve chamber (50) are in a straight line extending in the first direction when viewed in the second direction. The inner end faces (55, 56) on both sides of the valve chamber (50) in the first direction are arc-shaped and widen outward when viewed in the second direction. The rotary compressor according to claim 3.

5. The length of the inner surface (53, 54) of the valve chamber (50) in the first direction is greater than twice the radius of curvature of the inner end surface (55, 56). The rotary compressor according to claim 3.

6. The valve retainer (60) is A fixing portion (67) for fixing the base portion (71) of the reed valve (70), The open reed valve (70) has a contact portion (68) that comes into contact with the constricted portion (73) and the tip portion (72), 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. A rotary compressor according to any one of claims 1 to 5.

7. In the reed valve (70), the width in the third direction at the tip portion (72) is smaller than the width in the third direction at the base portion (71). A rotary compressor according to any one of claims 1 to 5.

8. 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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