Rotary compressor and refrigeration cycle device including same

Abstract

The invention discloses a rotary compressor and a refrigeration cycle device including the same. The rotary compressor includes a housing, a main bearing, a sub-bearing, a cylinder, a roller, a vane, and an injection channel provided in at least one of the main bearing, the sub-bearing, and the cylinder. A respective compression chamber may be in communication with the respective compression chamber after a compression start angle of the respective compression chamber. As a result, it is possible to minimize leakage of the injected refrigerant toward the suction port side while ensuring the maximum injection section.

Description

Technical Field

[0001] The invention relates to a rotary compressor and a refrigeration cycle device comprising the rotary compressor. Background Art

[0002] The rotary compressor can be divided into a type in which the blade is slidably inserted into the cylinder and contacts the roller and a type in which the blade is slidably inserted into the roller and contacts the cylinder. Generally, the former is called a roller eccentric rotary compressor (hereinafter referred to as a rotary compressor), and the latter is called a blade concentric rotary compressor (hereinafter referred to as a concentric rotary compressor).

[0003] In a rotary compressor, the blades inserted into the cylinder are drawn toward the roller due to elastic force or back pressure and contact the outer peripheral surface of the roller. This rotary compressor independently forms compression chambers equivalent to the number of blades in each rotation of the roller, and each compression chamber performs the suction stroke, compression stroke, and discharge stroke simultaneously.

[0004] In contrast, in a concentric rotary compressor, the blades inserted into the rollers rotate together with the rollers, and are drawn toward the cylinder due to centrifugal force and back pressure and contact the inner circumferential surface of the cylinder. This concentric rotary compressor continuously forms compression chambers equal to the number of blades in each rotation of the roller, and each compression chamber performs an intake stroke, a compression stroke, and a discharge stroke in sequence. Therefore, compared with a conventional rotary compressor, a concentric rotary compressor forms a higher compression ratio. Therefore, a concentric rotary compressor is more suitable for using high-pressure refrigerants with lower ozone depletion potential (ODP) and global warming potential (GWP), such as R32, R410a, and CO2.

[0005] In the existing concentric rotary compressor, a contact point is provided between the discharge port and the suction port, where the outer circumferential surface of the roller and the inner circumferential surface of the cylinder are almost in contact, thereby separating the discharge port and the suction port. The concentric rotary compressor of Patent Document 1 shows an example in which one suction port is applied. In other words, in the existing concentric rotary compressor, the refrigerant sucked in through one suction port can be sucked into each compression chamber in turn and discharged after being compressed respectively. In such a concentric rotary compressor, the amount of refrigerant sucked into each compression chamber is limited, so that the compression efficiency may be limited.

[0006] As another example, an injection channel may be provided in a concentric rotary compressor having a plurality of contact points. In such a concentric rotary compressor, the injection channel provided in the main bearing and / or the auxiliary bearing and the roller may be periodically connected to the compression chamber. As described above, although the injection channel of the concentric rotary compressor capable of injection is shielded by the roller, as the injection channel approaches the blade groove, the injected refrigerant leaks to the adjacent compression chamber through the blade groove, thereby possibly causing suction loss of the corresponding compression chamber.

[0007] As another example, in a rotary compressor, an injection channel provided in a main bearing can also be opened and closed by the rotation of a roller. In a rotary compressor having such an injection channel, as the injection channel is opened and closed by the roller, the cross-sectional area of ​​the injection channel cannot be fully ensured, and thus the injection flow rate of the refrigerant may be limited. Summary of the invention

[0008] An object of the present invention is to provide a rotary compressor capable of increasing compression capacity by injection and a refrigeration cycle device including the rotary compressor.

[0009] Another object of the present invention is to provide a rotary compressor and a refrigeration cycle device including the rotary compressor that can maximize the injection interval and suppress the leakage of the injected refrigerant to the suction port side.

[0010] Another object of the present invention is to provide a rotary compressor capable of increasing an injection flow rate by optimizing the specifications of an injection channel, and a refrigeration cycle device including the rotary compressor.

[0011] Another object of the present invention is to provide a rotary compressor capable of increasing an injection flow rate by maximally ensuring an actual cross-sectional area of ​​an injection passage, and a refrigeration cycle device including the rotary compressor.

[0012] Another object of the present invention is to provide a rotary compressor that can quickly discharge residual refrigerant even when using high-pressure refrigerants such as R32, R410a, CO2, and a refrigeration cycle device including the rotary compressor.

[0013] The rotary compressor for achieving the purpose of the present invention may include a housing, a main bearing and a secondary bearing, a cylinder, a roller, a blade, and an injection channel. The main bearing and the secondary bearing may be arranged in the inner space of the housing. The cylinder may be arranged between the main bearing and the secondary bearing to form a compression space. The roller may be rotatably arranged on the rotating shaft in the inner space of the cylinder, and may be eccentrically arranged relative to the center of the compression space to have a contact point close to the inner circumferential surface of the cylinder. The plurality of blades may be slidably inserted into the plurality of blade grooves arranged on the roller and rotate with the roller to divide the compression space into a plurality of compression chambers. The injection channel may inject a part of the refrigerant discharged from the compression space and condensed toward the compression space. In this case, the injection channel may be arranged in at least one of the main bearing, the secondary bearing, and the cylinder, and may be connected to the corresponding compression chamber after the compression start angle of the corresponding compression chamber. Thus, the injection interval can be maximized and the injected refrigerant can be suppressed from leaking toward the suction port side.

[0014] As an example, the injection channel may satisfy θ≤applicable area of ​​the injection channel≤θ+360 / n. θ is the compression start angle, and n is the number of blades. Thus, the injection channel is neither connected to the compression chamber in the suction stroke nor to the compression chamber that has completed the discharge stroke, thereby preventing suction loss caused by the injected refrigerant in the corresponding compression chamber in advance, and suppressing the refrigerant in the compression chamber from flowing back toward the injection channel.

[0015] For example, the circumferential width of the injection passage may be 0.4 to 0.8 times the thickness of the blade. Thus, good compression efficiency can be achieved regardless of the operating conditions of the compressor (injection operation or normal operation).

[0016] Specifically, the injection channel can be connected to the compression chamber within a range of 20° after the compression start angle based on the rotation direction of the roller. Thus, the connection position of the injection channel and the corresponding compression chamber is as close as possible to the compression start angle of the corresponding compression chamber, which can help ensure the injection flow rate.

[0017] As another example, the injection passage may be formed to penetrate from the outer peripheral surface of the cylinder to the inner peripheral surface of the cylinder. Thus, by minimizing the length of the injection passage, the refrigerant can be quickly injected into the compression chamber during the injection operation.

[0018] For example, the injection channel may include: an injection inlet, which is recessed from the outer circumference of the cylinder to the inner circumference of the cylinder by a predetermined depth; and an injection outlet, which is connected to the injection inlet and penetrates the inner circumference of the cylinder. The injection outlets may be formed in plurality and arranged at predetermined intervals in the axial direction. In this way, the cross-sectional area of ​​one injection outlet can be formed smaller, and the cross-sectional area of ​​the entire injection outlet can be expanded, so that during the injection operation, the refrigerant flow rate injected into the compression chamber can be increased to improve the compression efficiency.

[0019] In addition, the axial length of the injection channel can be formed to be greater than its circumferential length. Thus, when the position and specification of the injection channel are the same, the actual size of the injection channel can be increased.

[0020] As another example, the injection passage may be formed in at least one of the main bearing and the auxiliary bearing. Thus, the movement of the blades is stabilized during the injection operation, thereby improving the compressor performance, and by suppressing the increase in the surface pressure between the blades and the cylinder, the reliability can be improved, and compared with the cylinder injection structure, the leakage between the compression chambers can be effectively suppressed.

[0021] For example, the injection channel may include: an injection inlet, which is recessed from the outer peripheral surface of the main bearing or the outer peripheral surface of the auxiliary bearing to a predetermined depth toward the inner peripheral surface of the main bearing or the inner peripheral surface of the auxiliary bearing; and an injection outlet, which is connected to the injection inlet and penetrates the sliding surface toward the compression space. Thus, the injection inlet is connected to the inner peripheral surface of the housing, so that the injection pipe can be easily combined with the injection channel, and the injection channel and the injection pipe can be tightly sealed.

[0022] Specifically, the injection outlet may be formed at one. Thus, an injection passage can be formed in the main bearing and / or the auxiliary bearing, and the injection passage can be made as short as possible, so that the refrigerant can be quickly injected into the compression chamber during the injection operation.

[0023] In addition, the radial length of the injection outlet can be formed to be greater than its circumferential length. Thus, when the position and specification of the injection channel are the same, the actual size of the injection outlet directly connected to the compression chamber can be increased.

[0024] In addition, the plurality of blades may be arranged to be inclined at a predetermined angle relative to a radial direction based on the rotation center of the roller. The injection outlet may be formed long along the direction in which the blades are inclined. Thus, the actual size of the injection outlet communicated with the compression chamber may be increased when the position and specification of the injection channel are the same.

[0025] For example, the injection channel may include a first injection channel, a second injection channel, and an injection connection channel. The first injection channel may be formed in the main bearing or the auxiliary bearing, the second injection channel may be formed in the other of the main bearing and the auxiliary bearing that does not have the first injection channel, and the injection connection channel may connect the first injection channel and the second injection channel to each other. Thus, as one injection pipe is connected to a plurality of injection channels, the overall area of ​​the injection channel is expanded, thereby improving the injection effect.

[0026] Specifically, the injection connection channel can be formed by penetrating the axial side surfaces of the cylinder tube, thereby forming injection channels on the bearings on both sides respectively and stably sealing the injection channels.

[0027] For example, the injection channel may include: an injection hole penetrating through both axial sides of the main bearing or the auxiliary bearing; and an injection pipe connected to the injection hole from the outside of the main bearing or the auxiliary bearing. Thus, the injection pipe is immersed in the oil stored in the housing, so that a part of the liquid refrigerant injected through the injection pipe evaporates, thereby reducing the liquid refrigerant flowing into the compression space V.

[0028] Specifically, the injection pipe may penetrate the side surface of the housing and be bent along a curve toward the injection hole. Thus, the injection channel can be processed more easily by making the injection channel as short as possible.

[0029] Specifically, the main bearing may be provided with a discharge port, and the injection channel may be provided in the auxiliary bearing. Thus, since the injection channel is provided in the auxiliary bearing having a relatively simple structure, it is possible to easily process the injection channel and to easily connect the injection pipe to the injection channel.

[0030] As another example, a valve accommodating space may be formed in the injection passage, and an injection check valve that slides by pressure difference to open and close the injection passage may be provided inside the valve accommodating space. Thus, the dead volume caused by the injection passage can be minimized.

[0031] For example, a valve support surface that limits the movement of the injection check valve in the closing direction may be formed on the inner peripheral surface of the valve accommodating space. An injection pipe that is arranged across the injection check valve and limits the movement of the injection check valve in the closing direction may be inserted on the opposite side of the valve support surface. Thus, the manufacturing cost can be reduced by simplifying the structure of the injection check valve.

[0032] In addition, an elastic member that elastically supports the injection check valve in a closing direction may be provided in the valve accommodation space. Thus, by rapidly closing the injection check valve, refrigerant leakage in the compression chamber can be suppressed.

[0033] As another example, a valve receiving groove for receiving an injection check valve for opening and closing the injection channel may be formed on the inner side surfaces of the main bearing, the auxiliary bearing, and the cylinder barrel constituting the compression space, and the valve receiving groove may be connected to the injection channel. A valve support member may be inserted into the valve receiving groove across the injection check valve, and the valve support member may have a valve support surface for fixing one end of the injection check valve and limiting the opening of the other end of the injection check valve. The injection channel may be formed by extending between the inner peripheral surface of the valve receiving groove and the outer peripheral surface of the valve support member. Thus, by improving the movement reliability of the injection check valve constituted by the pilot valve, the injection channel can be stably opened and closed.

[0034] For example, the valve support member may be provided with a valve pressure hole extending from the inner side surface constituting the compression space toward the valve support surface. Thus, the injection check valve constituted by the pilot valve is quickly closed, thereby suppressing refrigerant leakage from the compression chamber.

[0035] As another example, a valve receiving groove for receiving an injection check valve for opening and closing the injection channel may be formed on the outer side surfaces of the main bearing, the auxiliary bearing, and the cylinder barrel, and the valve receiving groove may be connected to the injection channel. A valve support member may be inserted into the valve receiving groove across the injection check valve, and the valve support member may fix one end of the injection check valve and support the other end of the injection check valve. An injection hole constituting the injection channel may be formed in the valve support member. Thus, by facilitating the installation of the injection check valve constituted by the pilot valve, the manufacturing cost can be reduced.

[0036] For example, a valve support surface that limits the opening of the other end of the injection check valve may be formed on one side of the valve receiving groove. A valve pressure hole that penetrates toward the valve support surface may be formed on one side of the injection passage. Thus, by quickly closing the injection check valve formed by the pilot valve, refrigerant leakage in the compression chamber can be suppressed.

[0037] In order to achieve the purpose of the present invention, a refrigeration cycle device including a compressor, a condenser, an expander and an evaporator can be provided. The compressor can be the aforementioned rotary compressor. Thus, by maximally ensuring the injection interval while suppressing the injection refrigerant from leaking to the suction port side, the refrigeration capacity of the refrigeration cycle device can be improved.

[0038] As an example, an injection portion branching from between the condenser and the expander and connected to the injection passage may be provided, and an injection control valve for selectively opening and closing the injection portion may be provided in the injection portion. The injection control valve may control the pressure of the refrigerant injected into the compression chamber to 0.4 to 0.7 times the discharge pressure of the refrigerant discharged from the compression chamber. Thus, good compression efficiency is obtained regardless of the operating conditions of the compressor (injection operation or normal operation). BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Figure 1 This is a system diagram showing a refrigeration cycle device to which the rotary compressor of this embodiment is applied.

[0040] Figure 2 This is a cross-sectional view showing an embodiment of a vane rotary compressor according to the present invention.

[0041] Figure 3 Yes Figure 2 A portion of the compression portion is exploded and shown in a perspective view.

[0042] Figure 4 This is a cross-sectional view showing a part of the compression section of the rotary compressor of this embodiment being assembled.

[0043] Figure 5 is along Figure 4 Cross-sectional view taken along the “IX-IX” line.

[0044] Figure 6 : is a graph showing the change in compression efficiency depending on the size of the injection passage in this embodiment.

[0045] Figure 7 is a graph showing the change in heat according to the position of the injection channel in this embodiment.

[0046] Figure 8 : is a graph showing the change in heat quantity based on the injection pressure in this embodiment.

[0047] Fig. 9 This is a cross-sectional view showing an example in which an injection check valve constituted by a lead valve is provided on the inner peripheral side of a cylinder.

[0048] Fig.10 This is a cross-sectional view showing an example in which an injection check valve constituted by a pilot valve is provided on the outer peripheral side of a cylinder.

[0049] Fig.11 is a cross-sectional view showing another embodiment of the injection channel.

[0050] Fig.12 is along Fig.11 Sectional view taken along line “XX”.

[0051] Fig.13 is a cross-sectional view showing still another embodiment of the injection channel.

[0052] Fig.14 is along Fig.13 A cross-sectional view taken along the line “XI-XI”.

[0053] Fig.15 is a cross-sectional view showing still another embodiment of the injection channel.

[0054] Fig.16 and Fig.17 is along Fig.15 Cross-sectional view taken along line “XII-XII”.

[0055] Fig.18 and Fig.19 is a cross-sectional view showing still another embodiment of the injection channel.

[0056] Fig. 20 is a cross-sectional view showing still another embodiment of the injection channel. DETAILED DESCRIPTION

[0057] Hereinafter, the concentric rotary compressor of the present invention will be described in detail according to an embodiment shown in the accompanying drawings. In the present embodiment, the injection channel is formed in the cylinder, which can also be applied to the concentric rotary compressor in which the blades are slidably inserted into the roller. For example, it can be applied not only to the concentric rotary compressor having an elliptical (hereinafter, asymmetric elliptical) cylinder whose inner circumference is composed of a plurality of curvatures, but also to the concentric rotary compressor having a circular cylinder whose inner circumference is composed of a single curvature. In addition, it can be applied not only to the concentric rotary compressor in which the blade groove for slidably inserting the blade is formed to be inclined at a predetermined angle relative to the radial direction of the roller, but also to the concentric rotary compressor in which the blade groove is formed along the radial direction of the roller. Hereinafter, the example in which the inner circumference of the cylinder is an asymmetric elliptical shape and the blade groove is inclined relative to the radial direction of the roller will be described as a representative example.

[0058] Figure 1 This is a system diagram showing a refrigeration cycle device to which the rotary compressor of this embodiment is applied.

[0059] Reference Figure 1 The refrigeration cycle device 1 of this embodiment may include a compressor 10, a condenser 20, an expander 30, and an evaporator 40. In other words, the condenser 20, the expander 30, and the evaporator 40 are sequentially connected to the discharge side of the compressor 10, and the evaporator 40 is connected to the suction side of the compressor 10. Thus, the compressor 10, the condenser 20, the expander 30, and the evaporator 40 can form a closed loop.

[0060] In addition, the refrigeration cycle device 1 of the present embodiment may further include an injection unit 50. In other words, the first branch pipe 51 may branch from the refrigerant circulation pipe 60 between the outlet of the condenser 20 and the inlet of the expander 30, the first branch pipe 51 may be connected to the inlet 53a of the evaporation container (flash tank, or heat exchanger) 53, the first outlet 53b of the evaporation container (or heat exchanger) 53 may be connected to the refrigerant circulation pipe 60 between the expander 30 and the evaporator 40 through the second branch pipe 52, and the second outlet 53c of the evaporation container (or heat exchanger) 53 may be connected to the injection channel 1332 of the compressor 10 described later through the injection pipe 54. Thus, the gas refrigerant evaporated from the evaporation container (or heat exchanger) 53 and / or a part of the liquid refrigerant are injected into the compression chambers V1, V2, and V3 in compression through the injection pipe 54 and the injection channel 1332 described later, thereby increasing the compression capacity of the corresponding compression chambers V1, V2, and V3.

[0061] In this case, injection control valves 55a and 55b may be provided in the middle of the first branch pipe 51 and / or in the middle of the second branch pipe 52, respectively. This embodiment shows an example in which the first injection control valve 55a is provided in the middle of the first branch pipe 51, and the second injection control valve 55b is provided in the middle of the second branch pipe 52. Thus, the flow rate and pressure of the refrigerant to the injection pipe 54 can be controlled by controlling the opening of the first injection control valve 55a and the second injection control valve 55b. The appropriate pressure of the refrigerant injected by the first injection control valve 55a and the second injection control valve 55b will be re-explained later together with the injection channel 1332.

[0062] In addition, since the refrigerant injected into the compression chambers V1, V2, and V3 moves by the pressure difference between the evaporation container 53 and the compression chambers V1, V2, and V3, it is more advantageous in terms of injection to form the injection channel 1332 at a position as close to the suction port 1331 as possible and not to flow back to the suction port 1331. In other words, in a concentric rotary compressor in which one compression space V is divided into a plurality of compression chambers V1, V2, and V3, the injection channel 1332 can be formed at a position separated from the suction port 1331 in the circumferential direction by an amount corresponding to the interval constituting one compression chamber V1, V2, and V3, for example, it can be formed to communicate with the compression space V in the interval of the compression chambers V1, V2, and V3 after the compression start angle θ. As a result, the injection channel 1332 is separated from the suction port 1331 while being adjacent to the suction port 1331, so that the suction loss caused by the injection can be suppressed while ensuring the injection flow rate to the maximum. The appropriate position of the injection channel 1332 will be described again later.

[0063] In the refrigeration cycle device 1 as described above, the refrigerant compressed in the compressor 10 is discharged into the internal space of the shell 110 of the compressor 10 described later, and the refrigerant is discharged to the condenser 20 through the refrigerant discharge pipe 116 described later, and then passes through the expander 30 and the evaporator 40 in sequence, and then is re-inhaled into the compressor 10 through the refrigerant suction pipe 115 described later.

[0064] At this time, part of the refrigerant that has passed through the condenser 20 moves to the evaporation container 53 through the first branch pipe 51 branched from between the condenser 20 and the expander 30. The refrigerant that has moved to the evaporation container 53 is separated into liquid refrigerant and gas refrigerant. The liquid refrigerant moves to the evaporator 40 through the second branch pipe 52, and the gas refrigerant moves to the compressor 10 through the injection pipe 54, for example, to the compression chambers V1, V2, and V3 after the compression start angle θ. As a result, the amount of refrigerant in the compression chambers V1, V2, and V3 increases, thereby improving the compression efficiency. As a result, it is possible to compensate for the shortage of refrigerant that may occur under low-temperature heating and / or high-temperature cooling conditions.

[0065] Reference Figure 2 The concentric rotary compressor of this embodiment includes a housing 110, a drive motor 120 and a compression unit 130. The drive motor 120 is disposed in an upper inner space 110a of the housing 110, and the compression unit 130 is disposed in a lower inner space 110a of the housing 110. The drive motor 120 and the compression unit 130 are connected by a rotating shaft 123.

[0066] The housing 110 is a part that constitutes the appearance of the compressor, and can be divided into a vertical type or a horizontal type according to the installation form of the compressor. The vertical type is a structure in which the drive motor 120 and the compression part 130 are arranged on the upper and lower sides along the axial direction, and the horizontal type is a structure in which the drive motor 120 and the compression part 130 are arranged on the left and right sides. The housing of this embodiment is described with the vertical type as the center.

[0067] The housing 110 includes a middle housing 111 formed in a cylindrical shape, a lower housing 112 covering a lower end of the middle housing 111 , and an upper housing 113 covering an upper end of the middle housing 111 .

[0068] The driving motor 120 and the compression part 130 may be inserted and fixedly coupled to the intermediate housing 111, and the refrigerant suction pipe 115 may pass through the intermediate housing 111 and be directly connected to the compression part 130. The lower housing 112 is sealed and coupled to the lower end of the intermediate housing 111, and an oil storage space 110b for storing oil supplied to the compression part 130 may be formed at the lower side of the compression part 130. The upper housing 113 is sealed and coupled to the upper end of the intermediate housing 111, and an oil separation space 110c may be formed at the upper side of the driving motor 120 to separate oil from the refrigerant discharged from the compression part 130.

[0069] The driving motor 120 is a part constituting the electric part, and provides power for driving the compression part 130. The driving motor 120 includes a stator 121, a rotor 122, and a rotating shaft 123.

[0070] The stator 121 is fixedly disposed inside the housing 110 and can be pressed into and fixed to the inner circumference of the housing 110 by means of shrink fit or the like. For example, the stator 121 can be pressed into and fixed to the inner circumference of the intermediate housing 111.

[0071] The rotor 122 may be rotatably inserted into the stator 121, and the rotating shaft 123 may be press-fitted into the center of the rotor 122. Thus, the rotating shaft 123 rotates concentrically with the rotor 122.

[0072] A hollow oil passage 125 is formed at the center of the rotating shaft 123, and oil through holes 126a and 126b are formed in the middle of the oil passage 125 to penetrate the outer peripheral surface of the rotating shaft 123. The oil through holes 126a and 126b are composed of a first oil through hole 126a belonging to the range of a main bushing portion 1312 described later and a second oil through hole 126b belonging to the range of a secondary bearing portion 1322.

[0073] An oil absorber 127 may be provided in the middle or at the lower end of the oil flow path 125. The oil absorber 127 may be a gear pump, a viscous pump, a centrifugal pump, etc. This embodiment shows an example of applying a centrifugal pump. Thus, when the rotating shaft 123 rotates, the oil filled in the oil storage space 110b of the housing 110 is pumped by the oil absorber 127, and the oil may be sucked upward along the oil flow path 125 and supplied to each bearing surface.

[0074] The rotating shaft 123 may be provided with a roller 134 described later. The roller 134 may extend from the rotating shaft 123 as a single body, or the rotating shaft 123 and the roller 134 may be separately manufactured and then assembled. In the present embodiment, the rotating shaft 123 is inserted into the roller 134 and assembled later. For example, an axial hole 1341 provided at the center of the roller 134 is axially penetrated, and the rotating shaft 123 may be pressed into the axial hole 1341, or the rotating shaft 123 may be coupled to the axial hole 1341 in a manner that allows it to move in the axial direction. In the case where the rotating shaft 123 is coupled to the roller 134 in a manner that allows it to move in the axial direction, a rotation prevention portion (not shown) may be provided between the rotating shaft 123 and the roller 134, so that the rotating shaft 123 can be constrained in the circumferential direction relative to the roller 134.

[0075] The compression part 130 of this embodiment may include a main bearing 131, a sub-bearing 132, a cylinder 133, a roller 134, and a plurality of blades 135. The main bearing 131 and the sub-bearing 132 are respectively disposed on the upper and lower sides of the cylinder 133, and together with the cylinder 133, form a compression space V, the roller 134 is rotatably disposed in the compression space V, and the blade 135 is slidably inserted into the roller 134 and divides the compression space V into a plurality of compression chambers.

[0076] Reference Figure 2 and Figure 3 The main bearing 131 may be fixedly disposed on the middle housing 111 of the housing 110 . For example, the main bearing 131 may be inserted into and welded to the middle housing 111 .

[0077] The main bearing 131 may be closely coupled to the upper end of the cylinder 133. Thus, the main bearing 131 forms the upper side of the compression space V, and supports the top surface of the roller 134 in the axial direction and the upper half of the rotating shaft 123 in the radial direction.

[0078] The main bearing 131 may include a main plate portion 1311 and a main bushing portion 1312. The main plate portion 1311 covers the upper side of the cylinder 133 and is combined with the cylinder 133. The main bushing portion 1312 extends axially from the center of the main plate portion 1311 toward the driving motor 120 to support the upper half of the rotating shaft 123.

[0079] The main plate portion 1311 is formed in a disk shape, and the outer peripheral surface of the main plate portion 1311 can be closely fixed to the inner peripheral surface of the intermediate housing 111. Thus, the cylinder 133 described later can be easily processed and / or assembled.

[0080] At least one or more discharge ports 1313a, 1313b are formed on the main plate 1311, and at least one or more discharge valves 1361, 1362 for opening and closing the discharge ports 1313a, 1313b may be provided on the top surface of the main plate 1311. Thus, compared with the case where the discharge ports 1313a, 1313b are formed in the cylinder 133, the surface pressure between the blade 135 and the cylinder 133 around the discharge ports 1313a, 1313b is reduced while the surface pressure is kept constant, thereby reducing the vibration of the blade 135. Thus, the wear and vibration noise between the front surface 135a of the blade 135 and the inner peripheral surface 133b of the cylinder 133 facing it can be suppressed.

[0081] The plurality of discharge ports 1313a, 1313b may be formed as a plurality of holes arranged at predetermined intervals along the compression advancing direction (or the rotation direction of the roller). Thus, even if the interval between the inner peripheral surface 133b of the cylinder 133 and the outer peripheral surface 1342 of the roller 134 is narrowed around the contact point P1, the discharge area can be ensured to be as large as possible.

[0082] In the axial side surfaces of the main plate portion 1311, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b can be formed on the bottom surface of the main plate portion 1311 facing the top surface of the roller 134, that is, the main sliding surface 1311a. The first main bearing protrusion 1316a is formed on the inner peripheral surface of the first main back pressure pocket 1315a at the same height as the main sliding surface 1311a, and the inner peripheral surface of the second main back pressure pocket 1315b can be opened. Thus, the first main back pressure pocket 1315a can form a low intermediate pressure, and the second main back pressure pocket 1315b can form a high intermediate pressure (or discharge pressure).

[0083] The main bushing 1312 may be hollow with respect to the roller 134 to radially support the upper half of the rotating shaft 123. Thus, the upper half of the rotating shaft 123, that is, the upper side of the roller 134 described later, may be radially supported by the main bearing 131.

[0084] Reference Figure 2 and Figure 3 , the auxiliary bearing 132 can be closely coupled to the lower end of the cylinder 133. Thus, the auxiliary bearing 132 forms the lower side of the compression space V, and supports the bottom surface of the roller 134 in the axial direction while supporting the lower half of the rotating shaft 123 in the radial direction.

[0085] The auxiliary bearing 132 may include an auxiliary plate portion 1321 that covers the lower side of the cylinder 133 and is combined with the cylinder 133 , and an auxiliary bushing portion 1322 that extends axially from the center of the auxiliary plate portion 1321 toward the lower housing 112 and supports the lower half of the rotating shaft 123 .

[0086] The sub-plate portion 1321 may be formed in a disk shape similar to the main plate portion 1311 , and an outer peripheral surface of the sub-plate portion 1321 may be spaced apart from an inner peripheral surface of the intermediate housing 111 .

[0087] On both axial side surfaces of the auxiliary plate portion 1321 , a first auxiliary back pressure pocket 1325 a and a second auxiliary back pressure pocket 1325 b may be formed on the top surface of the auxiliary plate portion 1321 facing the bottom surface of the roller 134 , i.e., the auxiliary sliding surface 1321 a .

[0088] The first secondary back pressure bag 1325a and the second secondary back pressure bag 1325b can be formed symmetrically with the first main back pressure bag 1315a and the second main back pressure bag 1315b respectively with the roller 134 as the center. For example, the first secondary back pressure bag 1325a can be formed symmetrically with the first main back pressure bag 1315a, and the second secondary back pressure bag 1325b can be formed symmetrically with the second main back pressure bag 1315b.

[0089] A first auxiliary bearing convex portion 1326a may be formed on the inner circumference of the first auxiliary back pressure bag 1325a, and a second auxiliary bearing convex portion 1326b may be formed on the inner circumference of the second auxiliary back pressure bag 1325b. The first auxiliary bearing convex portion 1326a may be formed in the same manner as the auxiliary sliding surface, and the second auxiliary bearing convex portion 1326b may be formed to be lower than the auxiliary sliding surface. Thus, the first auxiliary back pressure bag 1325a may form a lower intermediate pressure in the same manner as the first main back pressure bag 1315a, and the second auxiliary back pressure bag 1325b may form a higher intermediate pressure (or discharge pressure) in the same manner as the second main back pressure bag 1315b.

[0090] The auxiliary bushing 1322 may be formed in a hollow shape based on the roller 134 to radially support the lower half of the rotating shaft 123. Thus, the lower half of the rotating shaft 123, that is, the lower side of the roller 134 described later, may be radially supported by the auxiliary bearing 132.

[0091] Reference Figure 2 and Figure 3 The cylinder 133 of this embodiment can also be closely attached to the bottom surface of the main bearing 131, and fastened to the main bearing 131 together with the auxiliary bearing 132 by bolts. Thus, the cylinder 133 can be fixedly combined with the housing 110 by the main bearing 131.

[0092] The cylinder 133 may be formed in a ring shape with a hollow space portion to form a compression space V at its center. The hollow space portion may be sealed by the main bearing 131 and the auxiliary bearing 132 to form the compression space V, and the roller 134 described later may be rotatably coupled to the compression space V.

[0093] The suction port 1331 may be formed to penetrate from the outer peripheral surface to the inner peripheral surface of the cylinder 133. However, the suction port 1331 may be formed to penetrate the main bearing 131 or the auxiliary bearing 132. In this embodiment, an example in which the suction port 1331 is formed to penetrate the cylinder 133 is shown.

[0094] The suction port 1331 may be formed on one side in the circumferential direction with the contact point P1 described later as the center. The discharge port 1313 may be formed on the main bearing 131 on the opposite side of the suction port 1331, that is, on the other side in the circumferential direction with the contact point P1 as the center.

[0095] The inner circumferential surface 133b of the cylinder 133 may be formed in an elliptical shape. The inner circumferential surface 133b of the cylinder 133 of this embodiment may be formed in an asymmetric elliptical shape by combining a plurality of ellipses, for example, four ellipses having different aspect ratios, with two origins.

[0096] In addition, a later-described injection channel 1332 may be formed on one side of the suction port 1331. In other words, the cylinder 133 may be provided with an injection channel 1332 that passes through the outer peripheral surface 133a of the cylinder 133 toward the inner peripheral surface 133b, and a portion of the refrigerant that has passed through the condenser 20 may bypass the injection channel 1332 and be sucked into the compression chambers V1, V2, and V3. Thus, by minimizing the length of the injection channel 1332, the refrigerant can be quickly injected into the compression chambers V1, V2, and V3 during the injection operation.

[0097] For example, the injection passage 1332 may be formed to be located on one side of the rotation direction of the roller 134 with respect to the suction port 1331. Thus, the amount of refrigerant compressed in the compression chambers V1, V2, and V3 increases, thereby improving the volumetric efficiency.

[0098] The injection passage 1332 may be provided with an injection check valve 1333 for opening and closing the injection passage 1332. The injection check valve 1333 may be variously formed of a plate valve, a pilot valve, a ball valve, etc. In this embodiment, the description will be centered on an example in which the injection check valve 1333 is formed of a plate valve.

[0099] Although not shown, the injection check valve 1333 may be disposed outside the injection passage 1332, in other words, outside the housing 110. In this case, the injection check valve 1333 can be easily disposed. The injection check valve 1333 will be described again later together with the injection passage 1332.

[0100] Reference Figure 2 and Figure 3 In this embodiment, the roller 134 is rotatably disposed in the compression space V of the cylinder 133, and the plurality of blades 135 described later can be inserted into the roller 134 at predetermined intervals in the circumferential direction. Thus, the compression space V can be divided into compression chambers corresponding to the number of the plurality of blades 135. In this embodiment, the description will be centered on an example in which the plurality of blades 135 is three and the compression space V is divided into three compression chambers V1, V2, and V3.

[0101] As described above, the roller 134 may be assembled after the rotating shaft 123 is extended as a single body or the rotating shaft 123 and the roller 134 may be separately manufactured. In this embodiment, the roller 134 and the rotating shaft 123 are assembled after assembly.

[0102] A plurality of blade grooves 1343 are formed on the outer circumference of the roller 134 so that the blades 135 described later can be slidably inserted therein, and a plurality of back pressure chambers 1344 communicating with the blade grooves 1343 can be formed on the inner circumference of the roller. The plurality of back pressure chambers 1344 are communicated with the back pressure bags 1315a, 1315b, 1325a, 1325b, and form an intermediate pressure and / or a discharge pressure together with the back pressure bags 1315a, 1315b, 1325a, 1325b. Thus, the blades 135 inserted into the blade grooves 1343 are pushed to the inner circumference 133b side of the cylinder 133 under the pressure of the back pressure chambers 1344, thereby suppressing leakage between the compression chambers V1, V2, and V3.

[0103] In addition, the rotation center Or of the roller 134 may be coaxial with the axis (not shown) of the rotating shaft 123, and the roller 134 may rotate concentrically with the rotating shaft 123. However, as described above, as the inner circumferential surface 133b of the cylinder 133 is formed into an asymmetric elliptical shape biased in a specific direction, the rotation center of the roller 134 may be eccentrically arranged relative to the outer diameter center of the cylinder 133. Thus, one side of the outer circumferential surface 1342 of the roller 134 is almost in contact with the inner circumferential surface 133b of the cylinder 133 to form a contact point P1.

[0104] Reference Figure 2 and Figure 3 , the plurality of blades 135 of the present embodiment can be slidably inserted into each blade groove 1343. Thus, the plurality of blades 135 can be formed into a shape substantially the same as that of each blade groove 1343.

[0105] The plurality of blades 135 may be formed in substantially the same shape. For example, the plurality of blades 135 may be formed in substantially rectangular parallelepiped shapes, and the front surface 135a of the blade 135 that contacts the inner circumferential surface 133b of the cylinder 133 may be formed as a curved surface along the circumferential direction. Thus, the front surface 135a of the blade 135 may be in line contact with the inner circumferential surface 133b of the cylinder 133, thereby reducing friction loss.

[0106] Reference numeral 137 (not described in the drawings) is a discharge muffler.

[0107] The vane rotary compressor provided with the injection passage as described above operates as follows.

[0108] That is, when power is applied to the driving motor 120 , the rotor 122 of the driving motor 120 and the rotating shaft 123 coupled to the rotor 122 rotate, and the roller 134 coupled to or integrally formed with the rotating shaft 123 rotates together with the rotating shaft 123 .

[0109] Then, the plurality of blades 135 are drawn out from the respective blade grooves 1343 and contact the inner circumferential surface 133 b of the cylinder 133 under the action of the centrifugal force generated by the rotation of the roller 134 and the back pressure of the back pressure chamber 1344 supporting the rear surface 135 b of the blade 135 .

[0110] Therefore, the compression space V of the cylinder 133 is divided by a plurality of blades 135 into compression chambers (including suction chambers or discharge chambers) V1, V2, V3, the number of which is equivalent to the number of blades 135, and the following series of processes are repeatedly performed: each compression chamber V1, V2, V3 moves with the rotation of the roller 134, and its volume changes due to the shape of the inner circumferential surface 133b of the cylinder 133 and the eccentricity of the roller 134, and the refrigerant sucked into each compression chamber V1, V2, V3 is compressed and discharged into the internal space of the shell 110 while moving with the roller 134 and the blades 135.

[0111] At this time, as the injection channel 1332 connected to the outlet of the condenser 20 through the evaporation container 53 is formed on one side of the suction port 1331 in the circumferential direction, a part of the refrigerant passing through the condenser 20 can be sucked into the corresponding compression chambers V1, V2, and V3 again through the injection pipe 54 and the injection channel 1332. As a result, the amount of refrigerant sucked into the corresponding compression chambers V1, V2, and V3 increases, thereby improving the volumetric efficiency.

[0112] In this case, the injection channel 1332 may be formed to communicate with the corresponding compression chambers V1, V2, V3 after the compression start angle of the corresponding compression chambers V1, V2, V3, in other words, after the suction completion angle of the corresponding compression chambers V1, V2, V3. Thus, the increase in the specific volume of the sucked refrigerant caused by the injected refrigerant can be suppressed.

[0113] Figure 4 This is a cross-sectional view showing a part of the compression part of the rotary compressor of this embodiment assembled and shown. Figure 5 is along Figure 4 Cross-sectional view taken along the “IX-IX” line.

[0114] Reference Figure 4 and Figure 5 The injection channel 1332 may be formed at a position where the injected refrigerant does not flow toward the suction port (or the compression chamber during suction) 1331 and the refrigerant compressed in the corresponding compression chambers V1, V2, and V3 does not flow back toward the injection pipe 54 via the injection channel 1332. In other words, the injection channel 1332 may be formed at a position that satisfies the following <Formula>.

[0115] <Formula>

[0116] θ≤Applicable area of ​​the injection channel≤θ+360 / n

[0117] Here, θ is the compression start angle and n is the number of blades.

[0118] For example, as in the present embodiment, when the contact point P1 is set to 0° and the number of blades 135 is three, the injection channel 1332 may be formed at a compression start angle greater than or equal to the corresponding compression chambers V1, V2, V3 (at Figure 5 The angle is approximately 170°)θ and is less than or equal to the compression start angle θ plus 120° (in Figure 5 Thus, the injection passage 1332 is neither connected to the compression chambers V1, V2, V3 in the suction stroke nor connected to the compression chambers V1, V2, V3 that have completed the discharge stroke. Thus, in the corresponding compression chambers V1, V2, V3, the suction loss caused by the injected refrigerant can be prevented in advance, and the refrigerant in the compression chambers V1, V2, V3 can be suppressed from flowing back to the injection passage.

[0119] Specifically, the injection channel 1332 may be formed so that its starting point is located at the compression start angle θ of the corresponding compression chambers V1, V2, and V3. In other words, the end portion of the injection channel 1332 located on the opposite side of the rotation direction of the roller 134 of both ends in the circumferential direction may be located at the compression start angle θ of the corresponding compression chambers V1, V2, and V3. Thus, as described above, the injection channel 1332 is not connected to the compression chambers V1, V2, and V3 in the suction stroke and the compression chambers V1, V2, and V3 after the discharge, and is located at the farthest position from the discharge port 1313, so that the injection interval can be formed as long as possible.

[0120] In addition, the injection channel 1332 of the present embodiment is formed with an injection outlet 1332b of a circular cross-section, and the injection outlet 1332b is connected to the corresponding compression chambers V1, V2, and V3, and the injection outlet 1332b can be formed to be smaller than the thickness T of the blade 135. It should be noted that the injection channel 1332 of the present embodiment can be formed in conjunction with the width (thickness) T of the blade 135. Generally, if the size (e.g., inner diameter) D of the injection channel 1332 is large, the compression efficiency increases during the injection operation. However, under normal operating conditions without injection operation, the injection channel 1332 acts as a dead volume, which reduces the compression efficiency. Thus, as described above, the inner diameter D of the injection channel (or injection outlet) 1332 can be formed to be smaller than the thickness T of the blade 135, and can be increased or decreased in conjunction with the thickness T of the blade 135.

[0121] Figure 6 : is a graph showing the change in compression efficiency depending on the size of the injection passage in this embodiment.

[0122] Reference Figure 6It can be confirmed that when the size of the injection channel 1332, that is, the value of the inner diameter D of the injection outlet 1332b divided by the blade thickness T is less than 0.4, the compression efficiency is greatly reduced during the injection operation. On the contrary, when the value of the inner diameter D of the injection outlet 1332b divided by the blade thickness T is greater than 0.8, the compression efficiency is greatly reduced during normal operation.

[0123] In other words, it can be confirmed that when the value of the inner diameter D of the injection outlet 1332b divided by the blade thickness T is greater than or equal to 0.4 and less than or equal to 0.8, good compression efficiency is exhibited regardless of the operating conditions of the compressor (injection operation or normal operation). Therefore, preferably, the inner diameter D of the injection outlet 1332b can be formed so that the value of the inner diameter D of the injection outlet 1332b divided by the thickness T of the blade 135 is 0.4 to 0.8 times.

[0124] In this case, preferably, the injection channel 1332 can be formed to be located in a preset range starting from the compression start angle θ, for example, within a range of 20° after the compression start angle θ. Generally, when the position where the injection channel 1332 is connected to the corresponding compression chambers V1, V2, and V3 is defined as a connection position based on the rotation direction of the roller 134, the connection position is formed as close as possible to the compression start angle θ of the corresponding compression chambers V1, V2, and V3, which is more conducive to ensuring the injection flow rate. If the injection position defined as the connection position is far away from the compression start angle θ, the injection operation may be delayed accordingly, resulting in a reduction in the injection flow rate.

[0125] Figure 7 1 is a graph showing the change in heat according to the position of the injection channel in this embodiment. This is a value obtained by taking the thickness T of the blade 135 into consideration.

[0126] Reference Figure 7 It can be confirmed that, based on the value of 0.4 to 0.8 times the inner diameter D of the jet outlet 1332b divided by the thickness T of the blade 135, the heat is highest when the jet outlet 1332b is formed at the compression start angle θ, and conversely, the farther the jet channel 1332 is from the compression start angle θ, the less heat is generated. In particular, it can be confirmed that, compared with the case where the jet channel 1332 is formed at a position deviating 20° from the compression start angle θ, the heat is sharply reduced when the jet channel 1332 is formed at a position deviating 30° from the compression start angle θ. Therefore, when the value of 0.4 to 0.8 times the inner diameter D of the jet outlet 1332b divided by the thickness T of the blade 135 is preferably, the jet channel 1332 is formed at a position deviating 20° from the compression start angle θ.

[0127] In addition, as described above, the injection channel 1332 of the present embodiment can be selectively opened and closed by the injection control valves 55a, 55b provided in the middle of the injection pipe 54. In other words, the injection channel 1332 can be opened during the injection operation, and can be closed when the injection operation is not performed. Generally, if the pressure of the injected refrigerant is too high, the pressure of the compression chambers V1, V2, and V3 will rise excessively, so that the compression efficiency will be reduced. On the contrary, if the pressure of the injected refrigerant is too low, the compressed refrigerant may flow back to the injection portion 50 side. Therefore, even in the case of injection operation, the opening of the injection channel 1332 can be appropriately increased or decreased according to the pressure of the compression chambers V1, V2, and V3.

[0128] Figure 8 : is a graph showing the change in heat quantity based on the injection pressure in this embodiment.

[0129] Reference Figure 8 It can be confirmed that when the value of injection pressure divided by discharge pressure reaches about 0.4, the increase of heat begins to slow down sharply, and when it reaches about 0.7, the heat decreases sharply. Therefore, preferably, the first injection control valve 55a and / or the second injection control valve 55b can be controlled to make the injection pressure reach about 0.4 to 0.7 times the discharge pressure.

[0130] As described above, when the injection channel 1332 is formed by passing through the cylinder 133, not only the structure of the injection channel 1332 is simple, but also the size and / or shape of the injection channel 1332 can be realized in various ways. Thus, not only the injection channel 1332 can be easily processed, but also an appropriate injection flow rate can be easily ensured.

[0131] In addition, when the injection channel 1332 is formed to penetrate the cylinder 133, the length of the injection channel 1332 can be minimized, so that the dead volume generated by the injection channel 1332 can be minimized.

[0132] On the other hand, a valve accommodation space 1336 is formed in the injection passage 1332, and an injection check valve 1333 that slides by a pressure difference to open and close the injection passage 1332 may be provided inside the valve accommodation space 1336. As described above, in this embodiment, the example in which the injection check valve 1333 is composed of a plate valve is mainly described, but the same can also be applied to the case in which the injection check valve 1333 is composed of a piston valve or a ball valve.

[0133] For example, a valve support surface 1336a that restricts the movement of the injection check valve 1333 in the closing direction may be formed on the inner circumferential surface of the valve accommodation space 1336, and an injection pipe 54 that is arranged across the injection check valve 1333 and restricts the movement of the injection check valve 1333 in the closing direction may be inserted on the opposite side of the valve support surface 1336a. In this case, the interval between the valve support surface 1336a and the injection pipe 54 may be larger than the thickness of the injection check valve 1333. Thus, the injection check valve 1333 moves in the opening and closing direction, for example, in the radial direction, by the pressure difference inside the valve accommodation space 1336 to open and close the injection channel 1332.

[0134] A plurality of injection grooves 1333a may be formed on the outer peripheral surface of the injection check valve 1333, and an injection hole 1336b may be formed in the center of the valve support surface 1336a. In this case, the inner diameter of the injection hole 1336b may be smaller than the inner diameter of the imaginary circle connecting the injection grooves 1333a of the injection check valve 1333. Thus, when the injection check valve 1333 is placed on the valve support surface 1336a, the injection channel 1332 may be closed.

[0135] Although not shown, an injection groove (not shown) may be formed along the inner peripheral surface of the valve accommodation space 1336. In this case, while a piston valve or a ball valve is used as the injection check valve 1333, the injection passage 1332 can be formed constantly.

[0136] In addition, although not shown, an elastic member (not shown) that elastically supports the injection check valve 1333 in the closing direction may be provided in the valve accommodating space 1336. In this case, when the compressor is running, the injection check valve 1333 may be quickly closed, thereby effectively preventing the refrigerant in the compression chambers V1, V2, and V3 from flowing back to the injection passage 1332.

[0137] On the other hand, the injection check valve can also be formed by a pilot valve. Fig. 9 is a cross-sectional view showing an example in which an injection check valve constituted by a pilot valve is provided on the inner peripheral side of a cylinder. Fig.10 This is a cross-sectional view showing an example in which an injection check valve constituted by a pilot valve is provided on the outer peripheral side of a cylinder.

[0138] Reference Fig. 9 A valve receiving groove 1337 is formed on the inner circumferential surface of the cylinder 133, and a valve support member 1338 covering the valve receiving groove 1337 can be fastened to the valve receiving groove 1337. The valve receiving groove 1337 is a space for receiving the injection check valve 1333, and the valve support member 1338 is a member that fixes one end of the injection check valve 1333 composed of a pilot valve and supports the other end to be rotatable. Thus, the injection check valve 1333 can rotate inside the valve receiving groove 1337 according to the pressure difference to open and close the injection channel 1332.

[0139] For example, the valve receiving groove 1337 may be recessed from the inner circumferential surface 133b of the cylinder 133 toward the outer circumferential surface 133a by a predetermined depth. In this case, the cross-sectional area of ​​the valve receiving groove 1337 may be larger than the cross-sectional area of ​​the valve support member. For example, the valve receiving groove 1337 may be formed into a rectangular shape that is long in the circumferential direction corresponding to the valve support member 1338, and an outlet of the injection channel 1332 may be formed between the inner circumferential surface of the valve receiving groove 1337 and the outer circumferential surface of the valve support member 1338. In other words, the axial length of the minor axis constituting the valve receiving groove 1337 is substantially the same as the axial length of the valve support member 1338, and the circumferential length of the major axis constituting the valve receiving groove 1337 may be larger than the circumferential length of the valve support member 1338. Thus, as described above, one side of the valve receiving groove 1337 in the circumferential direction may be separated from the valve support member 1338 and the outlet of the injection channel 1332 may be formed.

[0140] The inner side surface of the valve support member 1338 may be formed into an arc shape having the same curvature as the inner peripheral surface of the cylinder 133, and one end thereof may be closely attached to the bottom surface of the valve receiving groove 1337 and the side wall surface via the injection check valve 1333, while the other end thereof may be separated from the bottom surface and the side wall surface of the valve receiving groove 1337. In other words, one end of the valve support member 1338 may form a valve fixing surface 1338a, and the other end thereof may form a valve supporting surface 1338b. Thus, the injection check valve 1333 may rotate in a state fixed to the valve fixing surface 1338a of the valve support member 1338, and the opening degree may be limited by the valve supporting surface 1338b.

[0141] In addition, a valve pressure hole 1338c may be formed in the valve support member 1338. The valve pressure hole 1338c may be formed to pass through the inner side surface of the valve support member 1338 constituting the inner peripheral surface 133b of the cylinder 133 of the valve support member 1338 and the valve support surface 1336a. Thus, during the compression stroke, if the pressure in the compression space V and / or the compression chambers V1, V2, and V3 is greater than the pressure in the injection pipe 54, the injection check valve 1333 is quickly closed, thereby suppressing compression loss.

[0142] In this case, the cross-sectional area of ​​the valve pressure applying hole 1338c may be formed to be smaller than or equal to the cross-sectional area of ​​the injection channel 1332. Thus, the dead volume generated by the valve pressure applying hole 1338c can be minimized.

[0143] Reference Fig.10The valve receiving groove 1337 can be formed to be recessed from the outer peripheral surface 133a of the cylinder 133 to the inner peripheral surface 133b by a predetermined depth, and the valve support member 1338 is inserted into the valve receiving groove 1337 and fixes the injection check valve 1333. The valve receiving groove 1337 and the valve support member 1338 of this embodiment can be the same as the aforementioned Fig. 9 The valve receiving groove 1337 and the valve support member 1338 of the embodiment are similar.

[0144] However, in this embodiment, the valve fixing surface 1337a may be formed flat on one side of the valve receiving groove 1337, and the valve support surface 1337b may be formed in a curved surface on the other side of the valve receiving groove 1337. In this case, the inner side surface of the valve support member 1338 facing the valve support surface 1337b may be formed flat. Thus, in this embodiment, the injection check valve 1333 may rotate in a state fixed to the valve fixing surface 1337a provided in the valve receiving groove 1337, and the valve support surface 1337b may be used to limit the opening.

[0145] In addition, in the present embodiment, the injection passage 1332 may be formed to penetrate from one end of the valve receiving groove 1337, that is, one side of the valve support surface 1337b toward the inner circumferential surface of the cylinder 133, and the valve support member 1338 may be formed with an injection hole 1338d for inserting the injection pipe 54. Thus, the refrigerant flowing into the interior of the valve receiving groove 1337 through the injection hole 1338d may be injected into the compression space V through the injection passage 1332.

[0146] In addition, in the present embodiment, a valve pressure hole 1337c may be formed between the inner circumferential surface of the cylinder 133 and the valve support surface 1337b of the valve receiving groove 1337. Thus, during the compression stroke, if the pressure in the compression chambers V1, V2, and V3 is greater than the pressure in the injection pipe 54, the injection check valve 1333 is quickly closed, thereby suppressing compression loss.

[0147] In this case, the cross-sectional area of ​​the valve pressure hole 1337c may also be formed to be smaller than or equal to the cross-sectional area of ​​the injection channel 1332. Thus, the dead volume generated by the valve pressure hole 1337c can be minimized.

[0148] Although not shown, the valve receiving groove 1337 may be formed in the main bearing 131 and / or the auxiliary bearing 132. In other words, the valve receiving groove 1337 is formed in the outer side surface or the inner side surface of the main bearing 131 and / or the auxiliary bearing 132, and the injection check valve 1333 constituted by the pilot valve is inserted into the valve receiving groove 1337, and the opening degree is restricted while being fixed by the valve support member 1338. In these cases, the valve receiving groove 1337 and the valve support member 1338 may also be formed in the same or substantially similar manner as the aforementioned embodiment, and therefore, the description thereof is replaced by the description of the aforementioned embodiment.

[0149] Next, other embodiments of the injection channel will be described.

[0150] That is, in the aforementioned embodiment, the injection channel is composed of one hole, but depending on the situation, the injection channel may also be composed of a plurality of holes.

[0151] Fig.11 is a cross-sectional view showing another embodiment of the injection channel, Fig.12 is along Fig.11 Sectional view taken along line “XX”.

[0152] Re-reference Figure 1 and Figure 5 The basic structure and effects of the refrigeration cycle device 1 with the injection portion 50 and the rotary compressor 10 used in the refrigeration cycle device 1 of this embodiment are similar to those of the aforementioned embodiments. For example, in the cylinder 133 of the rotary compressor 10, an injection channel 1332 with a circular cross-sectional shape is formed from the outer peripheral surface of the cylinder 133 to the inner peripheral surface, and the injection channel 1332 can be formed around the compression start angle θ of the corresponding compression chambers V1, V2, and V3. For example, it can be formed in the range of the compression start angle θ to the compression start angle θ plus the value obtained by dividing 360° by the number of blades 135, that is, the maximum angle. In addition, the circumferential width of the injection channel 1332 can be formed to be 0.4 to 0.8 times the thickness T of the blade 135. In this case, the injection channel 1332 can be formed to be located in the range of the compression start angle θ to the compression start angle θ plus 20°. In addition, injection control valves 55a and 55b are provided in the injection pipe 54 connected to the injection passage 1332. The injection control valves 55a and 55b can control the pressure of the refrigerant injected into the corresponding compression chambers V1, V2, and V3 to be approximately 0.4 to 0.7 times the discharge pressure of the refrigerant discharged from the corresponding compression chambers V1, V2, and V3. The description of the position and specification of such an injection passage 1332 is replaced by the description of the aforementioned embodiment.

[0153] It should be noted that, in this embodiment, the outlet of the injection channel 1332 may be branched into a plurality of holes and pass through the inner circumferential surface of the cylinder 133. Thus, the actual size of the injection channel 1332 may be increased while the position and specifications of the injection channel 1332 are the same as those of the aforementioned embodiment.

[0154] Reference Fig.11 and Fig.12 The injection channel 1332 of this embodiment may include an injection inlet 1332a and a plurality of injection outlets 1332b. The injection inlet 1332a is a portion connected to the injection pipe 54, and the injection outlet 1332b is a portion connected to the corresponding compression chamber V.

[0155] The injection inlet 1332a may be formed by being recessed by a predetermined depth from the outer circumferential surface of the cylinder 133 toward the inner circumferential surface of the cylinder 133. In other words, the injection inlet 1332a may be formed by being recessed by a predetermined depth in the radial direction from the outer circumferential surface 133a toward the inner circumferential surface 133b of the cylinder 133. Thus, by minimizing the length of the injection inlet 1332a, the injection speed can be increased.

[0156] The jet outlet 1332b may be formed to be connected to both sides from the inner end of the jet inlet 1332a, and to penetrate the inner circumferential surface of the cylinder 133 on both sides in the axial direction. In this case, the jet outlet 1332b may be connected by bending vertically or by being connected obliquely. In this embodiment, an example in which the jet outlet 1332b is connected vertically from the jet inlet 1332a is shown.

[0157] As described above, when there are multiple injection outlets 1332b, the size (inner diameter) D of one injection outlet 1332b is formed to be the same as the inner diameter D of the injection outlet 1332b in the aforementioned embodiment, and substantially, the inner diameter D of the injection outlet 1332b can be formed to be twice that of the injection outlet 1332b in the aforementioned embodiment. Thus, during the injection operation, the refrigerant flow rate injected into the compression space V can be increased to improve the compression efficiency.

[0158] In addition, if there are multiple injection outlets 1332b, the width of the injection outlet 1332b in the circumferential direction can be reduced under the condition that the total cross-sectional area of ​​the injection outlet 1332b is the same. Therefore, when multiple discharge outlets 1313 are used, the interval of communication between the first discharge outlet 1313a located upstream with respect to the rotation direction of the roller 134 and the injection channel 1332 is reduced, so that the backflow of the refrigerant compressed through the injection channel 1332 can be effectively suppressed accordingly.

[0159] In addition, when there are a plurality of injection outlets 1332b, the area (circumferential width) of each injection outlet 1332b is reduced, and accordingly, the starting point of the injection channel 1332 can be located at a relatively far position from the compression start angle θ. As a result, the sealing distance of the injection channel 1332 is increased, so that even if the front surface 135a of the blade 135 facing the inner circumferential surface of the cylinder 133 is formed as a curved surface, the possibility of leakage between the compression chambers V can be reduced.

[0160] Next, another embodiment of the injection channel will be described.

[0161] That is, in the aforementioned embodiment, the injection channel is formed in a circular cross-sectional shape, but depending on circumstances, the injection channel may also be formed in a non-circular cross-sectional shape.

[0162] Fig.13is a cross-sectional view showing another embodiment of the injection channel, Fig.14 is along Fig.13 A cross-sectional view taken along the line “XI-XI”.

[0163] Re-reference Figure 1 and Figure 5 The basic structure and effects of the refrigeration cycle device 1 with the injection portion 50 and the rotary compressor 10 used in the refrigeration cycle device 1 of this embodiment are similar to those of the aforementioned embodiments. For example, in the cylinder 133 of the rotary compressor 10, the injection channel 1332 is formed by penetrating from the outer peripheral surface of the cylinder 133 to the inner peripheral surface, and the injection channel 1332 can be formed around the compression start angle θ of the corresponding compression chamber V, for example, it can be formed in the range of the compression start angle θ to the compression start angle θ plus the value obtained by dividing 360° by the number of blades 135, that is, the maximum angle. In addition, the circumferential width D1 of the injection channel 1332 can be formed to be 0.4 to 0.8 times the thickness T of the blade 135. In this case, the injection channel 1332 can be formed to be located in the range of the compression start angle θ to the compression start angle θ plus 20°. In addition, injection control valves 55a and 55b are provided in the injection section 50 connected to the injection passage 1332. The injection control valves 55a and 55b can control the pressure of the refrigerant injected into the corresponding compression chambers V1, V2, and V3 to 0.4 to 0.7 times the discharge pressure of the refrigerant discharged from the corresponding compression chambers V1, V2, and V3. The description of the position and specification of such an injection passage 1332 is replaced by the description of the aforementioned embodiment.

[0164] It should be noted that, in this embodiment, Fig.13 and Fig.14 , the injection channel 1332 can be formed into a non-circular cross section, for example, an elliptical cross section or a long hole shape. In other words, the injection channel 1332 can be formed into an elliptical cross section or a long hole shape in which the axial length L1 is greater than the circumferential length L2. Thus, when the position and specifications of the injection channel 1332 are the same as those in the aforementioned embodiment, the actual size of the injection channel 1332 can be increased.

[0165] As described above, when the injection channel 1332 is formed into an ellipse or a long hole shape that is long in the axial direction, the actual size (cross-sectional area) of the injection channel 1332 can be increased compared to the injection channel 1332 of the aforementioned embodiment. As a result, the refrigerant flow rate injected into the compression chamber V can be increased during the injection operation to improve the compression efficiency.

[0166] In addition, when the injection channel 1332 is formed in an ellipse or an elongated hole shape that is long in the axial direction, the circumferential width of the injection channel 1332 can be reduced while maintaining the same total cross-sectional area of ​​the injection channel 1332. Therefore, when a plurality of discharge ports 1313 are used, for example, the interval in which the first discharge port 1313a located on the upstream side with respect to the rotation direction of the roller 134 communicates with the injection channel 1332 is reduced, so that the backflow of the refrigerant compressed through the injection channel 1332 can be minimized.

[0167] In addition, when the injection channel 1332 is formed into an ellipse or an elongated hole shape that is long in the axial direction, the circumferential width of the injection channel 1332 is reduced, and accordingly, the starting point of the injection channel 1332 can be located at a relatively far position from the compression start angle θ. As a result, the sealing distance of the injection channel 1332 is expanded, so that even if the front surface 135a of the blade 135 facing the inner peripheral surface of the cylinder 133 is formed into a curved surface, the possibility of leakage between the compression chambers can be reduced.

[0168] Next, another embodiment of the injection channel will be described.

[0169] That is, in the aforementioned embodiment, the injection passage is formed in the cylinder tube, but depending on circumstances, the injection passage may also be formed in the main bearing.

[0170] Fig.15 is a cross-sectional view showing another embodiment of the injection channel, Fig.16 and Fig.17 is along Fig.15 Cross-sectional view taken along line “XII-XII”.

[0171] Re-reference Figure 1 and Figure 5The basic structure and effects of the refrigeration cycle device 1 with the injection portion 50 and the rotary compressor 10 used in the refrigeration cycle device 1 of this embodiment are similar to those of the aforementioned embodiments. For example, in the rotary compressor 10, the injection channel 1332 can be formed around the compression start angle θ of the corresponding compression chamber V, for example, it can be formed in the range of the compression start angle θ to the compression start angle θ plus the value obtained by dividing 360° by the number of blades 135, that is, the maximum angle. In addition, the circumferential width D1 of the injection channel 1332 can be formed to be 0.4 to 0.8 times the thickness T of the blade 135. In this case, the injection channel 1332 can be formed to be located in the range of the compression start angle θ to the compression start angle θ plus 20°. In addition, injection control valves 55a and 55b are provided in the injection section 50 connected to the injection passage 1332. The injection control valves 55a and 55b can control the pressure of the refrigerant injected into the corresponding compression chambers V1, V2, and V3 to 0.4 to 0.7 times the discharge pressure of the refrigerant discharged from the corresponding compression chambers V1, V2, and V3. The description of the position and specification of such an injection passage 1332 is replaced by the description of the aforementioned embodiment.

[0172] It should be noted that, in this embodiment, the injection channel 1332 may be formed by penetrating the main bearing 131. For example, the injection channel 1332 may include an injection inlet 1332a and an injection outlet 1332b. The injection inlet 1332a is a portion connected to the injection pipe 54, and the injection outlet 1332b is a portion connected to the compression space V.

[0173] Reference Figures 15 to 17 In this embodiment, the injection inlet 1332a can be recessed from the outer circumferential surface of the main bearing 131 to the inner circumferential surface of the main bearing 131 by a predetermined depth, and the injection outlet 1332b can be connected to the injection inlet 1332a and pass through the main sliding surface 1311a toward the compression chambers V1, V2, and V3. In other words, the injection inlet 1332a can be formed in the radial direction, and the injection outlet 1332b can be bent at the inner side end of the injection inlet 1332a and formed in the axial direction. As a result, the injection inlet 1332a is connected to the inner circumferential surface of the housing 110, so that the injection pipe 54 can be easily combined with the injection channel 1332, and the injection channel 1332 and the injection pipe 54 can also be tightly sealed.

[0174] In this case, the ejection outlet 1332b may be formed in a circular shape or in a non-circular shape. When the ejection outlet 1332b is formed in a circular shape, it can be easily processed. Fig.16As shown, the injection outlet 1332b can be formed in a non-circular shape, for example, the radial length L3 of the injection outlet 1332b is greater than the circumferential length L2. Thus, when the position and specification of the injection channel 1332 are the same, the actual size of the injection outlet 1332b connected to the compression chambers V1, V2, and V3 can be increased.

[0175] In addition, in this case, the jet outlet 1332b may extend in the axial direction or in a direction inclined relative to the axial direction. In the case where the jet outlet 1332b extends in the axial direction, the jet channel 1332 may be easily processed and the length of the jet channel 1332 may be minimized. Fig.17 As shown, the injection outlet 1332b may also be formed to extend long in the direction in which the blade 135 is inclined. In other words, when the blade 135 is axially projected, the blade 135 may be formed to be inclined at a predetermined angle relative to the radial direction based on the rotation center of the roller 134, and when the injection outlet 1332b is axially projected, the injection outlet 1332b may be formed to be inclined at the same angle as the angle of inclination of the blade 135 relative to the radial direction. Thus, when the position and specification of the injection channel 1332 are the same, the actual size of the injection outlet 1332b connected to the compression chambers V1, V2, and V3 can be increased.

[0176] As described above, when the injection passage 1332 is formed in the main bearing 131, the injected refrigerant is pressed toward the axial side of the blade 135 physically supported by the sub-bearing 132, so as not to significantly affect the reciprocating motion of the blade 135. Thus, during the injection operation, the movement of the blade 135 is stabilized, thereby being able to improve the compressor performance.

[0177] When the injection passage 1332 is formed in the main bearing 131, a large supporting area can be ensured between the front surface 135a of the vane 135 and the inner peripheral surface 133b of the cylinder 133 facing the front surface 135a. This can improve reliability by suppressing an increase in surface pressure between the vane 135 and the cylinder 133.

[0178] In addition, when the injection passage 1332 is formed in the main bearing 131, the axial side surface 135c of the vane 135 is formed into a flat surface, so that not only a large sealing area can be ensured, but also the contact state between the vane 135 and the main bearing 131 can be continuously maintained. Therefore, compared with the cylinder injection structure as in the above-mentioned embodiment, the leakage between the compression chambers V1, V2, and V3 can be effectively suppressed.

[0179] Although not shown, the injection passage 1332 may be formed obliquely from the outer peripheral surface of the main bearing 131 toward the main sliding surface 1311a, or may be formed axially through the main plate portion 1311 of the main bearing 131. In these cases, the injection passage 1332 is formed linearly, which can simplify processing accordingly.

[0180] Next, another embodiment of the injection channel will be described.

[0181] That is, in the aforementioned embodiment, the injection channel is formed in the main bearing, but it may be formed in the auxiliary bearing depending on circumstances.

[0182] Fig.18 and Fig.19 is a cross-sectional view showing still another embodiment of the injection channel.

[0183] Re-reference Figure 1 and Figure 5 The basic structure and effects of the refrigeration cycle device 1 with the injection portion 50 and the rotary compressor 10 used in the refrigeration cycle device 1 of this embodiment are similar to those of the aforementioned embodiments. For example, in the rotary compressor 10, the injection channel 1332 can be formed around the compression start angle θ of the corresponding compression chambers V1, V2, and V3. For example, it can be formed in the range of the compression start angle θ to the compression start angle θ plus the value obtained by dividing 360° by the number of blades 135, that is, the maximum angle. In addition, the circumferential width D1 of the injection channel 1332 can be formed to be 0.4 to 0.8 times the thickness T of the blade 135. In this case, the injection channel 1332 can be formed to be located in the range of the compression start angle θ to the compression start angle θ plus 20°. In addition, injection control valves 55a and 55b are provided in the injection section 50 connected to the injection passage 1332. The injection control valves 55a and 55b can control the pressure of the refrigerant injected into the corresponding compression chambers V1, V2, and V3 to 0.4 to 0.7 times the discharge pressure of the refrigerant discharged from the corresponding compression chambers V1, V2, and V3. The description of the position and specification of such an injection passage 1332 is replaced by the description of the aforementioned embodiment.

[0184] It should be noted that, in this embodiment, the injection channel 1332 may be formed by penetrating the auxiliary bearing 132. For example, the injection channel 1332 may include an injection inlet 1332a and an injection outlet 1332b. The injection inlet 1332a is a portion connected to the injection pipe 54, and the injection outlet 1332b is a portion connected to the compression space V.

[0185] Reference Fig.18In this embodiment, the injection inlet 1332a may be recessed from the outer circumferential surface of the auxiliary bearing 132 toward the inner circumferential surface of the auxiliary bearing 132 by a predetermined depth, and the injection outlet 1332b may be communicated with the injection inlet 1332a and pass through the auxiliary sliding surface 1321a toward the compression space V. In other words, the injection inlet 1332a may be formed in the radial direction, and the injection outlet 1332b may be bent at the inner side end of the injection inlet 1332a and formed in the axial direction.

[0186] In this case, the jet outlet 1332 b may be formed in a circular shape or in a long hole shape that is long in the radial direction, or may be formed in the radial direction or may be formed to be inclined with respect to the radial direction in accordance with the blade 135 .

[0187] As described above, when the injection channel 1332 is formed in the auxiliary bearing 132, its effect is the same as that of the aforementioned Fig.15 The embodiment is similar to the main bearing 131, so the above Fig.15 The description of the embodiments will be used instead of the description thereof.

[0188] It should be noted that, since the auxiliary bearing 132 has a simple structure compared to the main bearing 131 formed with the first discharge port 1313a and the second discharge port 1313b, it is possible to easily secure not only a space for forming the injection channel 1332 but also a space for connecting the injection pipe 54 in the injection channel 1332. Therefore, compared with the case where the injection channel 1332 is formed in the main bearing 131, it is possible to easily process the injection channel 1332 and also to easily connect the injection pipe 54 to the injection channel 1332.

[0189] In addition, refer to Fig.19 The injection channel 1332 may also be formed in the auxiliary bearing 132 and penetrate the axial side surfaces of the auxiliary bearing 132. In this case, the injection pipe 54 may penetrate the housing 110 in the radial direction and be bent in the axial direction inside the housing 110. For example, the injection pipe 54 may be bent along a curve and inserted into the injection channel 1332. Thus, the injection channel 1332 can be further easily processed by making the injection channel 1332 as short as possible.

[0190] In addition, when the injection passage 1332 is formed in the axial direction of the auxiliary bearing 132, the injection pipe 54 can be immersed in the oil stored in the housing 110. As a result, the injection pipe 54 is heated, so that a part of the liquid refrigerant injected through the injection pipe 54 evaporates, and the liquid refrigerant flowing into the compression space V can be reduced.

[0191] Next, another embodiment of the injection channel will be described.

[0192] That is, in some of the above-mentioned embodiments, the injection passage is formed in any one of the cylinder tube, the main bearing, and the auxiliary bearing, but depending on circumstances, the injection passage may be formed in both the main bearing and the auxiliary bearing.

[0193] Fig. 20 is a cross-sectional view showing still another embodiment of the injection channel.

[0194] Re-reference Figure 1 and Figure 5 The basic structure and effects of the refrigeration cycle device 1 with the injection portion 50 and the rotary compressor 10 used in the refrigeration cycle device 1 of this embodiment are similar to those of the aforementioned embodiments. For example, in the rotary compressor 10, the injection channel 1332 can be formed around the compression start angle θ of the corresponding compression chambers V1, V2, and V3. For example, it can be formed in the range of the compression start angle θ to the compression start angle θ plus the value obtained by dividing 360° by the number of blades 135, that is, the maximum angle. In addition, the circumferential width D1 of the injection channel 1332 can be formed to be 0.4 to 0.8 times the thickness T of the blade 135. In this case, the injection channel 1332 can be formed to be located in the range of the compression start angle θ to the compression start angle θ plus 20°. In addition, injection control valves 55a and 55b are provided in the injection section 50 connected to the injection passage 1332. The injection control valves 55a and 55b can control the pressure of the refrigerant injected into the corresponding compression chambers V1, V2, and V3 to 0.4 to 0.7 times the discharge pressure of the refrigerant discharged from the corresponding compression chambers V1, V2, and V3. The description of the position and specification of such an injection passage 1332 is replaced by the description of the aforementioned embodiment.

[0195] It should be noted that, in this embodiment, Fig. 20 As shown, the injection channel 1332 can be formed by passing through the main bearing 131 and the secondary bearing 132. For example, the injection channel 1332 may include a first injection channel 1335a and a second injection channel 1335b. The first injection channel 1335a can be formed by passing through the main bearing 131, and the second injection channel 1335b can be formed by passing through the secondary bearing 132. In this case, the first injection channel 1335a and the second injection channel 1335b can be formed by connecting to each other, or they can be formed independently. In this embodiment, an example in which the first injection channel 1335a and the second injection channel 1335b are connected to each other is shown.

[0196] Specifically, the first injection channel 1335a is connected to the injection pipe 54, and the second injection channel 1335b can be connected to the middle of the first injection channel 1335a. In other words, the first injection channel 1335a and the second injection channel 1335b can be connected to each other using the injection connection channel 1335c. In this case, the injection connection channel 1335c can be formed by passing through the interior of the cylinder 133, or it can be exposed to the outside of the cylinder 133. In the former case, the injection channel 1332 can be stably sealed, and in the latter case, the thickness of the cylinder 133 can be largely ensured, thereby suppressing the deformation of the cylinder 133. In this embodiment, an example in which the injection connection channel 1335c passes through the interior of the cylinder 133 is shown.

[0197] For example, the first injection passage 1335a may include: a first injection inlet 1335a1 that is recessed in the radial direction from the outer peripheral surface of the main bearing 131; and a first injection outlet 1335a2 that passes from the first injection inlet 1335a1 to the main sliding surface 1311a. Thus, while ensuring the sealing area between the main bearing 131 and the cylinder 133, the injection pipe 54 can be easily inserted into the first injection inlet 1335a1 for connection.

[0198] Although not shown, the first injection channel 1335a may be recessed to a predetermined depth from a side surface of the main bearing 131 facing a side surface of the cylinder 133 and extend radially. In this case, as the first injection channel 1335a is formed to the compression space V without bending in the radial direction, the first injection channel 1335a can be easily formed.

[0199] The second injection passage 1335b may include: a second injection inlet 1335b1 that is recessed from one axial side of the auxiliary bearing 132 toward the inner circumferential surface of the auxiliary bearing 132; and a second injection outlet 1335b2 that passes from the second injection inlet 1335b1 to the auxiliary sliding surface 1321a. Thus, the sealing area between the auxiliary bearing 132 and the cylinder 133 can be ensured.

[0200] Although not shown, the second injection channel 1335b may be recessed to a predetermined depth and extend radially from one side surface of the auxiliary bearing 132 facing the other side surface of the cylinder tube 133. In this case, as the second injection channel 1335b is formed to the compression space V without bending in the radial direction, the second injection channel 1335b can be easily formed.

[0201] The injection connection channel 1335c passes through one axial side surface of the cylinder 133 facing the main bearing 131 and the other axial side surface of the cylinder 133 facing the secondary bearing 132, and the first section 1335c1 of the injection connection channel 1335c can be formed to be connected to the middle of the first injection channel 1335a, and the second section 1335c2 of the injection connection channel 1335c can be formed to be connected to the middle or outer end of the second injection channel 1335b. In other words, a first branch channel 1335a3 opening toward one side surface of the cylinder 133 can be formed in the middle of the first injection channel 1335a, and a second branch channel 1335b3 opening toward the other side surface of the cylinder 133 can be formed in the middle or outer end of the second injection channel 1335b, and both ends of the injection connection channel 1335c can be connected to the first branch channel 1335a3 and the second branch channel 1335b3, respectively. Thus, part of the refrigerant flowing into the first injection channel 1335a through the injection pipe 54 moves to the second injection channel 1335b through the injection connection channel 1335c and is sucked into each compression chamber V1, V2, V3. Thus, the entire area of ​​the injection channel 1332 is expanded, thereby improving the injection effect.

Claims

1. A rotary compressor, wherein: include: case; A main bearing and a secondary bearing are arranged in the inner space of the housing; A cylinder barrel is disposed between the main bearing and the auxiliary bearing to form a compression space; a roller rotatably disposed on a rotating shaft in the internal space of the cylinder and eccentrically disposed relative to the center of the compression space so as to have a contact point close to the inner peripheral surface of the cylinder; A plurality of blades are slidably inserted into a plurality of blade grooves provided on the roller and rotate together with the roller to divide the compression space into a plurality of compression chambers; as well as an injection passage for injecting a portion of the refrigerant discharged from the compression space and condensed toward the compression space; The injection passage is provided in at least any one of the main bearing, the sub-bearing, and the cylinder tube, and communicates with the corresponding compression chamber after a compression start angle of the corresponding compression chamber.

2. The rotary compressor according to claim 1, wherein: The injection channel satisfies θ≤the applicable area of ​​the injection channel≤θ+360 / n, Where θ is the compression start angle and n is the number of blades.

3. The rotary compressor according to claim 2, wherein: The circumferential width of the injection channel is formed to be 0.4 to 0.8 times the thickness of the blade.

4. The rotary compressor according to claim 3, wherein: The injection channel communicates with the compression chamber within a range of 20° after the compression start angle based on the rotation direction of the roller.

5. The rotary compressor according to claim 1, wherein: The injection passage is formed to penetrate from the outer peripheral surface of the cylinder to the inner peripheral surface of the cylinder.

6. The rotary compressor according to claim 5, wherein: The injection channel comprises: an injection inlet recessed from the outer circumference of the cylinder to the inner circumference of the cylinder by a predetermined depth; and an injection outlet, which is in communication with the injection inlet and penetrates the inner peripheral surface of the cylinder; A plurality of the ejection outlets are formed and arranged at predetermined intervals in the axial direction.

7. The rotary compressor according to claim 5, wherein: The injection channel is formed such that its axial length is greater than its circumferential length.

8. The rotary compressor according to claim 1, wherein: The injection passage is formed in at least one of the main bearing and the auxiliary bearing.

9. A refrigeration cycle device, comprising a compressor, a condenser, an expander and an evaporator, wherein: The compressor is a rotary compressor as claimed in any one of claims 1 to 8.

10. The refrigeration cycle device according to claim 9, wherein: An injection portion is provided which branches from between the condenser and the expander and is connected to the injection passage, and an injection control valve which selectively opens and closes the injection portion is provided on the injection portion. The injection control valve controls the pressure of the refrigerant injected into the compression chamber to be 0.4 to 0.7 times the discharge pressure of the refrigerant discharged from the compression chamber.

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