Rotary compressor

Abstract

A rotary compressor according to an embodiment of the present invention includes a housing, a cylinder provided in an inner space of the housing to form a compression space, a rotary shaft rotatably penetrating the cylinder, a roller provided in the rotary shaft to be rotatable in an inner space of the cylinder and configured eccentrically with respect to a center of the compression space to have a contact point at which an outer circumferential surface of the roller contacts an inner circumferential surface of the cylinder, a vane slidably inserted into a vane groove provided in the roller to rotate together with the roller, a main bearing and a sub-bearing respectively configured at both axial sides of the cylinder to form the compression space together with the cylinder, and a discharge passage through which a refrigerant is discharged from the compression space to the inner space of the housing, a portion of the discharge passage being formed by penetrating the roller.

Description

TECHNICAL FIELD

[0001] The present application relates to a vane rotary compressor in which a vane is slidably inserted into a rotating roller. BACKGROUND

[0002] Rotary compressors can be classified into a type in which vanes are slidably inserted into a cylinder to contact a roller, and a type in which vanes are slidably inserted into a roller to contact a cylinder. The former is called an eccentric rotary compressor, and the latter is called a vane rotary compressor (or a concentric rotary compressor).

[0003] In the eccentric rotary compressor, the vanes inserted into the cylinder are drawn toward the roller by an elastic force or a back pressure, thereby contacting the outer circumferential surface of the roller. On the other hand, in the vane rotary compressor, the vanes inserted into the roller perform a rotational motion together with the roller, and are drawn toward the cylinder by a centrifugal force and a back pressure, thereby contacting the inner circumferential surface of the cylinder.

[0004] The eccentric rotary compressor independently forms compression chambers corresponding to the number of vanes per one revolution of the roller, and each of the compression chambers simultaneously performs a suction stroke, a compression stroke, and a discharge stroke. On the other hand, the vane rotary compressor continuously forms compression chambers corresponding to the number of vanes per one revolution of the roller, and each of the compression chambers sequentially performs a suction stroke, a compression stroke, and a discharge stroke. Therefore, the vane rotary compressor forms a higher compression ratio than the eccentric rotary compressor. Therefore, the vane rotary compressor is more suitable for use of high-pressure refrigerants such as R32, R410a, CO2, which have low ozone depletion potential (ODP) and global warming potential (GWP).

[0005] Patent Document 1 (US Patent Publication US2014 / 0369878A1), Patent Document 2 (Japanese Patent Publication No. 2000-265984), and Patent Document 3 (Japanese Patent Publication No. 2013-72429) each disclose a vane rotary compressor. These vane rotary compressors provide a contact point at which the outer circumferential surface of the roller and the inner circumferential surface of the cylinder almost contact each other between a discharge port and a suction port, thereby separating the discharge port and the suction port.

[0006] However, in the conventional vane rotary compressor, a gap is generated in the circumferential direction between the discharge port and the contact point, and thus the compressed refrigerant cannot be discharged in full amount in the discharge stroke. A part of the compressed refrigerant can remain in the space between the discharge port and the contact point. The refrigerant flows backward to the compression chamber, thereby possibly causing over-compression, increasing motor input, and reducing compressor efficiency.

[0007] In addition, in the conventional vane rotary compressor, due to over-compression of the residual refrigerant, the pressure of the front side of the vane is excessively increased, thereby generating a shaking phenomenon of the vane, and due to such shaking phenomenon of the vane, not only the vibration noise of the compressor is increased, but also the front side of the vane or the inner circumferential surface of the cylinder can be damaged, thereby possibly reducing the reliability of the compressor.

[0008] In addition, in the conventional vane rotary compressor, as the shaking phenomenon of the vane is continued, the refrigerant in the compression stroke is reversely flowed to the suction stroke side, thereby possibly heating the refrigerant of the suction stroke side. This can cause the specific volume of the suction refrigerant to be increased, generate suction loss as the refrigerant suction amount is reduced, thereby possibly reducing the efficiency of the compressor.

[0009] In addition, in the conventional vane rotary compressor, in the case where the discharge port is formed in the cylinder, while the surface pressure between the front side of the vane passing through the discharge port and the inner circumferential surface of the cylinder is increased, the surface pressure is not constantly formed, so that the front side of the vane or the inner circumferential surface of the cylinder can be damaged. At the same time, as the valve receiving groove is formed in the outer circumferential surface of the cylinder, the machining of the cylinder becomes complicated, thereby increasing the manufacturing cost, and due to the structure of the valve receiving groove, the rigidity of the cylinder is reduced, the shaking phenomenon of the vane is increased, thereby possibly aggravating the vibration noise of the compressor. SUMMARY

[0010] An object of the present application is to provide a rotary compressor capable of reducing the amount of refrigerant remaining in a compression space without being discharged.

[0011] Further, an object of the present application is to provide a rotary compressor capable of reducing the amount of refrigerant remaining in a compression space while suppressing the situation where refrigerant is leaked during a compression stroke.

[0012] Still further, an object of the present application is to provide a rotary compressor capable of periodically communicating a residual space with an inner space of a housing.

[0013] Another object of the present application is to provide a rotary compressor capable of rapidly discharging refrigerant during a discharge stroke.

[0014] Further, an object of the present application is to provide a rotary compressor capable of increasing the amount of refrigerant discharged by increasing the effective area of discharge of refrigerant.

[0015] Still further, an object of the present application is to provide a rotary compressor capable of extending an actual discharge stroke for a long time.

[0016] Another object of the present application is to provide a rotary compressor capable of suppressing the damage of a vane or a cylinder while reducing the vibration noise of the compressor.

[0017] Further, an object of the present application is to provide a rotary compressor capable of eliminating the difference between the pressure acting on the front side of the vane and the back pressure acting on the rear side of the vane.

[0018] Still further, an object of the present application is to provide a rotary compressor capable of uniformizing the pressure acting on the front side of the vane.

[0019] Another object of the present application is to provide a rotary compressor capable of suppressing the shaking phenomenon of the vane even in the case of using a high-pressure refrigerant such as R32, R410a, CO2.

[0020] To achieve the object of the present application, a rotary compressor can include a housing, a cylinder, a roller, a vane, a main bearing, a sub bearing, and a discharge passage. The housing has a sealed internal space. The cylinder is provided in the internal space of the housing to form a compression space. The roller is provided on a rotation shaft to be rotatable in the inside of the cylinder, and is eccentrically disposed with respect to the center of the compression space to have a contact point at which the outer circumferential surface of the roller contacts the inner circumferential surface of the cylinder. The vane is slidably inserted into a vane groove provided on the roller to rotate together with the roller. The main bearing and the sub bearing are respectively disposed on both sides of the cylinder in the axial direction to form the compression space together with the cylinder. A part of the discharge passage can be formed by penetrating the roller. Therefore, depending on the rotation angle of the roller, the residual space after the discharge stroke or the compression space in the discharge stroke can be periodically communicated with the internal space of the housing. Thereby, the structure of the cylinder is simplified to facilitate the machining, and the surface pressure between the vane and the cylinder around the discharge hole is reduced and the shaking phenomenon of the vane is reduced, so that the wear and the vibration noise between the vane and the cylinder can be suppressed. In addition, the amount of refrigerant remaining in the compression space can be reduced by discharging the refrigerant remaining in the residual space or rapidly discharging the refrigerant in the discharge stroke. In addition, by reducing the front and rear pressures of the vane, the wear and the vibration noise caused by the shaking phenomenon of the vane can be reduced.

[0021] For example, the discharge passage can be periodically opened as the roller rotates. Thereby, while the refrigerant after the discharge stroke or in the discharge stroke is periodically discharged, the refrigerant before the discharge stroke is prevented from being discharged in advance, so that the under-compression can be prevented.

[0022] In addition, the discharge passage can be provided with a plurality of passages at equal intervals in the circumferential direction of the roller. Thereby, the discharge passages are opened at the same rotation angle, so that the refrigerant can be periodically discharged at equal intervals after the discharge stroke or in the discharge stroke.

[0023] In addition, the roller can be formed with a plurality of vane grooves in a circumferential direction. A portion of the discharge passage can be formed between the plurality of vane grooves, respectively. Thus, the refrigerant compressed in each compression chamber can be periodically discharged through each back pressure passage according to a rotation angle of the roller.

[0024] In addition, to achieve the object of the present application, a rotary compressor can include a housing, a cylinder, a roller, a vane, a main bearing, a sub bearing, and a discharge passage. The housing has a sealed internal space. The cylinder is provided in the internal space of the housing to form a compression space. The roller is provided on a rotation shaft to be rotatable in the inside of the cylinder and is eccentrically disposed with respect to a center of the compression space to have a contact point at which an outer circumferential surface of the roller contacts an inner circumferential surface of the cylinder. The vane is slidably inserted into a vane groove provided on the roller to rotate together with the roller. The main bearing and the sub bearing are disposed on both sides of the cylinder in an axial direction to form the compression space together with the cylinder. The discharge passage includes a first discharge guide portion, a second discharge guide portion, and a third discharge guide portion to discharge the refrigerant from the compression space to the internal space of the housing. The first discharge guide portion is provided in one of the main bearing and the sub bearing. The second discharge guide portion can pass through between both ends of the roller in the axial direction and can communicate with the first discharge guide portion. The third discharge guide portion is provided in the other of the main bearing and the sub bearing and can communicate with the first discharge guide portion through the second discharge guide portion. Thus, the refrigerant remaining in a discharge residual space is discharged while reducing the refrigerant remaining in the compression space, and the compressed refrigerant is rapidly discharged while substantially expanding a discharge effective area, the amount of the refrigerant remaining can be reduced, and the compression efficiency can be improved. In addition, by eliminating a pressure difference acting on a front surface of the vane to suppress vane hunting, the wear of the vane or the cylinder can be reduced. In addition, as the discharge passage is periodically opened, the leakage of the refrigerant during a compression stroke can be suppressed, and thus, the occurrence of insufficient compression can be prevented.

[0025] As an example, the second discharge guide portion can periodically communicate with the first discharge guide portion. Thus, while reducing the amount of the refrigerant remaining, the leakage of the compressed refrigerant can be suppressed.

[0026] As another example, the second discharge guide portion can periodically communicate with the third discharge guide portion. Thus, while reducing the amount of the refrigerant remaining, the leakage of the compressed refrigerant can be suppressed.

[0027] As another example, the first discharge guide portion can periodically communicate with the second discharge guide portion and the third discharge guide portion through the second discharge guide portion as the roller rotates. Thus, while reducing the amount of the refrigerant remaining, the leakage of the compressed refrigerant can be suppressed.

[0028] As another example, the number of the second discharge guide portions can be more than the number of the first discharge guide portions or the number of the third discharge guide portions. Thereby, while smoothly discharging the refrigerant of the residual space, the leakage of the refrigerant being compressed can be suppressed.

[0029] Specifically, the first discharge guide portion and the third discharge guide portion can be respectively provided with one. The second discharge guide portion can be provided with a plurality, and can be formed at a predetermined interval in the circumferential direction. Thereby, the discharge passage discharging the residual refrigerant is opened once per one rotation of the roller, and is periodically opened in the residual space communicating with the final compression chamber.

[0030] In addition, the first discharge guide portion and the third discharge guide portion facing the second discharge guide portion can be formed on the same axis. The second discharge guide portion can be penetrated in the axial direction. Thereby, while minimizing the length of the second discharge guide portion to easily process the second discharge guide portion, the residual refrigerant can be rapidly discharged.

[0031] In addition, the first discharge guide portion and the third discharge guide portion facing the second discharge guide portion can be formed on different axes from each other. The second discharge guide portion can be obliquely penetrated with respect to the axial direction. Thereby, while easily processing the first discharge guide portion, the design freedom of the first discharge guide portion can be improved. In addition, as the second discharge guide portion is obliquely formed, the centrifugal force of the refrigerant passing through the second discharge guide portion increases, so that it can be more rapidly discharged from the residual space or the compression space in the discharge stroke.

[0032] As another example, the first discharge guide portion can include a first guide groove communicating with the compression space, and a second guide groove having one end communicating with the first guide groove and the other end communicating with the second discharge guide portion. The second guide groove can extend closer to the rotation center of the roller than the first guide groove. Thereby, the refrigerant of the residual space can be periodically passed through the roller and discharged to the inner space of the housing.

[0033] Specifically, at least one discharge port can be formed in the main bearing or the auxiliary bearing. At least a portion of the first guide groove can overlap the discharge port in the axial direction. Thereby, the effective discharge area of the refrigerant is enlarged, so that the refrigerant can be rapidly discharged from the compression space or the residual refrigerant can be smoothly discharged.

[0034] More specifically, the first guide groove and the discharge port can overlap in the axial direction by 50% or more. Thereby, the effective discharge area of the refrigerant is further enlarged, so that the refrigerant can be more rapidly discharged from the compression space or the remaining refrigerant can be more smoothly discharged.

[0035] In addition, at least one discharge port can be formed in the main bearing or the auxiliary bearing. The cross-sectional area of the first guide groove can be greater than or equal to the cross-sectional area of the discharge port that overlaps the first guide groove in the axial direction. Thereby, the refrigerant can be more rapidly discharged from the compression space or the remaining refrigerant can be more smoothly discharged.

[0036] In addition, at least one discharge port can be formed in the main bearing or the auxiliary bearing. The first guide groove can be located at a position that is more rearward than the discharge port that overlaps the first guide groove in the axial direction, with reference to the direction of rotation of the roller. Thereby, while effectively discharging the remaining refrigerant remaining in the remaining space after the discharge stroke to improve the compression efficiency, the blade flutter can be suppressed to suppress the wear of the blade or the cylinder.

[0037] For example, the first guide groove can be provided in plural in the circumferential direction, and an intermediate connection groove that connects the plural first guide grooves to each other can be provided between the plural first guide grooves. Thereby, the discharge passage can extend to the circumferential range of the corresponding compression chamber or outside the circumferential range of the corresponding compression chamber, so that the amount of refrigerant remaining can be minimized. Furthermore, since the arc length of the discharge passage is longer than or the same as the arc length of the compression chamber, continuous discharge can be achieved to reduce the pressure pulsation.

[0038] In addition, at least one discharge port can be formed in the main bearing or the auxiliary bearing. The first guide groove can be located at a position that is more forward than the discharge port that overlaps the first guide groove in the axial direction, with reference to the direction of rotation of the roller. Thereby, the effective discharge area of the refrigerant is enlarged to more rapidly discharge the refrigerant from the compression chamber, and the amount of refrigerant moving to the remaining space is reduced, so that the amount of refrigerant remaining can be suppressed.

[0039] For example, at least one discharge port can be formed in the main bearing or the auxiliary bearing. The first guide groove can be located between the plural discharge ports to communicate with the plural discharge ports, respectively. Thereby, the effective discharge area of the discharge port is enlarged, so that the refrigerant can be rapidly discharged from the compression chamber.

[0040] In addition, the side surface of the main bearing and the side surface of the sub bearing facing the roller in the axial direction can be formed with a plurality of back pressure pockets having different pressures from each other, spaced apart from each other in the circumferential direction. The second guide groove can be formed more thinly and longer than the first guide groove, and can be disposed between the circumferences of the plurality of back pressure pockets. Thereby, the discharge passage can pass through the roller and be periodically opened.

[0041] As another example, the vane groove can be formed with a plurality of vane grooves in the circumferential direction. The second discharge guide portion can be respectively disposed between each of the vane grooves adjacent to each other in the circumferential direction. Thereby, the discharge passage is periodically opened, and while reducing the amount of refrigerant remaining, leakage of the compressed refrigerant can be suppressed.

[0042] In addition, at least one of the end portions of the first discharge guide portion and the third discharge guide portion facing both ends of the second discharge guide portion can be formed with an expansion groove having an expanded cross-sectional area. Thereby, the discharge passages communicate with each other, the period of opening is extended, and thus the remaining refrigerant can be more quickly discharged.

[0043] As another example, the side surface of the main bearing and the side surface of the sub bearing facing the roller in the axial direction can be formed with a plurality of back pressure pockets having different pressures from each other, spaced apart from each other in the circumferential direction. The third discharge guide portion can be disposed between the circumferences of the plurality of back pressure pockets. Thereby, the discharge passage is periodically opened, and while reducing the amount of refrigerant remaining, leakage of the compressed refrigerant can be suppressed.

[0044] As another example, the main bearing or the sub bearing can be provided with a discharge muffler accommodating the discharge outlet. The third discharge guide portion can be opened from the outside of the discharge muffler toward the inside space of the housing. Thereby, as the refrigerant is discharged from the outside of the discharge muffler, an increase in the internal pressure of the discharge muffler is suppressed, and thus the discharge valve is quickly opened, and a vortex phenomenon in the discharge space is suppressed, and thus the refrigerant can be more quickly discharged from each discharge outlet.

[0045] Specifically, the main bearing or the sub bearing can include a plate portion combined with the axial side surface of the cylinder, and a boss portion extending in the axial direction from the axial side surface of the plate portion to be penetrated by the rotating shaft. The third discharge guide portion can be opened from the boss portion toward the inside of the housing.

[0046] As another example, the main bearing or the sub bearing can be provided with a discharge muffler accommodating the discharge outlet. The third discharge guide portion can be opened toward the inside space of the discharge muffler. Thereby, the length of the discharge passage provided on the bearing is reduced, and thus the discharge passage can be easily machined.

[0047] Specifically, the main bearing or the sub bearing can include a plate portion combined with an axial side of the cylinder, and a boss portion extending in an axial direction from the plate portion so as to be penetrated by the rotary shaft. The third discharge guide portion can penetrate the plate portion.

[0048] As another example, one of the main bearing and the sub bearing can be provided with a discharge port opened and closed by a discharge valve. The first discharge guide portion can be formed in the other of the main bearing and the sub bearing. Thereby, the refrigerant remaining in the compression space is periodically discharged, and at the same time, the amount of the remaining refrigerant is reduced, and compression deficiency can be prevented. BRIEF DESCRIPTION OF DRAWINGS

[0049] Figure 1 is a sectional view showing an embodiment of a vane rotary compressor according to the present application.

[0050] Figure 2 is a perspective view showing a part of a compression unit in Figure 1 disassembled.

[0051] Figure 3 is a plan view showing the compression unit in Figure 2 assembled.

[0052] Figure 4 is a perspective view showing the compression unit in Figure 1 disassembled and showing a discharge passage.

[0053] Figure 5 is a perspective view showing the compression unit in Figure 4 assembled and showing a discharge passage.

[0054] Figure 6 is a sectional view showing a discharge passage in Figure 5 .

[0055] Figure 7 is a schematic view for explaining a position of a first discharge guide portion in the vane rotary compressor in Figure 1 .

[0056] Figures 8A to 8C is a schematic view showing a process of discharging a remaining refrigerant through a discharge passage of the present embodiment.

[0057] Figure 9 is a plan view showing another embodiment of a discharge passage.

[0058] Figure 10 is a plan view showing still another embodiment of a discharge passage.

[0059] Figure 11 is a plan view showing still another embodiment of a discharge passage.

[0060] Figure 12 is a perspective view showing another embodiment of the discharge passage.

[0061] Figure 13 is a sectional view of Figure 12 .

[0062] Figure 14 is an exploded perspective view showing another embodiment of the discharge passage.

[0063] Figure 15 is a sectional view of Figure 14 .

[0064] Figure 16 is a schematic view showing a state in which the discharge passage of Figure 14 is open.

[0065] Figure 17 and Figure 18 are a perspective view and a sectional view showing another embodiment of the discharge passage. DETAILED DESCRIPTION

[0066] Hereinafter, a vane rotary compressor according to the present application will be described in detail with reference to an embodiment shown in the accompanying drawings.

[0067] The present application provides a vane rotary compressor in which a vane spring is provided on a roller. This can be applied to a vane rotary compressor in which a vane is slidably inserted into a roller. For example, this can be applied to a vane rotary compressor having a cylinder in which an inner circumferential surface is formed in a plurality of curvatures, i.e., an asymmetric elliptical shape (hereinafter, referred to as an asymmetric elliptical cylinder), as well as to a vane rotary compressor having a cylinder in which an inner circumferential surface is formed in one curvature, i.e., a circular shape. In addition, this can be applied to a vane rotary compressor in which a vane groove for slidably inserting a vane is formed to be inclined at a predetermined angle with respect to a radial direction of a roller, as well as to a vane rotary compressor in which a vane groove is formed along a radial direction of a roller. Hereinafter, an example in which an inner circumferential surface of a cylinder is formed in an asymmetric elliptical shape and a vane is inclined with respect to a radial direction of a roller will be described as a representative example.

[0068] Figure 1 is a sectional view showing an embodiment of a vane rotary compressor according to the present application, Figure 2 is an exploded perspective view showing a compression unit in Figure 1 , Figure 3 is a plan view showing the compression unit of Figure 2 .

[0069] Referring to Figure 1The vane rotary compressor of the present embodiment includes a housing 110, a driving motor 120, and a compression part 130. The driving motor 120 is provided in an upper side internal space 110a of the housing 110, and the compression part 130 is provided in a lower side internal space 110b of the housing 110. The driving motor 120 and the compression part 130 are connected by a rotating shaft 123.

[0070] The housing 110 is a part that forms the appearance of the compressor, and can be classified into a vertical type or a horizontal type according to the installation state of the compressor. The vertical type is a structure in which the driving motor 120 and the compression part 130 are arranged on the upper and lower sides in the axial direction, and the horizontal type is a structure in which the driving motor 120 and the compression part 130 are arranged on the left and right sides. The housing of the present embodiment is described mainly with reference to the vertical type.

[0071] The housing 110 includes a middle case 111 formed in a cylindrical shape, a lower case 112 covering the lower end of the middle case 111, and an upper case 113 covering the upper end of the middle case 111.

[0072] The driving motor 120 and the compression part 130 are inserted and fixedly coupled to the middle case 111, and a suction pipe 115 can be penetrated through the middle case 111 to be directly connected to the compression part 130. The lower case 112 is sealingly coupled to the lower end of the middle case 111, and an oil storage space 110b can be formed on the lower side of the compression part 130, in which oil to be supplied to the compression part 130 is stored. The upper case 113 is sealingly coupled to the upper end of the middle case 111, and an oil separation space 110c can be formed on the upper side of the driving motor 120 to separate oil from refrigerant discharged from the compression part 130.

[0073] The driving motor 120 is a part that constitutes an electric part, and provides power to drive the compression part 130. The driving motor 120 includes a stator 121, a rotor 122, and a rotating shaft 123.

[0074] The stator 121 is fixedly provided in the inside of the housing 110, and is fixed by being pressed into the inner circumferential surface of the housing 110, such as by shrink fitting. For example, the stator 121 can be fixed by being pressed into the inner circumferential surface of the middle case 111.

[0075] The rotor 122 is rotatably inserted into the inside of the stator 121, and the rotating shaft 123 can be pressed into the center of the rotor 122 and coupled. Accordingly, the rotating shaft 123 will perform concentric rotation with the rotor 122.

[0076] An oil flow path 125 is formed in a hollow hole shape in the center of the rotation shaft 123, and oil through holes 126a, 126b are formed penetrating the outer circumferential surface of the rotation shaft 123 in the middle of the oil flow path 125. The oil through holes 126a, 126b are composed of a first oil through hole 126a belonging to the range of the main bush portion 1312 described later and a second oil through hole 126b belonging to the range of the sub bush portion 1322. The first oil through hole 126a and the second oil through hole 126b can each be formed with one or a plurality of holes. The present embodiment shows an example in which each is formed with a plurality of holes.

[0077] In the middle or lower end of the oil flow path 125, an oil suction device 127 can be provided. The oil suction device 127 can be a gear pump, a viscous pump, a centrifugal pump, or the like. The present embodiment shows an example in which a centrifugal pump is used. Thus, when the rotation shaft 123 rotates, the oil filled in the oil storage space 110b of the housing 110 is pumped by the oil suction device 127, and the oil can be sucked upward along the oil flow path 125, and then supplied to the sub bearing surface 1322b of the sub bush portion 1322 through the second oil through hole 126b and to the main bearing surface 1312b of the main bush portion 1312 through the first oil through hole 126a.

[0078] In addition, the rotation shaft 123 can be provided with a roller 134 described later. The roller 134 can extend from the rotation shaft 123 as a single body, or the rotation shaft 123 and the roller 134 can be manufactured separately and then assembled. In the present embodiment, the rotation shaft 123 is inserted into the roller 134 and then assembled, for example, a shaft hole 1341 provided at the center of the roller 134 penetrates in the axial direction, and the rotation shaft 123 can be pressed into the shaft hole 1341 and combined, or can be movably combined in the axial direction with the shaft hole 1341. In the case where the rotation shaft 123 and the roller 134 are movably combined in the axial direction, an anti-rotation portion (not shown) is provided between the rotation shaft 123 and the roller 134, so that the rotation shaft 123 can be constrained in the circumferential direction with respect to the roller 134.

[0079] The compression portion 130 includes a main bearing 131, a sub bearing 132, a cylinder 133, a roller 134, and a plurality of vanes 1351, 1352, 1353. The main bearing 131 and the sub bearing 132 are respectively provided on the upper and lower sides of the cylinder 133, thereby forming a compression space V together with the cylinder 133, the roller 134 is rotatably provided in the compression space V, and the vanes 1351, 1352, 1353 are slidably inserted into the roller 134, thereby dividing the compression space V into a plurality of compression chambers.

[0080] Referring to Figures 1 to 3 The main bearing 131 can be fixedly provided in the middle housing 111 of the housing 110. For example, the main bearing 131 can be inserted and welded in the middle housing 111.

[0081] The main bearing 131 can be closely attached to and combined with the upper end of the cylinder 133. Thus, the main bearing 131 forms the upper side of the compression space V, and supports the upper half of the rotating shaft 123 in the radial direction while supporting the upper surface of the roller 134 in the axial direction.

[0082] The main bearing 131 can 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, and the main bushing portion 1312 extends from the center of the main plate portion 1311 in the axial direction toward the driving motor 120 and supports the upper half of the rotating shaft 123.

[0083] The main plate portion 1311 is formed in a disc shape, and the outer circumferential surface of the main plate portion 1311 can be closely attached to and fixed to the inner circumferential surface of the intermediate housing 111. One or more discharge outlets 1313a, 1313b, 1313c can be formed in the main plate portion 1311, and a plurality of discharge valves 1361, 1362, 1363 that open and close the respective discharge outlets 1313a, 1313b, 1313c can be provided on the upper surface of the main plate portion 1311, and a discharge muffler 137 having a discharge space (not marked) can be provided on the upper side of the main plate portion 1311 to accommodate the discharge outlets 1313a, 1313b, 1313c and the discharge valves 1361, 1362, 1363.

[0084] Thus, as the discharge outlets 1313a, 1313b, 1313c are formed in the main bearing (or the sub bearing) 131 rather than the cylinder 133, the structure of the cylinder 133 can be simplified and the cylinder can be easily machined. At the same time, the face pressure between the front surface of the vane 1351, 1352, 1353 and the inner circumferential surface of the cylinder 133 facing the same is kept constant while being reduced, and the shaking phenomenon of the vane 1351, 1352, 1353 is reduced, so that wear and vibration noise between the front surface of the vane 1351, 1352, 1353 and the inner circumferential surface of the cylinder 133 facing the same can be suppressed. The discharge outlets will be described later.

[0085] In the axial direction both sides of the main plate portion 1311, the lower surface of the main plate portion 1311, i.e., the main sliding surface 1311a, facing the upper surface of the roller 134 can be formed with a first main back pressure pocket 1315a and a second main back pressure pocket 1315b.

[0086] The first main back pressure pocket 1315a and the second main back pressure pocket 1315b can be formed in a circular arc shape and formed at a predetermined interval from each other in the circumferential direction. The inner circumferential surface of the first main back pressure pocket 1315a and the second main back pressure pocket 1315b is formed in a circular shape, and the outer circumferential surface can be formed in an elliptical shape in consideration of the vane groove described later.

[0087] The first main back pressure pocket 1315a and the second main back pressure pocket 1315b can be formed in the outer diameter range of the roller 134. Therefore, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b can be separated from the compression space V. Only, as long as the main sliding surface 1311a, which is the lower surface of the main plate portion 1311, and the upper surface of the roller 134, which faces the main sliding surface 1311a, are not equipped with an additional sealing member therebetween, the first main back pressure pocket 1315a and the second main back pressure pocket 1315b can be finely communicated through the gap between the both side surfaces.

[0088] The first main back pressure pocket 1315a forms a lower pressure than the second main back pressure pocket 1315b, for example, an intermediate pressure between the suction pressure and the discharge pressure. The first main back pressure pocket 1315a can cause the oil (refrigerant oil) to flow into the first main back pressure pocket 1315a through a fine passage between the first main bearing protrusion 1316a described later and the upper surface of the roller 134. The first main back pressure pocket 1315a can be formed in the range of the compression chamber in which the intermediate pressure is constituted in the compression space V. Therefore, the first main back pressure pocket 1315a will maintain the intermediate pressure.

[0089] The second main back pressure pocket 1315b forms a higher pressure than the first main back pressure pocket 1315a, for example, the discharge pressure or an intermediate pressure between the suction pressure and the discharge pressure close to the discharge pressure. The second main back pressure pocket 1315b can cause the oil that has flowed into the main bearing hole 1312a of the main bearing 1312 through the first oil through hole 126a to flow into the second main back pressure pocket 1315b. The second main back pressure pocket 1315b can be formed in the range of the compression chamber in which the discharge pressure is constituted in the compression space V. Therefore, the second main back pressure pocket 1315b will maintain the discharge pressure.

[0090] In addition, on the inner peripheral side of the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, the first main bearing protrusion 1316a and the second main bearing protrusion 1316b can be formed, respectively, so as to extend from the main bearing surface 1312b of the main bushing portion 1312. Therefore, while the first main back pressure pocket 1315a and the second main back pressure pocket 1315b are sealed from the outside, the rotating shaft 123 can be stably supported.

[0091] The first main bearing protrusion 1316a and the second main bearing protrusion 1316b can be formed to the same height, or can be formed to different heights from each other.

[0092] For example, in a case where the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are formed to the same height, an oil communication groove (not shown) or an oil communication hole (not shown) can be formed in the end face of the second main bearing protrusion 1316b to communicate the inner peripheral surface and the outer peripheral surface of the second main bearing protrusion 1316b. Thus, the oil (refrigerant oil) of high pressure, which flows into the inside of the main bearing surface 1312b, can be caused to flow into the second main back pressure pocket 1315b through the oil communication groove (not shown) or the oil communication hole (not shown).

[0093] On the other hand, in a case where the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are formed to different heights from each other, the height of the second main bearing protrusion 1316b can be formed to be lower than the height of the first main bearing protrusion 1316a. Thus, the oil (refrigerant oil) of high pressure, which flows into the inside of the main bearing hole 1312a, can be caused to flow into the second main back pressure pocket 1315b over the second main bearing protrusion 1316b.

[0094] In addition, the main sliding surface 1311a can be formed with a third discharge guide portion 143 that constitutes a part of a residual refrigerant discharge passage 140 described later. The third discharge guide portion 143 can be formed between the first main back pressure pocket 1315a and the second main back pressure pocket 1315b. A first end 143a of the third discharge guide portion 143 can be formed to periodically communicate with a second end 142b of the second discharge guide portion 142 of the roller 134 described later, and a second end 143b of the third discharge guide portion 143 can be formed to penetrate the main bush portion 1312 described later in the axial direction and open to the inside space 110a of the housing 110. The third discharge guide portion 143 will be described later together with the residual refrigerant discharge passage 140.

[0095] In addition, the main bush portion 1312 can be formed in a hollow bush shape, and a first oil groove 1312c can be formed in the inner peripheral surface of the main bearing hole 1312a that constitutes the inner peripheral surface of the main bush portion 1312. The first oil groove 1312c is linear or oblique between the upper and lower ends of the main bush portion 1312, and can communicate with the first oil through hole 126a.

[0096] Referring to Figures 1 to 3 The sub bearing 132 can be in close contact with and coupled to the lower end of the cylinder tube 133. Thus, the sub bearing 132 forms a lower side surface of the compression space V, and supports the lower surface of the roller 134 in the axial direction while supporting the lower half of the rotation shaft 123 in the radial direction.

[0097] The sub bearing 132 can include a sub plate portion 1321 and a sub bushing portion 1322. The sub plate portion 1321 covers the lower side of the cylinder barrel 133 and is combined with the cylinder barrel 133, and the sub bushing portion 1322 extends in the axial direction from the center of the sub plate portion 1321 toward the lower case 112 and supports the lower half of the rotation shaft 123.

[0098] The sub plate portion 1321 can be formed in a disc shape like the main plate portion 1311, and the outer peripheral surface of the sub plate portion 1321 can be spaced apart from the inner peripheral surface of the middle case 111.

[0099] Among the axial both side surfaces of the sub plate portion 1321, a lower surface of the sub plate portion 1321, i.e., a sub sliding surface 1321a, which faces the lower surface of the roller 134, can be formed with a first sub back pressure pocket 1325a and a second sub back pressure pocket 1325b.

[0100] The first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b can be symmetrically formed with the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, respectively, which are described above, with the roller 134 as the center.

[0101] For example, the first sub back pressure pocket 1325a can be symmetric with the first main back pressure pocket 1315a, and the second sub back pressure pocket 1325b can be symmetric with the second main back pressure pocket 1315b. Accordingly, a first sub bearing protrusion 1326a can be formed on the inner peripheral side of the first sub back pressure pocket 1325a, and a second sub bearing protrusion 1326b can be formed on the inner peripheral side of the second sub back pressure pocket 1325b.

[0102] As for the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b, the first sub bearing protrusion 1326a and the second sub bearing protrusion 1326b, the description for the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, the first main bearing protrusion 1316a and the second main bearing protrusion 1316b will be replaced.

[0103] However, depending on the situation, the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b can be asymmetrically formed with the first main back pressure pocket 1315a and the second main back pressure pocket 1315b, respectively, with the roller 134 as the center. For example, the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b can be formed deeper than the first main back pressure pocket 1315a and the second main back pressure pocket 1315b.

[0104] Further, the sub slide surface 1321a can be formed with a first discharge guide portion 141 that constitutes a part of a residual refrigerant discharge passage 140 described later. The first discharge guide portion 141 can be formed between the first sub back pressure pocket 1325a and the second sub back pressure pocket 1325b. One side of the first discharge guide portion 141 communicates with the compression space V, more accurately, with the residual space S, and the other side of the first discharge guide portion 141 can be formed to periodically communicate with the second discharge guide portion 142 described later provided on the roller 134. The first discharge guide portion 141 will be described later together with the residual refrigerant discharge passage 140.

[0105] Further, the sub bush portion 1322 can be formed in a hollow bush shape, and an oil groove 1322c can be formed on the inner circumferential surface of a sub bearing hole 1322a that constitutes the inner circumferential surface of the sub bush portion 1322. The oil groove 1322c is linear or oblique between the upper and lower ends of the sub bush portion 1322, and can communicate with the second oil through hole 126b of the rotating shaft 123.

[0106] Although not shown, the back pressure pockets 1315a and 1315b, 1325a and 1325b can be formed on only one side of either the main bearing 131 or the sub bearing 132.

[0107] Further, as described above, the discharge port 1313 can be formed in the main bearing 131. However, the discharge port 1313 can also be formed in the sub bearing 132, or can be formed in the main bearing 131 and the sub bearing 132, respectively, and can also be formed through between the inner circumferential surface and the outer circumferential surface of the cylinder 133. The present embodiment will be described centering on the case where the discharge port 1313 is formed in the main bearing 131.

[0108] The discharge port 1313 can also be formed with only one. However, the discharge port 1313 of the present embodiment can be formed with a plurality of discharge ports 1313a, 1313b, 1313c at a predetermined interval from each other in the compression direction (or the rotation direction of the roller).

[0109] Generally, in a vane rotary compressor, as the roller 134 is eccentrically disposed with respect to the compression space V, a contact point P of almost contact is generated between the outer circumferential surface 1342 of the roller 134 and the inner circumferential surface 1332 of the cylinder 133, and the discharge port 1313 is formed to be adjacent to the contact point P on the opposite side of the suction port 1331 from the contact point P. Therefore, the closer the compression space V is to the contact point P, the smaller the interval between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1342 of the roller 134, and thus it is not easy to secure the area of the discharge port 1313.

[0110] Therefore, the discharge port 1313 of the present embodiment is divided into a plurality of discharge ports 1313a, 1313b, 1313c having a small inner diameter, and the plurality of discharge ports 1313a, 1313b, 1313c can be arranged at a predetermined interval from each other in the circumferential direction, i.e., the rotation direction of the roller 134.

[0111] In addition, the plurality of discharge ports 1313a, 1313b, 1313c can each be formed with one, but as shown in the present embodiment, can be formed with two as a pair. For example, the discharge ports 1313 can be arranged in the order of the first discharge port 1313a, the second discharge port 1313b, and the third discharge port 1313c, starting from the discharge port closest to the approach portion 1332a.

[0112] The interval between the discharge ports 1313a, 1313b, 1313c can be substantially the same. For example, the first interval between the rear end of the first discharge port 1313a and the front end of the second discharge port 1313b can be formed to be substantially the same as the second interval between the rear end of the second discharge port 1313b and the front end of the third discharge port 1313c.

[0113] In addition, the interval from the front end to the rear end of the discharge port 1313, i.e., the arc length of the discharge port 1313, can be formed to be substantially the same as the arc length of each compression chamber V1, V2, V3. For example, the arc length between the front end of the first discharge port 1313a and the rear end of the third discharge port 1313b can be formed to be substantially similar to the interval between the preceding blade and the following blade, i.e., the arc length of each compression chamber V1, V2, V3.

[0114] However, depending on the situation, the arc length between the front end of the first discharge port 1313a and the rear end of the third discharge port 1313b can be formed to be larger than the interval between the preceding blade and the following blade, i.e., the arc length of each compression chamber V1, V2, V3. In this case, since at least one compression chamber V1, V2, V3 is located within the circumferential range of the discharge port 1313, continuous discharge can be achieved, thereby suppressing over-compression and / or pressure pulsation.

[0115] Although not shown, in the case where the blade grooves 1343a, 1343b, 1343c described later are formed at unequal intervals, the circumferential length of each compression chamber V1, V2, V3 can be formed to be different, and the plurality of discharge ports can communicate with one compression chamber, or the plurality of compression chambers can communicate with one discharge port.

[0116] In addition, the plurality of discharge ports 1313a, 1313b, 1313c can be opened and closed by the respective discharge valves 1361, 1362, 1363 described above. The respective discharge valves 1361, 1362, 1363 can be constituted by a reed valve of a cantilever shape, one end of which constitutes a fixed end and the other end of which constitutes a free end. Such respective discharge valves 1361, 1362, 1363 are widely known in a conventional rotary compressor, and thus a description thereof will be omitted.

[0117] With reference to Figures 1 to 3 The cylinder 133 of the present embodiment can be attached to the lower surface of the main bearing 131 and can be fastened to the main bearing 131 together with the sub bearing 132 by means of a bolt. Thus, the cylinder 133 can be fixedly coupled to the housing 110 via the main bearing 131.

[0118] The cylinder 133 can be formed in an annular shape having a hollow space portion in the center to constitute a compression space V. The hollow space portion is sealed by the main bearing 131 and the sub bearing 132 to form the compression space V described above, and the roller 134 described later can be rotatably coupled to the compression space V.

[0119] The cylinder 133 can be formed by penetrating the suction port 1331 from the outer circumferential surface to the inner circumferential surface. However, the suction port can also be formed by penetrating the main bearing 131 or the sub bearing 132.

[0120] The suction port 1331 can be formed on one circumferential side with the contact point P described later as the center. The discharge port 1313 described above can be formed on the other circumferential side opposite to the suction port 1331 in the main bearing 131 with the contact point P as the center.

[0121] The inner circumferential surface 1332 of the cylinder 133 can be formed in an elliptical shape. The inner circumferential surface 1332 of the cylinder 133 of the present embodiment can be combined in a manner having two circular points by a plurality of ellipses, for example, four ellipses having different ratios of length to width, thereby forming an asymmetric elliptical shape.

[0122] Specifically, the inner circumferential surface 1332 of the cylinder 133 of the present embodiment can be formed such that the center of the roller 134 described later or the rotational center (axial center or outer diameter center of the cylinder) Or of the roller 134 has a first circular point O and a second circular point O' that is offset to the contact point P side with respect to the first circular point O.

[0123] An X-Y plane formed with the first circular point O as the center will form a third quadrant face Q3 and a fourth quadrant face Q4, and an X-Y plane formed with the second circular point O' as the center will form a first quadrant face Q1 and a second quadrant face Q2. The third quadrant face Q3 is formed by a third ellipse, the fourth quadrant face Q4 is formed by a fourth ellipse, the first quadrant face Q1 is formed by a first ellipse, and the second quadrant face Q2 is formed by a second ellipse.

[0124] In addition, the inner circumferential surface 1332 of the cylinder 133 of the present embodiment can include a proximal portion 1332a, a distal portion 1332b, and a curved portion 1332c. The proximal portion 1332a is a portion closest to the outer circumferential surface (or the rotational center of the roller) 1341 of the roller 134, the distal portion 1332b is a portion farthest from the outer circumferential surface 1342 of the roller 134, and the curved portion 1332c is a portion connecting the proximal portion 1332a and the distal portion 1332b.

[0125] The proximal portion 1332a can also be defined as the contact point P, and can be divided into the first quadrant face Q1 and the fourth quadrant face Q4 described above with the proximal portion 1332a as the center. On both sides of the proximal portion 1332a as the center, the suction port 1331 can be formed in the first quadrant face Q1, and the discharge port 1313 can be formed in the fourth quadrant face Q4. Thus, when the vanes 1351, 1352, 1353 pass through the contact point P, the compression face on the rotational direction side of the vanes 1351, 1352, 1353 will be subjected to the low-pressure suction pressure, and the compression back face on the opposite side thereof will be subjected to the high-pressure discharge pressure. Then, during the passage of the roller 134 through the contact point P, the greatest variation in pressure will be experienced between the front face 1351a, 1352a, 1353a of each vane 1351, 1352, 1353 abutting the inner circumferential surface of the cylinder 133 and the back end face 1351b, 1352b, 1353b of each vane 1351, 1352, 1353 facing the back pressure chamber 1344a, 1344b, 1344c, and thus the phenomenon of the vanes 1351, 1352, 1353 being greatly shaken can occur.

[0126] Referring to Figures 1 to 3 The roller 134 of the present embodiment is rotatably disposed in the compression space V of the cylinder 133, and the plurality of vanes 1351, 1352, 1353 described below can be inserted into the roller 134 at a predetermined interval in the circumferential direction. Thus, in the compression space V, compression chambers can be formed in the number of the plurality of vanes 1351, 1352, 1353. In the present embodiment, the plurality of vanes 1351, 1352, 1353 is constituted by three, and thus the description will be made centering on the example in which the compression space V is divided into three compression chambers V1, V2, V3.

[0127] As described above, the roller 134 can be extended as a single body on the rotational shaft 123, or can be manufactured separately from the rotational shaft 123 and then assembled. In the present embodiment, the description will be made centering on the example in which the roller 134 is assembled with the rotational shaft 123.

[0128] However, even in the case where the roller 134 extends as a single body with the rotation shaft 123, the rotation shaft 123 and the roller 134 can be formed similarly to the present embodiment, and the resulting basic effects can be almost similar to the present embodiment. Only in the case where the roller 134 is assembled after the rotation shaft 123 as in the present embodiment, the roller 134 can be formed of a material different from the rotation shaft 123, for example, a hard material lighter than the rotation shaft 123. In this case, the roller 134 can be easily processed while reducing the weight of the rotating body including the roller 134, thereby improving the efficiency of the compressor.

[0129] The roller 134 of the present embodiment can be formed as a single body, that is, an integrated roller composed of one roller main body (not shown). However, the roller 134 is not necessarily formed as an integrated roller. For example, the roller 134 can also be formed as a separated roller separated into a plurality of roller main bodies (not shown). In this regard, a separate embodiment will be described later, and the present embodiment will be described centering on the integrated roller 134 composed as a single body.

[0130] Referring to Figures 1 to 3 The roller 134 of the present embodiment can be formed in a ring shape having an axial hole 1341 at its center. For example, the roller 134 has an inner peripheral surface and an outer peripheral surface, and the inner peripheral surface and the outer peripheral surface of the roller 134 can each be formed in a circular shape. Only the inner peripheral surface of the roller 134 is formed as a continuous surface, and the outer peripheral surface of the roller 134 is provided with opening surfaces of the vane grooves 1343a, 1343b, 1343c described later, and thus can be formed as a discontinuous surface corresponding to the number of the vane grooves 1343a, 1343b, 1343c thereof.

[0131] In addition, the rotation center Or of the roller 134 is coaxial with the axial center (not shown) of the rotation shaft 123, and the roller 134 will perform concentric rotation with the rotation shaft 123. Only as described above, as the inner peripheral surface 1332 of the cylinder barrel 133 is formed in an asymmetric elliptical shape biased toward a specific direction, the rotation center Or of the roller 134 can be eccentrically disposed with respect to the outer diameter center Oc of the cylinder barrel 133. Therefore, one side of the outer peripheral surface 1341b of the roller 134 almost contacts the inner peripheral surface 1332, and more precisely the approach portion 1332a of the cylinder barrel 133, thereby forming a contact point P.

[0132] As described above, the contact point P can be formed at the approach portion 1332a. Therefore, an imaginary line passing through the contact point P can correspond to a minor axis of the elliptical curve constituting the inner peripheral surface 1332 of the cylinder barrel 133.

[0133] The roller 134 is formed with a plurality of vane grooves 1343a, 1343b, 1343c into which vane 1351, 1352, 1353 described later can be respectively slidably inserted and coupled. The plurality of vane grooves 1343a, 1343b, 1343c are formed at a predetermined interval from each other in the circumferential direction, and the outer circumferential surface 1342 of the roller 134 is formed with an opening surface that is opened in the radial direction, and the inner side end portions on the opposite sides of the opening surface are respectively provided with back pressure chambers 1344a, 1344b, 1344c described later, and can be formed in a shape that is blocked in the radial direction.

[0134] The plurality of vane grooves 1343a, 1343b, 1343c are defined as a first vane groove 1343a, a second vane groove 1343b, and a third vane groove 1343c in the direction in which compression is performed (the direction of rotation of the roller), and the first vane groove 1343a, the second vane groove 1343b, and the third vane groove 1343c can be respectively formed at the same interval or at different intervals in the circumferential direction.

[0135] For example, each of the vane grooves 1343a, 1343b, 1343c is formed at a predetermined angle with respect to the radial direction, so that the length of the vane 1351, 1352, 1353 can be sufficiently ensured. Therefore, in the case where the inner circumferential surface 1332 of the cylinder 133 is formed in an asymmetric elliptical shape, even if the distance from the outer circumferential surface 1342 of the roller 134 to the inner circumferential surface 1332 of the cylinder 133 becomes farther, the vane 1351, 1352, 1353 can be prevented from being detached from the vane groove 1343a, 1343b, 1343c, so that not only the design freedom with respect to the inner circumferential surface 1332 of the cylinder 133 can be improved, but also the design freedom with respect to the roller 134 can be improved.

[0136] The direction in which the vane grooves 1343a, 1343b, 1343c are inclined can be preferably the opposite direction with respect to the direction of rotation of the roller 134, that is, the front surface 1351a, 1352a, 1353a of each vane 1351, 1352, 1353 that is in contact with the inner circumferential surface 1332 of the cylinder 133 is inclined to the side of the direction of rotation of the roller 134, so that the compression start angle can be pulled to the side of the direction of rotation of the roller 134, so that compression can be started quickly.

[0137] The inner side end of each vane groove 1343a, 1343b, 1343c can be formed to communicate with each back pressure chamber 1344a, 1344b, 1344c. Each back pressure chamber 1344a, 1344b, 1344c is a space in which oil (or refrigerant) of a discharge pressure or an intermediate pressure is accommodated to a rear side of each vane 1351, 1352, 1353, that is, to the rear end surface 1351c, 1352c, 1353c side of the vane 1351, 1352, 1353, and each vane 1351, 1352, 1353 can be pressed toward the inner peripheral surface of the cylinder 133 under the action of the pressure of the oil (or refrigerant) filled in the back pressure chamber 1344a, 1344b, 1344c. Hereinafter, the direction toward the inner peripheral surface of the cylinder can be defined as the front direction, and the opposite side thereof can be defined as the rear direction, based on the moving direction of the vane, and will be described.

[0138] Although not illustrated, the plurality of vane grooves 1343a, 1343b, 1343c can also be formed radially, that is, radially, with respect to the rotation center Or of the roller 134. The resulting effect is similar to the later-described embodiment in which the plurality of vane grooves 1343a, 1343b, 1343c are formed obliquely with respect to the rotation center Or of the roller 134, and thus the description thereof will be replaced by the description of the later-described embodiment.

[0139] The roller 134 can be formed with a second discharge guide portion 142 that constitutes a part of the later-described residual refrigerant discharge passage 140. The second discharge guide portion 142 can be provided with a plurality of and formed between the vane grooves 1343a and 1343b, 1343b and 1343c, 1343c and 1343a adjacent to each other in the circumferential direction. The first end 142a of the second discharge guide portion 142 can be formed to periodically communicate with the second end 1412b of the second guide groove 1412 of the first discharge guide portion 141, and the second end 142b of the second discharge guide portion 142 can be formed to periodically communicate with the first end 143a of the third discharge guide portion 143 described later. The second discharge guide portion 142 will be described later together with the residual refrigerant discharge passage 140.

[0140] In addition, the back pressure chambers 1344a, 1344b, 1344c can be formed to be sealed by the main bearing 131 and the auxiliary bearing 132, respectively. The back pressure chambers 1344a, 1344b, 1344c can be independently communicated with each of the back pressure pockets 1315a and 1315b, 1325a and 1325b, or can be formed to be communicated with each other through the back pressure pockets 1315a and 1315b, 1325a and 1325b.

[0141] Reference Figures 1 to 3The plurality of vanes 1351, 1352, 1353 of the present embodiment can be slidably inserted into the respective vane grooves 1343a, 1343b, 1343c. Thus, the plurality of vanes 1351, 1352, 1353 can be formed in substantially the same shape as the respective vane grooves 1343a, 1343b, 1343c.

[0142] For example, the plurality of vanes 1351, 1352, 1353 can be defined as a first vane 1351, a second vane 1352, and a third vane 1353 according to the direction of rotation of the roller 134. The first vane 1351 can be inserted into the first vane groove 1343a, the second vane 1352 can be inserted into the second vane groove 1343b, and the third vane 1353 can be inserted into the third vane groove 1343c.

[0143] The plurality of vanes 1351, 1352, 1353 can be formed in substantially the same shape. For example, the plurality of vanes 1351, 1352, 1353 can each be formed in a substantially rectangular parallelepiped, and the front faces 1351a, 1352a, 1353a of the vanes 1351, 1352, 1353 that come into contact with the inner circumferential surface 1332 of the cylinder 133 can be formed in a curved surface in the circumferential direction. Thus, the front faces 1351a, 1352a, 1353a of the vanes 1351, 1352, 1353 will be in line contact with the inner circumferential surface 1332 of the cylinder 133, thereby enabling reduction of frictional loss.

[0144] In addition, the sub bearing 132 and the roller 134 and the main bearing 131 can be formed with a residual refrigerant discharge passage 140 that communicates with the residual space S to discharge refrigerant remaining in the residual space S to the inside space 110a of the housing 110.

[0145] The residual refrigerant discharge passage 140 includes a first discharge guide portion 141 provided to the sub bearing 132, a second discharge guide portion 142 provided to the roller, and a third discharge guide portion 143 provided to the main bearing 131, and the first discharge guide portion 141 and the second discharge guide portion 142 and the third discharge guide portion 143 can be formed to communicate successively. Thus, refrigerant remaining in the residual space S can be discharged to the inside space 110a of the housing 110 through the first discharge guide portion 141 and the second discharge guide portion 142 and the third discharge guide portion 143. The residual refrigerant discharge passage 140 will be described later.

[0146] In the vane rotary compressor having the hybrid cylinder as described above, when power is supplied to the drive motor 120, the rotor 122 of the drive motor 120 and the rotary shaft 123 combined with the rotor 122 will rotate, and the roller 134 combined with or formed integrally with the rotary shaft 123 will rotate together with the rotary shaft 123.

[0147] Then, under the action of centrifugal force generated by the rotation of the roller 134 and back pressure of the back pressure chambers 1344a, 1344b, 1344c supporting the back end surfaces 1351b, 1351b, 1351c of the plurality of vanes 1351, 1352, 1353, the vanes 1351, 1352, 1353 are drawn out of the respective vane grooves 1343a, 1343b, 1343c and come into contact with the inner peripheral surface 1332 of the cylinder 133.

[0148] Then, the compression space V of the cylinder 133 is divided by the plurality of vanes 1351, 1352, 1353 into compression chambers (including suction chambers or discharge chambers) VI, V2, V3 corresponding to the number of the plurality of vanes 1351, 1352, 1353, and each of the compression chambers VI, V2, V3 repeatedly performs a series of processes in which each of the compression chambers VI, V2, V3 moves with the rotation of the roller 134, the volume thereof changes depending on the shape of the inner peripheral surface 1332 of the cylinder 133 and the eccentricity of the roller 134, the refrigerant suctioned into each of the compression chambers VI, V2, V3 is compressed while moving along the roller 134 and the vanes 1351, 1352, 1353, and is discharged to the inside space of the housing 110.

[0149] At this time, the interval between the inner peripheral surface 1332 of the cylinder 133 and the outer peripheral surface 1322 of the roller 134 narrows sharply closer to the contact point P, and therefore the third discharge port 1313c as the final discharge port is formed at a predetermined interval in the circumferential direction from the contact point P. Thus, a residual space S is formed between the third discharge port 1313c and the contact point P, and in the residual space S, the non-discharged refrigerant that is not discharged in the third discharge port 1313c will be left. As described above, this can cause over-compression in the residual space S, and thus can reduce the compressor efficiency.

[0150] Therefore, in the present embodiment, a residual refrigerant discharge passage (hereinafter, discharge passage) 140 can also be formed, one end of which is communicated to between the third discharge port 1313c and the contact point P, and the other end of which is communicated to the inside space 110a of the housing 110. Thus, by discharging the refrigerant left in the residual space S to the inside space 110a of the housing 110, the refrigerant left in the residual space S is suppressed or minimized, and thus the reduction in the compressor efficiency due to over-compression of the refrigerant can be suppressed.

[0151] The discharge passage 140 of the present embodiment is formed with an inlet of the discharge passage 140 on the bearing not having the discharge port, and is formed with an outlet of the discharge passage 140 on the bearing having the discharge port between the roller 134 and the bearing, and the intermediate passage can be formed between the inlet of the discharge passage 140 and the outlet of the discharge passage 140. Therefore, when the inlet and the outlet of the discharge passage 140 are communicated by the intermediate passage, the refrigerant remaining in the residual space S can sequentially pass through the inlet of the discharge passage 140, the intermediate passage of the discharge passage 140, and the outlet of the discharge passage 140, and thus be discharged to the inside space 110a of the housing 110.

[0152] For example, in the case where the discharge ports 1313a, 1313b, 1313c and the discharge muffler 137 are provided on the main bearing 131, the inlet of the discharge passage 140 can be formed on the sub bearing 132, and the outlet of the discharge passage 140 can be formed on the main bearing 131. However, in the case where the discharge port and the discharge muffler are provided on the sub bearing 132, the inlet of the discharge passage 140 can be formed on the main bearing 131, and the outlet of the discharge passage 140 can be formed on the sub bearing 132.

[0153] As described above, even in the case where the inlet and the outlet of the discharge passage 140 are formed on the bearings opposite to each other, the basic shape of the discharge passage 140 or the corresponding effect thereof can be the same. Hereinafter, the case where the inlet of the discharge passage 140 is formed on the sub bearing 132 and the outlet of the discharge passage 140 is formed on the main bearing 131 will be described as a center.

[0154] Figure 4 is a perspective view showing the compression part in the Figure 1 and showing the discharge passage, Figure 5 is a perspective view showing the assembled state of the compression part in the Figure 4 and showing the discharge passage, Figure 6 is a sectional view showing the discharge passage in the Figure 5 , Figure 7 is a schematic view for explaining the position of the first discharge guide part in the vane rotary compressor of the Figure 1 .

[0155] Referring again to Figure 1The rotary compressor of the present embodiment can have the main plate portion 1311 of the main bearing 131 formed with the discharge ports 1313a, 1313b, 1313c therethrough in the axial direction, and the discharge valves 1361, 1362, 1363 opening and closing the discharge ports 1313a, 1313b, 1313c can be provided on the opposite side surface of the main plate portion 1311, i.e., the main sliding surface 1311a, and the discharge muffler 137 accommodating the discharge ports 1313a, 1313b, 1313c and the discharge valves 1361, 1362, 1363 can be provided on the outer side surface of the main bearing 131.

[0156] Referring to Figures 4 to 6 The discharge muffler 137 can include a muffler fixing portion 1371 and a discharge space portion 1372.

[0157] The muffler fixing portion 1371 can be formed in a flange shape to be fastened to the outer side surface of the main bearing 131, and the discharge space portion 1372 can extend from the inner circumferential surface of the muffler fixing portion 1371 and be formed in a substantially cylindrical shape.

[0158] For example, the muffler fixing portion 1371 can have an outer diameter smaller than that of the main plate portion 1311, and a plurality of bolt holes (not marked) can be formed in the circumferential direction, so that the main bearing 131 can be bolt-fastened together with the cylinder 133 and the sub bearing 132.

[0159] The discharge space portion 1372 can be bent in such a manner as to protrude in the axial direction from the muffler fixing portion 1371, so as to be formed in a substantially cylindrical shape. Thus, the inner side surface of the discharge space portion 1372 is spaced apart from the outer side surface of the main plate portion 1311 to form a discharge space 1372a, and the discharge ports 1313a, 1313b, 1313c and the discharge valves 1361, 1362, 1363 described above can be accommodated in the discharge space 1372a.

[0160] The height H1 of the discharge space portion 1372 with reference to the upper surface of the main plate portion 1311 can be formed lower than the height H2 of the main bush portion 1312, and a bearing through-hole 1372b can be formed in the center of the discharge space portion 1372. Thus, the discharge space portion 1372 can be inserted into the main bush portion 1312 combined to the main bearing 131.

[0161] The inner peripheral surface of the bearing through-hole 1372b is separated from the outer peripheral surface of the main bushing portion 1312 by a predetermined interval, and an exhaust interval D can be formed between the inner peripheral surface of the bearing through-hole 1372b and the outer peripheral surface of the main bushing portion 1312. Thus, the refrigerant compressed in the compression chambers V1, V2, V3 is discharged to the discharge space 1372a of the discharge muffler 137 through the discharge outlets 1313a, 1313b, 1313c, and the refrigerant is discharged to the inner space 110a of the housing 110 through the exhaust interval D between the inner peripheral surface of the discharge muffler 137 and the outer peripheral surface of the main boss portion 1312. At this time, the pulsation pressure of the refrigerant can be reduced in the discharge space 1372a.

[0162] Referring to Figures 4 to 6 , the discharge passage 140 of the present embodiment can include a first discharge guide portion 141, a second discharge guide portion 142, and a third discharge guide portion 143. The first discharge guide portion 141 can be formed in the sub bearing 132, the second discharge guide portion 142 can be formed in the roller 134, and the third discharge guide portion 143 can be formed in the main bearing 131.

[0163] For example, the first discharge guide portion 141 of the present embodiment can include a first guide groove 1411 and a second guide groove 1412. The first guide groove 1411 can communicate with the compression space V, more accurately, the residual space S, and the second guide groove 1412 can communicate with the second discharge guide portion 142.

[0164] The first guide groove 1411 can be formed in substantially the same shape as the third discharge outlet 1313c which is the final discharge outlet. For example, the first guide groove 1411 can be formed in a circular cross-sectional shape.

[0165] The first guide groove 1411 can be formed at a position where the third discharge outlet 1313c can overlap at least a portion in the axial direction. For example, in the case where the third discharge outlet 1313c is formed by two as a pair as shown in Figure 3 , the first guide groove 1411 can be formed at a position where the third discharge outlet (hereinafter, a rear third discharge outlet) 1313c2 which is relatively adjacent to the contact point can overlap at least a portion.

[0166] Referring to Figure 7 , the first guide groove 1411 can be formed on the same axis as the rear third discharge outlet 1313c2, or can be formed to be more adjacent to the contact point P than the rear third discharge outlet 1313c2.

[0167] For example, in a case where the tip of the rear third discharge port 1313c2 is formed at a position pulled away by substantially 5° or more from the contact point P as the minimum seal distance (or seal angle) a, the first guide groove 1411 can be formed so as to be more eccentric toward the contact point P side than the rear third discharge port 1313c2. In this case, the first guide groove 1411 is preferably formed at a position pulled away by substantially 5° or more from the contact point P so as to be able to secure the minimum seal distance a described above. Thus, it is possible to suppress the high-pressure refrigerant from passing over the contact point P and moving toward the suction side due to the first guide groove 1411.

[0168] On the other hand, in a case where the tip of the rear third discharge port 1313c2 is formed at a position of substantially 5° from the contact point P as the minimum seal distance a, the first guide groove 1411 can be formed so as to be on substantially the same axis as the rear third discharge port 1313c2. In this case, it is also possible to suppress the high-pressure refrigerant from passing over the contact point P and flowing toward the suction side due to the first guide groove 1411.

[0169] In addition, the first guide groove 1411 can be formed so that substantially 50% or more of the entire area of the first guide groove 1411 overlaps the rear third discharge port 1313c2 in the axial direction. Thus, the area in which the first guide groove 1411 overlaps the residual space S described above in the axial direction widens, and thus it is possible to effectively discharge the residual refrigerant.

[0170] The discharge passage circular arc angle β of the present embodiment is greater than or equal to the vane included angle θ, and preferably, the discharge passage circular arc angle β can be greater than the vane included angle θ. Although the discharge passage circular arc angle β shown in Figure 7 the discharge passage circular arc angle β is less than the vane included angle θ, in a case where the first guide groove 1411 is formed in a long rectangular shape that is longer in the circumferential direction, the discharge passage circular arc angle β can be greater than or equal to the vane included angle θ.

[0171] Here, the discharge passage circular arc angle β can be defined as the circular arc angle between both ends of the first guide groove 1411 at a position located more rearward than the third discharge port 1313c, which constitutes the final discharge port, from the start end of the first discharge port 1313a, which constitutes the initial discharge port, and the vane included angle θ can be defined as each of the circular arc angles between the two adjacent vane 1351 and 1352, 1352 and 1353, and 1353c and 1351 in a case where the three vanes 1351, 1352, and 1353 are arranged at equal intervals in the circumferential direction of the roller 134.

[0172] In this case, the blade included angle θ can be 120°, respectively, and the discharge passage circular arc angle β can be greater than or equal to about 120°, preferably greater than 120°. Thus, the discharge passage including the discharge port and the discharge passage 140 can extend to the circumferential range of the corresponding compression chamber or beyond the circumferential range of the corresponding compression chamber. Then, it is possible to ensure that the length of the discharge stroke of the refrigerant in the corresponding compression chamber is longer than the length of the compression stroke, thereby minimizing the amount of compressed refrigerant remaining after the discharge stroke in the corresponding compression chamber or remaining in the residual space S adjacent to the contact point P. Furthermore, as the circular arc length of the discharge passage is formed to be greater than or equal to the circular arc length of the compression chamber, continuous discharge can be achieved, thereby reducing pressure pulsation.

[0173] In addition, the cross-sectional area of the first guide groove 1411 can be greater than or equal to the cross-sectional area of the rear third discharge port 1313c2. Thus, the area of the first guide groove 1411 overlapping with the remaining refrigerant is enlarged, thereby enabling more efficient discharge of the remaining refrigerant. However, the cross-sectional area of the first guide groove 1411 can also be smaller than the cross-sectional area of the rear third discharge port 1313c2.

[0174] Although not illustrated, the first guide groove 1411 can be formed in various shapes. For example, in Figure 4 In FIG. 8, the first guide groove 1411 is formed only one, but according to circumstances, the first guide groove 1411 can also be formed in two constituting a pair and communicating with each other, or can also be formed in one long groove shape, as with the third discharge port. In this case, the first guide groove 1411 can be lengthened in the circumferential direction, thereby enabling more efficient discharge of the remaining refrigerant.

[0175] Referring to Figures 4 to 6 , the first end 1412a of the second guide groove 1412 can communicate with the first guide groove 1411, and the second end 1412b of the second guide groove 1412 can communicate with the second discharge guide portion 142. For example, the second guide groove 1412 can be formed in a long shape extending longer in the radial direction.

[0176] Specifically, the first end 1412a of the second guide groove 1412 can be located radially outward, and the second end 1412b of the second guide groove 1412 can be located radially inward. Thus, the second end 1412b of the second guide groove 1412 can be formed to be located closer to the rotation center Or of the roller 134 than the first guide groove 1411.

[0177] The cross-sectional area (or width) of the second guide groove 1412 can be smaller than the inner diameter of the first guide groove 1411. For example, the second guide groove 1412 can be formed thinner and longer than the first guide groove 1411. Thus, a portion of the second guide groove 1412 can be formed between the first sub-back pressure pocket 1325a and the second sub-back pressure pocket 1325b. For example, a first end 1412a of the second guide groove 1412 can be formed at a position further outward than the pocket virtual circle C of the outer peripheral surface of the first sub-back pressure pocket 1325a and the outer peripheral surface of the second sub-back pressure pocket 1325b, whereas a second end 1412b of the second guide groove 1412 can be formed at a position between the circumferences of the first sub-back pressure pocket 1325a and the second sub-back pressure pocket 1325b.

[0178] The second guide groove 1412 can be formed so that its cross-sectional area is greater than or equal to that of the second discharge guide portion 142 on the same axis as the second discharge guide portion 142 described later. Thus, the second guide groove 1412 can periodically communicate with the second discharge guide portion 142 provided on the roller 134 as the roller 134 rotates.

[0179] Referring to Figures 4 to 6 The second discharge guide portion 142 of the present embodiment can be formed so as to penetrate both sides of the roller 134 in the axial direction. For example, a first end 142a of the second discharge guide portion 142 can be open to the lower surface of the roller 134 facing the sub-slide surface 1321a, and a second end 142b of the second discharge guide portion 142 can be open to the upper surface of the roller 134 facing the main bearing surface 131.

[0180] The second discharge guide portion 142 can be penetrated in the axial direction. Thus, the second discharge guide portion 142 can be easily machined. However, the second discharge guide portion 142 need not necessarily be penetrated in the axial direction.

[0181] Although not shown, the second discharge guide portion 142 can also be formed so as to be inclined with respect to the axial direction, for example, from the first end 142a to the second end 142b of the second discharge guide portion 142, in the positive direction with respect to the rotation direction of the roller 134. In this case, the refrigerant of the first discharge guide portion 141 can be more rapidly discharged while being subjected to centrifugal force during passage through the second discharge guide portion 142.

[0182] The second discharge guide portion 142 can be formed at a position axially overlapping the second guide groove 1412 of the first discharge guide portion 141 described earlier. Thus, the second discharge guide portion 142 can periodically communicate with the second guide groove 1412 of the first discharge guide portion 141 as the roller 134 rotates.

[0183] The second discharge guide portion 142 can be formed in one or more. For example, the second discharge guide portion 142 can be formed in a number greater than that of the first discharge guide portion 141, more precisely, a number greater than that of the second guide groove 1412. Accordingly, the second discharge guide portion 142 can be communicated with the second guide groove 1412 a plurality of times, precisely, a number of times corresponding to the number of the second discharge guide portion 142, per one rotation of the roller 134, and the first discharge guide portion 141 including the second guide groove 1412 can be communicated with the third discharge guide portion 143 once per one rotation of the roller 134.

[0184] The second discharge guide portion 142 is formed corresponding to the number of the vane 135 (or the number of the compression chamber), and the first discharge guide portion 141 and the third discharge guide portion 143 can be formed in one each. In other words, the first discharge guide portion 141 and the third discharge guide portion 143 are formed on the same axis, and the second discharge guide portion 142 can be formed in equal intervals along the circumference, for example, in the case where the vane 135 is three, each of the second discharge guide portions 142 can be formed in equal intervals along the circumference at intervals of 120° from each other. Accordingly, the second discharge guide portion 142 can communicate the first discharge guide portion 141 and the third discharge guide portion 143 every 120° with reference to the rotation angle of the roller (or the rotation shaft) 134.

[0185] Then, the discharge passage 140 can be opened once every 120° to discharge the residual refrigerant not discharged from each of the compression chambers V1, V2, V3 to the inside space 110a of the housing 110 through each of the second discharge guide portions 142. Accordingly, in the compression stroke, the discharge passage 140 is blocked to suppress the refrigerant in compression from flowing out through the discharge passage 140, so that it is possible to prevent the compression deficiency due to the discharge passage 140 in advance.

[0186] Although not illustrated, the second discharge guide portion 142 can also be formed in a plurality in each of the vanes 1351 and 1352, 1352 and 1353, 1353 and 1351 adjacent to each other, that is, each of the compression chambers V1, V2, V3. In this case, it is also possible to discharge the residual refrigerant not discharged from each of the compression chambers V1, V2, V3 through each of the second discharge guide portions 142.

[0187] The second discharge guide portion 142 can be formed in the same number or the same cross-sectional area in each of the compression chambers V1, V2, V3. Accordingly, it is possible to equally discharge the residual refrigerant not discharged from each of the compression chambers.

[0188] The inner diameter of the second discharge guide portion 142 can be formed to be greater than or equal to the width of the second guide groove 1412. Thus, the refrigerant passing through the second guide groove 1412 of the first discharge guide portion 141 can move to the second discharge guide portion 142 without obstruction, thereby enabling the residual refrigerant to be rapidly discharged.

[0189] Referring to Figures 4 to 6 The third discharge guide portion 143 of the present embodiment can be formed to pass through between the axial both sides of the main bearing 131. For example, the first end 143a of the third discharge guide portion 143 can be opened toward the main sliding surface 1311a of the main plate portion 1311, and the second end 143b of the third discharge guide portion 143 can be opened toward the outer circumferential surface of the main boss portion 1312.

[0190] The third discharge guide portion 143 can be formed to communicate with the second guide groove 1412 of the first discharge guide portion 141 through the second discharge guide portion 142. For example, in the case where the second discharge guide portion 142 is formed to pass through in the axial direction, the first end 143a of the third discharge guide portion 143 can be located on the same axis as the second end 1412b of the second guide groove 1412.

[0191] Although not illustrated, in the case where the second discharge guide portion 142 is formed to be inclined, the third discharge guide portion 143 can be formed such that the first end 143a of the third discharge guide portion 143 communicates with the second end 142b of the second discharge guide portion 142 at the point in time when the first end of the second discharge guide portion 142 communicates with the second end 1412b of the second guide groove 1412. For example, the first end 143a of the third discharge guide portion 143 can be formed between the circumferences of the first main back pressure bag 1315a and the second main back pressure bag 1315b. Thus, the second discharge guide portion 142 can be formed to pass through the main boss portion 1312 in the axial direction.

[0192] Although not illustrated, the first end 143a of the third discharge guide portion 143 can also be formed at a position further outward than the bag virtual circle C connecting the outer circumferential surface of the first main back pressure bag 1315a and the outer circumferential surface of the second main back pressure bag 1315b. In this case, the second discharge guide portion 142 can be formed to pass through the main boss portion 1312 inclined with respect to the axial direction, or can be formed to pass through a guide boss (not illustrated) extending in the radial direction from the outer circumferential surface of the main boss portion 1312 in the axial direction.

[0193] The third discharge guide portion 143 can be formed in a number less than that of the second discharge guide portion 142. For example, the third discharge guide portion 143 can be formed with only one, like the first discharge guide portion 141, and formed on the same axis. In this case, the second discharge guide portion 142 can be formed in three along the circumference at equal intervals in the number of compression chambers V1, V2, V3, and the third discharge guide portion 143 and the first discharge guide portion 141 can be formed on the same axis with each of the second discharge guide portions 142. Therefore, the third discharge guide portion 143 can communicate with the first discharge guide portion 141 once per one rotation of the roller 134.

[0194] Although not illustrated, the third discharge guide portion 143 can also be formed in a number different from that of the first discharge guide portion 141. For example, the third discharge guide portion 143 can be formed with only one, and the first discharge guide portion 141 can be formed with a plurality, or conversely, the third discharge guide portion 143 can be formed with a plurality, and the first discharge guide portion 141 can be formed with only one. In this case, however, each of the second discharge guide portions 142 can be formed on the same axis, and therefore the third discharge guide portion 143 can communicate with the first discharge guide portion 141 once per one rotation of the roller 134.

[0195] The inner diameter of the third discharge guide portion 143 can be formed to be greater than or equal to the inner diameter of the second discharge guide portion 142. For example, the cross-sectional area of the first end 143a of the third discharge guide portion 143 can be formed to be greater than or equal to the cross-sectional area of the second end 142b of the second discharge guide portion 142. Therefore, the refrigerant passing through the second discharge guide portion 142 can move to the third discharge guide portion 143 without obstruction, and thus the remaining refrigerant can be rapidly discharged.

[0196] The second end 143b of the third discharge guide portion 143 can be opened from the outer circumferential surface of the main boss portion 1312 toward the internal space 110a of the housing 110. For example, the height H3 of the second end 143b of the third discharge guide portion 143 can be formed to be greater than the height H1 of the discharge space portion 1372 of the discharge muffler 137, with the upper surface of the main plate portion 1311 as a reference. In other words, the second end 143b of the third discharge guide portion 143 can be opened to the outer circumferential surface of the main boss portion 1312 at a position higher than the discharge space portion 1372a of the discharge muffler 137. Therefore, the refrigerant passing through the third discharge guide portion 143 can be directly discharged to the internal space 110a of the housing 110 without passing through the discharge space 1372a of the discharge muffler 137. Thus, it is possible to suppress an increase in the internal pressure of the discharge muffler 137 due to the refrigerant, to suppress a vortex phenomenon in the discharge space 1372a while rapidly opening the discharge valves 1361, 1362, 1363, and to rapidly discharge the refrigerant from each discharge port 1313a, 1313b, 1313c.

[0197] In addition, as the second end 143b of the third discharge guide portion 143 is opened to the outer circumferential surface of the main boss portion 1312, the refrigerant passing through the third discharge guide portion 143 and being discharged to the internal space 110a of the housing 110 will smoothly be guided to the gap between the inner circumferential surface of the stator 121 and the inner circumferential surface of the rotor 122, or the internal gap of the stator 121, or the gap between the outer circumferential surface of the stator 121 and the inner circumferential surface of the housing 110, and thus can rapidly move toward the discharge pipe 116.

[0198] Although not shown, the second end 143b of the third discharge guide portion 143 can also be opened to the upper end surface of the main boss portion 1312. In this case, as the third discharge guide portion 143 is formed by a single machining, the third discharge guide portion 143 can be easily machined.

[0199] The rotary compressor of the present embodiment described above has the following effects.

[0200] Referring again to Figure 3As the vanes 1351, 1352, 1353 rotate together with the roller 134, the corresponding compression chambers VI, V2, V3 pass through the respective discharge ports 1313a, 1313b, 1313c in order from the first discharge port 1313a to the third discharge port 1313c. At this time, most of the refrigerant compressed in the corresponding compression chambers VI, V2, V3 is discharged to the discharge space 1372a of the discharge muffler 137 through the respective discharge ports 1313a, 1313b, 1313c, and thus is discharged to the inside space 110a of the housing 110. However, a portion of the refrigerant is not discharged even through the third discharge port 1313c, but remains as residual refrigerant in the residual space S between the third discharge port 1313c and the contact point P.

[0201] Therefore, in the present embodiment, the discharge passage 140 is provided at the rear side of the third discharge port 1313, and thus it is possible to discharge the refrigerant remaining in the residual space S to the inside space 110a of the housing 110. In other words, as shown in the present embodiment, in a case where the first discharge guide portion 141, which constitutes a part of the discharge passage 140, is formed at a position overlapping with the rear side third discharge port 1313c2 of the third discharge port 1313c, which is the final discharge port, or the residual space S, the refrigerant remaining in the residual space S can be directly discharged to the inside space 110a of the housing 110 through the discharge passage 140 constituted by the first discharge guide portion 141, the second discharge guide portion 142, and the third discharge guide portion 143. Therefore, by minimizing the situation where the high-pressure refrigerant remains in the residual space S, it is possible to reduce the motor input or to stabilize the behavior of the vanes.

[0202] Figures 8A to 8C is a schematic view showing a process of discharging the residual refrigerant through the discharge passage of the present embodiment. For convenience, in Figures 8A to 8C , the inner diameters of the second guide groove, the second discharge guide portion, and the third discharge guide portion are shown differently. Note that the inner diameters of these second guide groove, the second discharge guide portion, and the third discharge guide portion can be formed differently as shown in the figure, or can be formed identically.

[0203] Figure 8Ais a state in which the roller 134 rotates so that the corresponding vane 135 reaches a position adjacent to the third discharge port 1313c. In this state, the corresponding vane 135 is still in the process of passing through the third discharge port 1313c, and the third discharge port 1313c is still in an open state, so the residual space S in communication with the third discharge port 1313c is also not sealed and remains in an open state. At this time, the second discharge guide portion 142 provided to the roller 134 is in a non-communication state between the first discharge guide portion 141 of the sub bearing 132 and the third discharge guide portion 143 of the main bearing 131. Then, before the corresponding vane 135 passes through the rear third discharge port 1313c2 constituting the third discharge port 1313c, the refrigerant of the residual space S will be discharged to the inside space 110a of the housing 110 along with the refrigerant of the corresponding compression chamber through the third discharge port 1313c.

[0204] Figure 8B is a state in which the roller 134 further rotates so that the corresponding vane 135 just passes through the third discharge port 1313c. In this state, the corresponding vane 135 is located between the third discharge port 1313c and the residual space S, and the residual space S is separated from the third discharge port 1313c to reach a sealed state. At this time, the second discharge guide portion 142 provided to the roller 134 reaches a communication state between the first discharge guide portion 141 of the sub bearing 132 and the third discharge guide portion 143 of the main bearing 131. Then, the refrigerant of the residual space S can pass through the first discharge guide portion 141, the second discharge guide portion 142, and the third discharge guide portion 143 in sequence and be discharged to the inside space 110a of the housing 110. Therefore, even if a part of the refrigerant remains due to the residual space S being sealed, the remaining refrigerant can be discharged to the inside space 110a of the housing 110 through the discharge passage 140, so that it is possible to suppress the high-pressure refrigerant remaining in the residual space S.

[0205] Figure 8Cis further rotated so that the corresponding vane 135 passes through the third discharge port 1313c and almost reaches the contact point P. In this state, although the preceding vane has already passed through the third discharge port 1313c, the following vane has not yet reached the third discharge port 1313c, and thus the third discharge port 1313c will be in an open state. Therefore, the residual space S communicating with the third discharge port 1313c will also be in an open state without being sealed. At this time, the second discharge guide portion 142 provided to the roller 134 will pass between the first discharge guide portion 141 of the sub bearing 132 and the third discharge guide portion 143 of the main bearing 131 to reach a non-communicating state. Then, before the following vane passes through the rear third discharge port 1313c2 constituting the third discharge port 1313c, the refrigerant of the residual space S will be discharged to the inside space 110a of the housing 110 together with the refrigerant of the following compression chamber through the third discharge port 1313c.

[0206] Thus, even after the discharge stroke, the residual refrigerant remaining in the compression space is discharged to the inside space of the housing through the discharge passage, and thus the situation in which the refrigerant remains in the compression space after the discharge stroke can be minimized. At the same time, as the discharge passage is periodically opened, the outflow of the refrigerant during the compression stroke can be suppressed, thereby preventing under-compression from occurring.

[0207] In addition, the discharge guide portion is provided in addition to the discharge port to form the discharge passage, and thus the discharge effective area in which the compressed refrigerant is discharged to the inside space of the housing can be enlarged, and thus the compressed refrigerant in the compression chamber can be more rapidly discharged during the discharge stroke, thereby enabling the over-compression loss to be suppressed.

[0208] In addition, as the high-pressure refrigerant remaining in the residual space is suppressed, the pressure acting on the front side of the vane can be uniformized, thereby eliminating the pressure difference acting on the front side and the rear side of the vane, and thus the jumping phenomenon of the vane can be suppressed. In addition, the front side of the vane or the inner circumferential surface of the cylinder tube facing the same can be prevented from being worn, and at the same time, the vibration noise caused by the shaking of the vane can be reduced. Furthermore, the high-pressure refrigerant is prevented from flowing to the suction side beyond the contact point P, and thus the suction loss can be reduced.

[0209] In addition, the discharge passage including the discharge passage can extend to the circumferential range of the corresponding compression chamber or beyond the circumferential range of the corresponding compression chamber, and thus continuous discharge can be achieved during the discharge stroke, and thus the pressure pulsation can be reduced.

[0210] In addition, the rotary compressor of the present embodiment can more greatly obtain the effects described above in the case of using a high-pressure refrigerant such as R32, R410a, or CO2.

[0211] Further, another embodiment of the discharge passage is as follows.

[0212] That is, in the foregoing embodiment, the inlet of the discharge passage is formed between the discharge port and the residual space, but according to the situation, the inlet of the discharge passage can also be formed at a position further forward than the discharge port.

[0213] Figure 9 is a plan view showing another embodiment of the discharge passage.

[0214] Referring to Figure 9 The discharge passage 140 of the present embodiment can include a first discharge guide portion 141, a second discharge guide portion 142, and a third discharge guide portion 143. The basic configuration of these first discharge guide portion 141, second discharge guide portion 142, and third discharge guide portion 143 and their effect are the same as those of the foregoing embodiment, so the specific description thereof will be replaced with the description of the foregoing embodiment.

[0215] However, the first discharge guide portion 141 of the present embodiment is configured of a first guide groove 1411 and a second guide groove 1412, and the first guide groove 1411 can be located at a position further forward than the rear third discharge port 1313c2 which is the final discharge port. For example, the first guide groove 1411 can be formed to be located at a position further forward in the circumferential direction than the front third discharge port 1313cl. Thus, a part of the refrigerant that has passed through the second discharge port 1313b will flow into the first discharge guide portion 141 which constitutes the inlet of the discharge passage 140 before moving to the front third discharge port 1313cl, and the refrigerant can be preliminarily discharged to the inside space 110a of the housing 110 through the second discharge guide portion 142 and the third discharge guide portion 143.

[0216] In this case, the first guide groove 1411 can also be formed to overlap the front third discharge port 1313cl by substantially 50% or more in the axial direction. Thus, it is possible to suppress the insufficient compression of the refrigerant of the corresponding compression chamber due to the discharge passage 140.

[0217] As described above, in the case where the first guide groove 1411 of the first discharge guide portion 141 which constitutes the inlet of the discharge passage 140 is located at a position further forward than the front third discharge port 1313cl, it is possible to expand the effective discharge area of the third discharge port 1313c. Thus, the refrigerant compressed in the compression chamber can not only be discharged through the third discharge port 1313c but also be rapidly discharged through the discharge passage 140, so it is possible to accordingly reduce the non-discharge amount in the corresponding compression chamber. Thereby, the residual amount of the refrigerant which is not discharged from the corresponding compression chamber and moves to the residual space is reduced, so it is possible to suppress the reduction in motor efficiency due to the over-compression in the compression space and the abrasion and vibration noise due to the flutter of the vane as described above.

[0218] Although not shown, in a case where the rear third discharge port 1313c2 is formed at a position pulled away by 5° or more from the minimum seal distance a from the contact point P, the first guide groove 1411 can be formed on the front side of the rear third discharge port 1313c2, for example, from an interval more on the front side than the front third discharge port 1313cl to an interval more on the rear side than the rear third discharge port 1313c2. In these cases, the first guide groove 1411 can also preferably be formed so as to overlap the front third discharge port 1313cl and / or the rear third discharge port 1313c2 by substantially 50% or more in the axial direction at a position where the minimum seal distance is ensured. In these cases, the effects are similar to those of the foregoing embodiments, and thus a description thereof will be omitted.

[0219] In addition, another embodiment having a discharge passage is as follows.

[0220] That is, in the foregoing embodiments, the inlet of the discharge passage is formed so as to be biased toward the rear side or toward the front side with respect to the discharge port, but according to the situation, the inlet of the discharge passage can also be formed on substantially the same axis as the discharge port.

[0221] Figure 10 is a plan view showing another embodiment of a discharge passage.

[0222] Referring to Figure 10 The discharge passage 140 of the present embodiment can include a first discharge guide portion 141, a second discharge guide portion 142, and a third discharge guide portion 143. The basic configuration of these first discharge guide portion 141, second discharge guide portion 142, and third discharge guide portion 143 and the effects thereof are the same as those of the foregoing embodiments, and thus a detailed description thereof will be replaced by the description of the foregoing embodiments.

[0223] However, the first discharge guide portion 141 of the present embodiment is configured by a first guide groove 1411 and a second guide groove 1412, and the first guide groove 1411 can have at least a portion thereof located on the same axis as the third discharge port 1313c, which is the final discharge port. For example, the rear third discharge port 1313c2 can be formed at a position corresponding to 5° of the minimum seal distance a from the contact point P, and the first guide groove 1411 can be located on substantially the same axis as the rear third discharge port 1313c2.

[0224] In this case, the first guide groove 1411 can be positioned between the rear third discharge port 1313c2 and the front third discharge port 1313c1. For example, the first guide groove 1411 can be formed to be positioned more rearward than the front third discharge port 1313c1 (or on the same axis), but to be positioned more forward than the rear third discharge port 1313c2 (or on the same axis). Thus, the first guide groove 1411 can be partially communicated to the rear third discharge port 1313c2 and the front third discharge port 1313c1.

[0225] As described above, in the case where the first guide groove 1411 of the first discharge guide portion 141 constituting the inlet of the discharge passage 140 is positioned more forward than the rear third discharge port 1313c2 which is the final discharge port, the discharge passage 140 will function as a kind of discharge port or bypass passage. That is, a part of the refrigerant passing through the second discharge port 1313b flows into the first discharge guide portion 141 constituting the inlet of the discharge passage 140, and the refrigerant can also be discharged to the inside space 110a of the housing 110 through the second discharge guide portion 142 and the third discharge guide portion 143 constituting the discharge passage 140.

[0226] Thus, as the discharge passage 140 functions as the third discharge port 1313c, the effective discharge area of the third discharge port 1313c is enlarged, so that the refrigerant compressed in the compression chamber can be more rapidly discharged. Thereby, the refrigerant remaining amount from the corresponding compression chamber not being discharged and moving to the residual space is reduced, so that the reduction of the motor efficiency due to over-compression in the compression space and the abrasion and vibration noise due to the blade flutter explained in the foregoing can be suppressed.

[0227] In addition, as the first guide groove 1411 is positioned more forward than the rear third discharge port 1313c2 and is positioned at the same or more rearward than the front third discharge port 1313c1, the refrigerant of the corresponding compression chamber can be suppressed from flowing out in an under-compression state.

[0228] Although not shown, in a case where the rear third discharge port 1313c2 is formed at a position that is 5° as the minimum seal distance a from the contact point P, the first guide groove 1411 can also be formed at a position that is more forward than the front third discharge port 1313cl. In other words, the first guide groove 1411 can be formed in an interval from a position overlapping the rear third discharge port 1313c2 to a position that is more forward than the front third discharge port 1313cl. In these cases, the first guide groove 1411 can also preferably be formed so as to overlap the front third discharge port 1313cl and / or the rear third discharge port 1313c2 by substantially 50% or more in the axial direction at a position that ensures the minimum seal distance. In these cases, the effects are similar to those of the foregoing embodiments, and a description thereof will be omitted.

[0229] In addition, another embodiment having a discharge passage is as follows.

[0230] That is, in the foregoing embodiments, the inlet of the discharge passage is formed with only one, but depending on the situation, the inlet of the discharge passage can also be formed with a plurality.

[0231] Figure 11 is a plan view showing another embodiment of a discharge passage.

[0232] Referring to Figure 11 , the discharge passage 140 of the present embodiment can include a first discharge guide portion 141, a second discharge guide portion 142, and a third discharge guide portion 143. The basic configuration of these first discharge guide portion 141, second discharge guide portion 142, and third discharge guide portion 143 and the effects thereof are the same as those of the foregoing embodiments, and a detailed description thereof will be replaced with a description of the foregoing embodiments.

[0233] However, the first discharge guide portion 141 of the present embodiment is configured with a first guide groove 1411 and a second guide groove 1412, and the first guide grooves 1411a, 1411b can be formed in two to constitute a pair.

[0234] In this case, the second guide groove 1412 can communicate with either side first guide groove (for example, the rear first guide groove) 1411b of the two first guide grooves 1411a, 1411b, and the two first guide grooves 1411 can communicate with each other. For example, as shown in Figure 11 , the plurality of first guide grooves 1411a, 1411b are spaced apart from each other at a predetermined interval in the circumferential direction, and are connected to each other by an intermediate connection groove 1411c, or although not shown, a portion of the two side first guide grooves 1411a, 1411b can be formed so as to overlap each other in the circumferential direction.

[0235] In this case, as described above, the discharge passage circular arc angle β is greater than or equal to the vane included angle θ, in other words, the vane included angle θ can be 120°, and the discharge passage circular arc angle β can be formed to be greater than or equal to about 120°. Thus, the discharge passage including the discharge port and the discharge passage 140 can extend to the circumferential range of the corresponding compression chamber or beyond the circumferential range of the corresponding compression chamber, thereby enabling minimization of the refrigerant residual amount in the corresponding compression chamber or the residual space S. Furthermore, since the circular arc length of the discharge passage is greater than or equal to the circular arc length of the compression chamber, continuous discharge can be achieved, thereby enabling reduction of pressure pulsation.

[0236] As described above, in the case where a plurality of first guide grooves 1411a, 1411b are formed, since the interval between the first sub-back pressure pocket 1325a and the second sub-back pressure pocket 1326b is narrow, even in the case where only one second guide groove 1412 is formed between these pockets, a plurality of first guide grooves 1411a, 1411b can be formed, thereby discharging the residual refrigerant or the compressed refrigerant more rapidly. Thereby, over-compression in the final compression chamber can be suppressed, thereby further improving motor efficiency.

[0237] In addition, another embodiment having a discharge passage is as follows.

[0238] That is, the aforementioned discharge passage is formed to have the same inner diameter, but depending on the case, the inner diameter of the discharge passage can be formed to be different.

[0239] Figure 12 is a perspective view showing another embodiment of a discharge passage, Figure 13 is Figure 12 a sectional view of

[0240] Referring to Figure 12 and Figure 13 , the discharge passage 140 of the present embodiment can include a first discharge guide portion 141, a second discharge guide portion 142, and a third discharge guide portion 143. The basic configuration of these first discharge guide portion 141, second discharge guide portion 142, and third discharge guide portion 143 and the effect thereof are similar to those of the aforementioned embodiment, and thus the detailed description thereof will be replaced with the description of the aforementioned embodiment.

[0241] Only, at one end or both ends of the second discharge guide portion 142 of the present embodiment, an expansion groove 1421, 1422 having an expanded cross-sectional area can be formed. For example, the expansion grooves 1421, 1422 are formed at both ends of the second discharge guide portion 142, and each of the expansion grooves 1421, 1422 can be formed to have the same shape as each other or different shapes from each other. Hereinafter, the case where the expansion grooves 1421, 1422 are formed to have the same shape at both ends of the first discharge guide portion 142 will be described as a center.

[0242] For example, the inner diameter of the second discharge guide 142 is formed to be the same as the width (or inner diameter) of the second guide groove 1412 of the first discharge guide 141, and each expansion groove 1421, 1422 can be formed to be larger than the inner diameter of the first end 142a and the second end 142b of the second discharge guide 142.

[0243] The expansion groove 1421 may be formed concentrically with the first end 142a of the second discharge guide 142, or it may be formed eccentrically relative to the first end 142a of the second discharge guide 142, depending on the situation.

[0244] As described above, when expansion grooves 1421 and 1422 are formed at both ends of the second discharge guide 142, the communication cycle between the first discharge guide 142 and the second discharge guide 142, as well as the communication cycle between the second discharge guide 142 and the third discharge guide 143, can be increased. Therefore, residual refrigerant can be discharged more quickly.

[0245] Although not illustrated, the expansion groove can be formed in the second guide groove 1412 of the first discharge guide 141 facing the first end 142a of the second discharge guide 142, or it can be formed in the first end 143a of the third discharge guide 143 facing the second end 142b of the second discharge guide 142. Alternatively, the expansion groove can be formed in both the first end 142a of the second discharge guide 142 and the second guide groove 1412 of the first discharge guide 141 facing thereto, or it can be formed in both the second end 142b of the second discharge guide 142 and the first end 143a of the third discharge guide 143 facing thereto. The effects of these embodiments may be similar to those of the foregoing embodiments, or they may improve the discharge effect of residual refrigerant.

[0246] Another embodiment with an exhaust pathway is as follows.

[0247] That is, the second discharge guide portion, which constitutes part of the aforementioned discharge passage, extends axially through the roller, but depending on the circumstances, it may also be formed at an angle relative to the axial direction.

[0248] Figure 14 This is an exploded perspective view illustrating yet another embodiment of the discharge pathway. Figure 15 yes Figure 14 Assembly sectional view, Figure 16 It is shown Figure 14 A schematic diagram showing the open state of the discharge pathway.

[0249] Reference Figures 14 to 16The discharge passage 140 of the present embodiment can include a first discharge guide portion 141, a second discharge guide portion 142, and a third discharge guide portion 143. The basic configuration of these first discharge guide portion 141, second discharge guide portion 142, and third discharge guide portion 143 and their effects are similar to those of the aforementioned embodiment, and thus detailed description thereof will be replaced with the description of the aforementioned embodiment.

[0250] However, the first end 142a of the first discharge guide portion 141 and the second discharge guide portion 142 of the present embodiment can be formed at a position more outward than the first sub back pressure bag 1325a and the second sub back pressure bag 1325b, in other words, a position more outward than the bag virtual circle C. As described in the aforementioned embodiment, the third discharge guide portion 143 can be formed at a position between the first main back pressure bag 1315a and the second main back pressure bag 1315b, in other words, inside the bag virtual circle C. Thus, the first discharge guide portion 141 can be formed of one guide groove unlike the aforementioned embodiment.

[0251] For example, the first discharge guide portion 141 can exclude the second guide groove 1412 in the aforementioned embodiment, and be formed of only the first guide groove 1411. In this case, the first guide groove 1411 can be formed to be larger than the inner diameter of the third discharge port 1313 or be formed in a long groove shape that is longer in the radial direction so that a part thereof is located at a position more inside than the outer peripheral surface 1342 of the roller 134.

[0252] As described above, in the case where the first discharge guide portion 141 is formed of only one guide groove, the first guide groove 1411, not only the processing of the first discharge guide portion 141 is easily performed, but also as the first discharge guide portion 141 is located at a position more outward than the first sub back pressure bag 1325a and the second sub back pressure bag 1325b, the design freedom for the shape or position of the first discharge guide portion 141 can be improved.

[0253] Although not illustrated, in the case where the first discharge guide portion 141 is formed of the first guide groove 1411 and the second guide groove 1412 as described in the aforementioned embodiment, the length of the second guide groove 1412 can be shorter. Also in this case, as the total length of the first discharge guide portion 141 becomes shorter, the processing of the first discharge guide portion 141 is easily performed, and as the first discharge guide portion 141 is located at a position more outward than the first sub back pressure bag 1325a and the second sub back pressure bag 1325b, the design freedom for the shape or position of the first discharge guide portion 141 can be improved.

[0254] In addition, as the first discharge guide 141 and the third discharge guide 143 are located on different axes from each other, the second discharge guide 142 can be formed obliquely. For example, a first end 142a of the second discharge guide 142 can be formed at a position more outward than the bag virtual circle C to be located on the same axis as the first discharge guide 141, and a second end 142b of the second discharge guide 142 can be formed inside the bag virtual circle C to be located on the same axis as the third discharge guide 143.

[0255] As described above, as the second discharge guide 142 is formed obliquely, the refrigerant passing through the second discharge guide 142 will be subjected to centrifugal force, and thus the refrigerant in the residual space S or the compression space V in the discharge stroke can be more rapidly moved to the third discharge guide 143 through the second discharge guide 142 and discharged.

[0256] In addition, another embodiment having a discharge passage is as follows.

[0257] That is, in the foregoing embodiment, the outlet of the discharge passage is formed through the main protrusion portion of the main bearing, but according to circumstances, the inlet of the discharge passage can also be formed on almost the same axis as the discharge port.

[0258] Figure 17 And Figure 18 is a perspective view and a sectional view showing another embodiment of the discharge passage.

[0259] Referring to Figure 17 and Figure 18 , the discharge passage 140 of the present embodiment can include a first discharge guide 141, a second discharge guide 142, and a third discharge guide 143. The basic configuration of these first discharge guide 141, second discharge guide 142, and third discharge guide 143 and the effects thereof are the same as those of the foregoing embodiment, and thus a detailed description thereof will be replaced by the description of the foregoing embodiment.

[0260] However, a first end 143a of the third discharge guide 143 of the present embodiment is opened toward the lower surface of the main plate portion 1311 constituting the main sliding surface 1311a facing the roller 134 in the axial direction, and a second end 143b of the third discharge guide 143 can be opened from the upper surface of the main plate portion 1311 toward the discharge space portion 1372 of the discharge muffler 137. In other words, as the second end 143b of the third discharge guide 143 is formed in the main plate portion 1311, the height H3' of the second end 143b of the third discharge guide 143 can be formed to be lower than the height H1 of the discharge space portion 1372.

[0261] In this case, the second end 143b of the third discharge guide portion 143 can be positioned between the first main back pressure pocket 1315a and the second main back pressure pocket 1315b and formed separately from each of the discharge valves 1361, 1362, 1363. Therefore, the refrigerant discharged by the third discharge guide portion 143 to the discharge space 1372a of the discharge muffler 137 can not be blocked by each of the discharge valves 1361, 1362, 1363, but always open to the discharge space 1372a of the discharge muffler 137.

[0262] As described above, in the case where the third discharge guide portion 143 is formed so as to penetrate the main plate portion 1311, the length of the third discharge guide portion 143 can be shortened, thereby easily processing the third discharge guide portion 143. In particular, even in the case where the inner diameter of the third discharge guide portion 143 is small, the processing can be easily performed to reduce the manufacturing cost.

[0263] In addition, as the third discharge guide portion 143 is formed in the main plate portion 1311, the length of the first discharge guide portion 141, in other words, the length of the second guide groove 1412, can be shortened, thereby easily processing the first discharge guide portion 141 accordingly. Furthermore, according to the case, the second guide groove 1412 can be formed outside the first main back pressure pocket and the second main back pressure pocket, that is, at a position further outside than the pocket virtual circle C connecting the outer circumferential surface of the first main back pressure pocket 1315a and the outer circumferential surface of the second main back pressure pocket 1315b. In this case, a wider second guide groove 1412 or a plurality of second guide grooves 1412 can be formed, thereby more rapidly discharging the refrigerant accordingly.

[0264] In addition, although not shown, the discharge ports 1313a, 1313b, 1313c can be formed in the sub bearing 132. In this case, the first discharge guide portion 141 constituting the discharge passage 140 can be formed in the main bearing 131, the second discharge guide portion 142 constituting the discharge passage 140 can be formed in the roller 134, and the third discharge guide portion 143 constituting the discharge passage 140 can be formed in the sub bearing 132. In this case, the constitution of the first discharge guide portion 141, the second discharge guide portion 142, and the third discharge guide portion 143 and the effect thereof can be formed the same as the aforementioned embodiment. The description thereof will be replaced by the description of the aforementioned embodiment.

[0265] Further, in the foregoing embodiment, the discharge grooves 1314a, 1314b can also be extended to be formed in a part of the discharge ports. For example, the first discharge port 1313a and the second discharge port 1313b are respectively extended to be formed with the discharge grooves 1314a, 1314b, and each of the discharge grooves 1314a, 1314b can be extended in an arc shape along the compression direction (the rotation direction of the roller). Thus, the refrigerant that is not discharged in the preceding compression chamber can be guided to the discharge ports 1313a, 1313b that communicate with the following compression chamber through each of the discharge grooves 1314a, 1314b, and thus can be discharged together with the refrigerant that is compressed in the following compression chamber. Thereby, by minimizing the residual refrigerant in the compression space V, over-compression is suppressed, and thus the compressor efficiency can be improved.

Claims

1. A rotary compressor, wherein comprises: a housing; a cylinder provided in an inner space of the housing to form a compression space; a rotary shaft rotatably penetrating the cylinder; a roller provided at the rotary shaft to be rotatable in an inner space of the cylinder and eccentrically disposed with respect to a center of the compression space to have a contact point at which an outer circumferential surface of the roller contacts an inner circumferential surface of the cylinder; a vane slidably inserted into a vane groove provided at the roller to rotate together with the roller; a main bearing and a sub bearing disposed at both axial sides of the cylinder to form the compression space together with the cylinder; and a discharge passage through which a refrigerant is discharged from the compression space to the inner space of the housing, the discharge passage comprises: a first discharge guide portion provided at one of the main bearing and the sub bearing; a second discharge guide portion penetrating between both axial ends of the roller and communicating with the first discharge guide portion; and a third discharge guide portion provided at the other of the main bearing and the sub bearing and communicating with the first discharge guide portion through the second discharge guide portion. 2.The rotary compressor according to claim 1, wherein the second discharge guide portion periodically communicates with at least one of the first discharge guide portion and the third discharge guide portion as the roller rotates. 3.The rotary compressor according to claim 1, wherein the first discharge guide portion and the third discharge guide portion communicate with each other through the second discharge guide portion according to a rotation angle of the roller. 4.The rotary compressor according to claim 1, wherein a number of the second discharge guide portions is greater than a number of the first discharge guide portions or a number of the third discharge guide portions. 5.The rotary compressor according to claim 1, wherein one of the first discharge guide portion and the third discharge guide portion is provided, a plurality of the second discharge guide portions are provided and formed at a predetermined interval in a circumferential direction. 6.The rotary compressor according to claim 5, wherein the first discharge guide portion and the third discharge guide portion facing the second discharge guide portion are formed on the same axis, the second discharge guide portions are penetrated in an axial direction. 7.The rotary compressor according to claim 5, wherein the first discharge guide portion and the third discharge guide portion facing the second discharge guide portion are formed on different axes from each other, the second discharge guide portions are obliquely penetrated with respect to the axial direction. 8.The rotary compressor according to claim 1, wherein the first discharge guide portion comprises: a first guide groove communicating with the compression space; and a second guide groove communicating at one end with the first guide groove and at the other end with the second discharge guide portion, the second guide groove extends closer to a rotation center of the roller than the first guide groove. 9.The rotary compressor according to claim 8, wherein at least one discharge outlet is formed at the main bearing or the sub bearing, ​ At least a portion of the first guide groove overlaps the discharge port in the axial direction.

10. The rotary compressor of claim 9, wherein At least 50% or more of the first guide groove overlaps the discharge port in the axial direction.

11. The rotary compressor of claim 8, wherein At least one discharge port is formed in the main bearing or the auxiliary bearing, The cross-sectional area of the first guide groove is greater than or equal to the cross-sectional area of the discharge port that overlaps the first guide groove in the axial direction.

12. The rotary compressor of claim 8, wherein At least one discharge port is formed in the main bearing or the auxiliary bearing, The first guide groove is located on a more rear side than the discharge port that overlaps the first guide groove in the axial direction, with reference to the direction of rotation of the roller.

13. The rotary compressor of claim 12, wherein A plurality of the first guide grooves are circumferentially provided, and an intermediate connection groove that connects the plurality of the first guide grooves to each other is provided between the plurality of the first guide grooves.

14. The rotary compressor of claim 8, wherein At least one discharge port is formed in the main bearing or the auxiliary bearing, The first guide groove is located on a more front side than the discharge port that overlaps the first guide groove in the axial direction, with reference to the direction of rotation of the roller.

15. The rotary compressor of claim 14, wherein A plurality of discharge ports are formed in the main bearing or the auxiliary bearing, The first guide groove is located between the plurality of the discharge ports to respectively communicate with the plurality of the discharge ports.

16. The rotary compressor of claim 8, wherein A plurality of back pressure pockets having different pressures from each other are circumferentially formed apart from each other in a side surface of the main bearing and a side surface of the auxiliary bearing that face the roller in the axial direction, The second guide groove is formed more slender and longer than the first guide groove, and is provided between circumferences of the plurality of the back pressure pockets.

17. The rotary compressor of claim 1, wherein A plurality of the vane grooves are circumferentially formed, The second discharge guide portions are respectively provided between each of the vane grooves that are circumferentially adjacent to each other.

18. The rotary compressor of claim 17, wherein An expansion groove whose cross-sectional area is expanded is formed in both ends of the second discharge guide portion and at least one of an end of the first discharge guide portion and an end of the third discharge guide portion that face the both ends of the second discharge guide portion.

19. The rotary compressor of claim 1, wherein A plurality of back pressure pockets having different pressures from each other are circumferentially formed apart from each other in a side surface of the main bearing and a side surface of the auxiliary bearing that face the roller in the axial direction, The third discharge guide portion is provided between circumferences of the plurality of the back pressure pockets.

20. The rotary compressor of claim 1, wherein A discharge muffler that accommodates a discharge port is provided in the main bearing or the auxiliary bearing, The third discharge guide portion is opened from the outside of the discharge muffler toward the inside of the housing.

21. The rotary compressor of claim 20, wherein the main bearing or the auxiliary bearing includes: a plate portion combined with an axial side of the cylinder tube; and a boss portion extending in an axial direction from an axial side of the plate portion so as to be penetrated by the rotary shaft, the third discharge guide portion is opened from the boss portion toward the inside of the housing.

22. The rotary compressor of claim 1, wherein a discharge muffler accommodating a discharge port is provided in the main bearing or the auxiliary bearing, the third discharge guide portion is opened toward an inside space of the discharge muffler.

23. The rotary compressor of claim 22, wherein the main bearing or the auxiliary bearing includes: a plate portion combined with an axial side of the cylinder tube; and a boss portion extending in an axial direction from the plate portion so as to be penetrated by the rotary shaft, the third discharge guide portion penetrates the plate portion.

24. The rotary compressor of any one of claims 1 to 23, wherein a discharge port opened and closed by a discharge valve is provided in one of the main bearing and the auxiliary bearing, the first discharge guide portion is formed in the other of the main bearing and the auxiliary bearing.

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