Rotary compressor

Abstract

A rotary compressor is disclosed. The rotary compressor comprises a casing, a cylinder, a bearing plate, a roller, vanes and a plurality of pressing passages, wherein the plurality of pressing passages penetrate the discharge side of a vane slot from the outer peripheral surface of the cylinder, and can be spaced apart from each other in the height direction of the vane slot. Therefore, each of the pressing passages is formed at upper and lower ends or near both ends of the vane corresponding to both ends of the vane slot in the height direction, so as to ensure the straightness of the vane such that the vane can be more stably supported.

Description

rotary compressor

[0001] The present invention relates to a rotary compressor.

[0002] A rotary compressor compresses refrigerant using a roller that rotates within the cylinder's compression space and vanes that contact or are joined to the outer surface of the rollers to divide the cylinder's compression space into multiple compartments. Centered around the vanes, the compression space can be divided into a suction chamber, which communicates with the suction port, and a discharge chamber, which communicates with the discharge port.

[0003] Rotary compressors can be categorized into rotary roller and hinge vane types, depending on the combination of rollers and vanes. In the rotary roller type, the vanes slide against the outer surface of the roller, while in the hinge vane type, the vanes are hinged to the roller so that they can rotate.

[0004] In each rotary compressor, vane slots are formed radially on the inner surface of the cylinder, and an inlet forming an intake passage is formed on one side of the circumference based on the vane slots, and an outlet forming a discharge passage or a discharge guide groove communicating with the outlet is formed on the other side. In particular, a partition is provided between the vane slots and the suction port to separate the vane slots (or the discharge port) from the suction port.

[0005] The suction port of the rotary compressor may be formed by penetrating from the outer surface of the cylinder to the inner surface, or may be formed by penetrating from the outer surface of the cylinder to the inner surface, but opening to both axial sides on the inner surface.

[0006] In a rotary compressor, vanes are in contact with or coupled to the outer surface of rollers to divide the compression space into a suction chamber and a discharge chamber, and when the rotary shaft rotates, the rollers coupled to the eccentric portion of the rotary shaft rotate to move the refrigerant from the suction chamber toward the discharge chamber, thereby compressing the refrigerant. At this time, the vanes are pushed circumferentially (laterally) toward the suction chamber by the pressure load of the discharge chamber, and the suction side of the vanes is pressed against the circumferential inner surface of the vane slots that form the bulkhead. Then, if the vanes cannot smoothly enter and exit the vane slots, the motor input may increase, which may lower the compressor efficiency.

[0007] This can be even more pronounced when the suction port penetrates radially. That is, as the suction port penetrates radially around the rotating shaft, the periphery of the suction port connects to the inner surface of the cylinder. This can prevent the baffle between the suction port and the vane slot from securing adequate elasticity, preventing it from adequately absorbing the pressure load in the discharge chamber. This can further increase motor input, as the vanes may press excessively against the baffle forming the inner surface of the vane slot, preventing them from reciprocating smoothly.

[0008] Conversely, if part of the intake port, i.e., the axial side, is open, the baffle can be separated from the inner surface of the cylinder. This allows the baffle to retain elasticity compared to the previously described case. However, even in this case, the vanes can still be pressed against the side surfaces of the vane slots forming the baffle due to the pressure load from the discharge chamber.

[0009] Due to this, in conventional rotary compressors, when the vanes reciprocate inside the vane slots, the compression surface of the vanes and the suction side of the vane slots come into excessive contact, which increases friction loss and reduces compressor efficiency, or noise may be generated due to abnormal behavior of the vanes.

[0010] The purpose of the present invention is to provide a rotary compressor in which energy efficiency can be improved by improving excessive adhesion of the vane to the inner surface of the vane slot.

[0011] Another object of the present invention is to provide a rotary compressor capable of ensuring straightness of the vane by forming sufficient back pressure between one side of the vane and the discharge side of the vane slot facing it.

[0012] Another object of the present invention is to provide a rotary compressor capable of ensuring smooth reciprocating movement of the vane while forming sufficient back pressure between one side of the vane and the discharge side of the vane slot facing it.

[0013] Another object of the present invention is to provide a rotary compressor capable of smoothly supplying oil between a vane and a vane slot while forming sufficient back pressure between one side of a vane and the discharge side of a vane slot facing it.

[0014] In order to achieve the object of the present invention, a rotary compressor including a casing, a cylinder, a bearing plate, rollers, vanes, and a plurality of pressurization passages may be provided. The cylinder may be provided in an internal space of the casing, and may be provided with vane slots. The bearing plates may be provided on each of the axial sides of the cylinder to support a rotational shaft and form a compression chamber together with the cylinder. The rollers may be provided inside the cylinder and may rotate together with the rotational shaft. The vanes may be inserted into vane slots of the cylinder to reciprocate. The plurality of pressurization passages may be formed through the cylinder to communicate the vane slots with the internal space of the casing. The plurality of pressurization passages may be formed to penetrate from an outer peripheral surface of the cylinder to a discharge side of the vane slots, and to be spaced apart from each other along a height direction of the vane slots. Through this, since the pressurized passage is formed at the upper and lower ends or near the ends of the vane corresponding to the height-wise ends of the vane slot, the moment generated during the reciprocating motion of the vane can be effectively reduced, thereby supporting the vane more stably.

[0015] For example, the plurality of pressurized passages may be spaced apart from each other by a predetermined distance on both sides along the height direction of the vane slot at the mid-height of the vane slot. Through this, the vane can be supported more stably while being pressurized at both upper and lower ends within the vane slot.

[0016] As another example, the plurality of pressurized passages may be formed symmetrically relative to each other based on the mid-height of the vane slot. This allows the pressures transmitted to the upper and lower sides of the vane through the plurality of pressurized passages to be of approximately equal magnitude, thereby supporting the vane more stably.

[0017] For example, each of the plurality of pressurized passages may be formed by a single hole. This allows the pressurized passages to be easily processed while securing their cross-sectional area.

[0018] Additionally, each of the plurality of pressurized passages may be formed with a plurality of holes. This allows the cross-sectional area of ​​the pressurized passages to be minimized, thereby reducing the surface pressure on the vane slot.

[0019] As another example, the plurality of pressurized passages may be formed so that the length in the height direction of the vane slot is less than 1 / 4 of the total height of the vane slot. This can suppress the compression back surface of the vane from being excessively pressed against the suction side surface of the vane slot due to the high-pressure oil and / or refrigerant flowing in through the pressurized passage, thereby increasing friction loss.

[0020] As another example, the plurality of pressurized passages may be formed such that the length between the two ends in the height direction of the vane slots is greater than the length between the two ends in the reciprocating direction of the vanes. This can suppress the compression back surface of the vanes from being excessively pressed against the suction side surface of the vane slots due to high-pressure oil and / or refrigerant flowing in through the pressurized passages, thereby increasing friction loss.

[0021] For example, the plurality of pressurized passages may be formed at predetermined sealing distances from both ends of the vane slot along the height direction of the vane slot. This prevents high-pressure oil and / or refrigerant flowing into the vane slot through the pressurized passage from leaking to the upper and lower ends of the vane, thereby maintaining smooth reciprocating motion of the vane.

[0022] Specifically, the sealing distance may be formed at equal intervals from both ends of the vane slot. This allows high-pressure oil and / or refrigerant flowing into the vane slot through the pressurized passage to pressurize the same location from both ends of the vane, thereby more stably supporting the vane.

[0023] As another example, the plurality of pressurized passages may be formed to overlap the side surface of the vane at the bottom dead center of the vane. This can prevent high-pressure oil and / or refrigerant flowing into the vane slot through the pressurized passages during the backward movement of the vane from interfering with the reciprocating motion of the vane.

[0024] As another example, the plurality of pressurized passages may be formed symmetrically on both sides along the reciprocating direction of the vane, based on the height direction of the vane slot. This allows for easy processing of the plurality of pressurized passages while ensuring an optimal cross-sectional area for the plurality of pressurized passages.

[0025] As another example, each of the plurality of pressurized passages may be formed such that the cross-sectional area of ​​the outer circumference side adjacent to the outer circumference of the cylinder, based on the height direction of the vane slot, is larger than the cross-sectional area of ​​the inner circumference side adjacent to the inner circumference of the cylinder. This allows the center of pressure of the pressurized passage that pressurizes the vane to be as close as possible to the bottom dead point of the vane, thereby supporting the vane more stably.

[0026] As another example, the plurality of pressurized passages may be formed in a direction orthogonal to the reciprocating direction of the vane. This can minimize the length of the pressurized passages, thereby allowing the oil and / or refrigerant in the casing to quickly flow into the vane slots.

[0027] As another example, the vane may be supported by an elastic member while in sliding contact with the outer surface of the roller, and a spring receiving groove may be formed on both sides of the vane slot facing both sides of the vane by being sunken to a preset depth so that the elastic member may be inserted. The plurality of pressurized passages may be formed on both sides with a preset interval in the height direction of the vane slot centered on the spring receiving groove. Through this, the straightness of the vane is secured by the oil and / or refrigerant transmitted through the plurality of pressurized passages while the vane is in sliding contact with the roller, thereby reducing the frictional loss between the vane and the vane slot.

[0028] For example, the plurality of pressure passages may be formed at equal intervals from the center of the spring receiving groove. This allows the pressure force transmitted to the vane through the plurality of pressure passages to be formed to be of approximately equal magnitude, thereby supporting the vane more stably.

[0029] As another example, the vane may be rotatably coupled to the outer surface of the roller, and both sides of the vane slot facing both sides of the vane may be formed flat. The plurality of pressurized passages may be formed at equal intervals at the mid-height of the vane slot. Through this, while the vane is rotatably coupled to the roller, the straightness of the vane is secured by the oil and / or refrigerant transmitted through the plurality of pressurized passages, thereby reducing the frictional loss between the vane and the vane slot.

[0030] A rotary compressor according to the present invention comprises a casing, a cylinder, a bearing plate, a roller, a vane, and a plurality of pressurized passages, wherein the plurality of pressurized passages penetrate from the outer peripheral surface of the cylinder to the discharge side of the vane slot and may be formed to be spaced apart from each other along the height direction of the vane slot. Accordingly, since the pressurized passages are formed at the upper and lower ends or near the ends of the vane corresponding to the height direction ends of the vane slot, the straightness of the vane is secured, thereby supporting the vane more stably.

[0031] In the rotary compressor according to the present invention, a plurality of pressurized passages can be spaced apart from each other by a predetermined distance along the height direction of the vane slot at the mid-height of the vane slot. Through this, the vane can be supported more stably while being pressurized at both upper and lower ends within the vane slot.

[0032] The rotary compressor according to the present invention can have a plurality of pressurized passages formed symmetrically relative to each other based on the mid-height of the vane slots. This allows the pressures transmitted to the upper and lower sides of the vane through the plurality of pressurized passages to be of approximately equal magnitude, thereby supporting the vane more stably.

[0033] The rotary compressor according to the present invention can have a plurality of pressurized passages formed to overlap the side surface of the vane at the bottom dead center of the vane. This can prevent high-pressure oil and / or refrigerant flowing into the vane slots through the pressurized passages when the vane moves backward from interfering with the reciprocating motion of the vane.

[0034] Fig. 1 is a longitudinal cross-sectional view showing a rotary compressor according to the present embodiment.

[0035] Fig. 2 is a perspective view showing a portion of the compression section in Fig. 1.

[0036] Figure 3 is a perspective view showing the pressurized passage in Figure 2.

[0037] Fig. 4 is a plan view showing a state in which a vane is positioned at the bottom dead center in a compression section to which a pressurized passage according to the present embodiment is applied.

[0038] Figure 5 is a cross-sectional view taken along the line “VV” of Figure 4.

[0039] Fig. 6 is a schematic diagram illustrating the change in state of the vane according to the pressurized passage of the present embodiment.

[0040] Fig. 7 is a plan view showing a state in which a vane is positioned at top dead center in a compression section to which a pressurized passage according to the present embodiment is applied.

[0041] Figure 8 is a cross-sectional view taken along the line “Ⅷ-Ⅷ” of Figure 7.

[0042] Figure 9 is a side view showing another example of a pressurized passage.

[0043] Fig. 10 is a side view showing another embodiment of a pressurized passage.

[0044] Fig. 11 is a plan view showing an example of a pressurized passage applied to another embodiment of a rotary compressor.

[0045] Hereinafter, a rotary compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings.

[0046] Typically, a rotary compressor may have only one cylinder, which constitutes the compression space, or it may have multiple cylinders stacked axially. A single-cylinder rotary compressor is defined as a single-cylinder rotary compressor, while a multiple-cylinder rotary compressor is defined as a double-cylinder rotary compressor. The following description uses a single-cylinder rotary compressor as an example. However, the same principles apply to double-cylinder rotary compressors.

[0047] In addition, the rotary compressor can be formed into a vertical type in which the electric motor and the compression unit are arranged along the axial direction of the rotational shaft, but are arranged in a direction almost orthogonal to the installation surface, and a horizontal type in which the electric motor and the compression unit are arranged almost parallel to the installation surface. The following description will be given using a vertical rotary compressor as an example. However, the same can be applied to a horizontal rotary compressor. The following description can be given by defining the axial direction of the rotational shaft as the up-down direction, and in this case, the side facing away from the installation surface can be understood as the upper side, and the side adjacent to the installation surface can be understood as the lower side.

[0048] Fig. 1 is a cross-sectional view showing a rotary compressor according to the present embodiment, Fig. 2 is a perspective view showing a part of a compression section in Fig. 1, and Fig. 3 is a perspective view showing a pressurization passage in Fig. 2.

[0049] Referring to Fig. 1, in a single-stage rotary compressor (hereinafter, abbreviated as a rotary compressor) according to the present embodiment, an electric motor (20) is installed in the internal space of a casing (10), and a compression unit (30) is installed on the lower side of the electric motor (20) to suck in refrigerant, compress it, and then discharge it into the internal space (10a) of the casing (10). The electric motor (20) and the compression unit (30) are mechanically connected by a rotary shaft (23).

[0050] The casing (10) according to the present embodiment includes a cylindrical shell (11), an upper cap (12), and a lower cap (13). The cylindrical shell (11) is open at both upper and lower ends, and the upper cap (12) and the lower cap (13) cover both upper and lower ends of the cylindrical shell (11) to seal the internal space (10a) of the casing (10). Accordingly, the internal space (10a) of the casing (10) can have an oil storage space (10b) formed in the lower half and an oil separation space (10c) formed in the upper half, respectively.

[0051] A suction pipe (15) connected to the outlet side of the accumulator (40) may be coupled to the lower half of the cylindrical shell (11), and a discharge pipe (16) connected to the discharge side refrigerant pipe on the inlet side of a condenser (not shown) may be coupled to the upper cap (12). The suction pipe (15) may pass through the cylindrical shell (11) and be directly connected to the suction port (331) of the cylinder (33) to be described later, and the discharge pipe (16) may pass through the upper cap (12) and be connected to the internal space (10a) of the casing (10). The suction port (331) of the cylinder (33) forming the suction passage will be described later.

[0052] The electric motor (20) according to the present embodiment includes a stator (21) and a rotor (22).

[0053] The stator (21) is press-fitted and fixed inside the casing (10), and the rotor (22) is rotatably inserted inside the stator (21). A rotational shaft (23) can be press-fitted and coupled to the center of the rotor (22).

[0054] The rotation shaft (23) may be formed in a hollow shape. One end of the rotation shaft (23) may be extended along the same axis so as to be pressed into the rotor (22), and an eccentric portion (23a) may be formed on the end of the rotation shaft (23) so that a roller (or rolling piston) (34) to be described later may be eccentrically coupled thereto.

[0055] Referring to FIGS. 1 and 2, the compression unit (30) according to the present embodiment includes a main bearing plate (hereinafter, main bearing) (31), a sub-bearing plate (hereinafter, sub-bearing) (32), a cylinder (33), and a roller (34).

[0056] The main bearing (31) is formed in an annular shape and is fixedly connected to the inner surface of the cylindrical shell (11), and the sub-bearing (32) is formed in an annular shape and can be supported by being bolted to the main bearing (31) with the cylinder (33) interposed therebetween.

[0057] Although not shown in the drawing, the sub-bearing (32) may be fixed to the cylindrical shell (11), and the main bearing (31) may be fastened to the sub-bearing (32), or both the main bearing (31) and the sub-bearing (32) may be fastened to the cylindrical shell (11). In addition, the cylinder (33) may be fixed to the cylindrical shell (11), and the main bearing (31) and the sub-bearing (32) may be fastened to and supported by the cylinder (33).

[0058] The main bearing (31) and the sub-bearing (32) support the rotation shaft (23), and the cylinder (33) forms a compression space (Vc) together with the main bearing (31) and the sub-bearing (32).

[0059] A discharge port (311) for discharging compressed refrigerant from a compression space (Vc) is formed in the main bearing (31), and a discharge valve (312) for opening and closing the discharge port (311) is installed at an end of the discharge port (311). A discharge cover (37) having a discharge space (37a) is installed on one side of the main bearing (31), and the discharge cover (37) opens toward the internal space (10a) of the casing (10). Accordingly, the refrigerant discharged through the discharge space (37a) of the discharge cover (37) is discharged into the internal space (10a) of the casing (10), so that the internal space (10a) of the casing (10) forms a discharge pressure.

[0060] Although not shown in the drawing, a discharge port (not shown) may be formed in the sub-bearing (32). In this case, a discharge cover (not shown) having a discharge space (not shown) may be installed on one side of the sub-bearing (32).

[0061] Referring to FIGS. 1 and 2, the cylinder (33) may be provided so that at least a portion thereof is submerged in the oil storage space (10b) of the casing (10). Accordingly, oil filled in the oil storage space (10b) may flow into the vane slot (332) described later to lubricate the space between the vane slot (332).

[0062] In addition, a suction port (331) forming a suction passage is formed in the cylinder (33), and a suction pipe (15) is inserted and connected to the suction port (331). Accordingly, the compression space (Vc) can be connected to the suction pipe (15) through the suction port (331).

[0063] In addition, a vane slot (332) is formed in the cylinder (33) into which a vane (35) is slidably inserted. In other words, the vane slot (332) can be formed between the suction port (331) and the discharge port (311) in the circumferential direction. Accordingly, the suction port (331) and the discharge port (311) can be separated by .

[0064] The vane slot (332) is formed by cutting a predetermined depth from the inner surface (33a) of the cylinder (33) toward the outer surface (33b). In other words, the vane slot (332) is formed by cutting so as to penetrate both axial ends of the cylinder (33). Accordingly, the cylinder (33) is cut in the circumferential direction at the vane slot (332), while the outer surface of the vane slot (332) is connected, so that the cylinder (33) forms an annular shape.

[0065] In addition, the vane slot (332) is formed with a slot portion (332a) and a space portion (332b) that are continuously formed in the radial direction of the rotation axis (23) on the inner surface (33a) of the cylinder (33). The slot portion (332a) is covered by the main bearing (31) and the sub-bearing (32), and the space portion (332b) can be exposed to the outer side of the main bearing (31) and the sub-bearing (32). Accordingly, as described above, the oil stored in the oil storage space (10b) of the casing (10) can flow into the slot portion (332a) through the space portion (332b) to lubricate the space between the vane slot (332). However, for convenience, the slot portion (332a) and the space portion (332b) may be defined and described as a vane slot (332) in the following.

[0066] Referring to FIGS. 2 and 3, a pressurized passage (335) may be formed on the outer circumferential side of the vane slot (332) to communicate with the inner space of the casing. In other words, the pressurized passage (335) may be formed to penetrate from the outer circumferential side of the cylinder (33) toward the vane slot (332). Accordingly, oil stored in the inner space (10a) of the casing (10) is supplied to the vane slot (332) through the pressurized passage (335). Through this, the vane (35) is supported in the circumferential direction (in the width direction of the first vane) by the oil flowing into the vane slot (332) from the inner space (more precisely, the oil storage space) (10a) of the casing (10) through the pressurized passage (335), thereby stabilizing the behavior of the vane. The pressurized passage (335) will be described later.

[0067] A partition wall (333) is formed between the suction port (331) and the vane slot (332). The partition wall (333) can be defined by the circumferential inner surface of the suction port (331) and the circumferential inner surface of the vane slot (332) adjacent thereto. Accordingly, the suction port (331) and the vane slot (332) are separated circumferentially by the partition wall (333).

[0068] Referring to FIGS. 1 and 3, the roller (34) is formed in a cylindrical shape so as to be rotatably inserted into the eccentric portion (23a) of the rotational shaft (23). For example, the roller (34) may be formed in a circular shape in which the inner and outer peripheries thereof have the same center, or in some cases, the inner and outer peripheries of the roller (34) may be formed in an eccentric circular shape in which the inner and outer peripheries of the roller (34) have different centers.

[0069] The axial height of the roller (34) is formed to be approximately the same as the height of the inner surface (33a) of the cylinder (33). However, the axial height of the roller (34) may be formed to be slightly smaller than the height of the inner surface (33a) of the cylinder (33). Accordingly, the roller (34) can slide while being axially supported against the lower surface of the main bearing (31) and the upper surface of the sub-bearing (32) facing it.

[0070] The vane (35) may be formed in a flat shape with a predetermined length and thickness so as to be inserted into the vane slot (332) and reciprocate in the radial direction of the rotation axis (23) (or in the longitudinal direction of the vane slot) in the vane slot (332). For example, the vane (35) may be formed in an overall rectangular hexahedral shape. The vane (35) may be formed to have a length such that the vane (35) remains in the vane slot (332) even when the roller (34) has completely moved to the opposite side of the vane slot (332).

[0071] In the drawing, the unexplained symbol 334 is a discharge guide groove forming a discharge passage, and 36 is a vane spring.

[0072] The rotary compressor according to the present embodiment as described above operates as follows.

[0073] That is, when power is applied to the stator (21), the rotor (22) and the rotation shaft (23) rotate inside the stator (21), causing the roller (34) to rotate, and as the volume of the suction chamber of the compression space (Vc) changes according to the rotational movement of the roller (34), the refrigerant is sucked into the compression space (Vc) of the cylinder (33).

[0074] The refrigerant sucked into this compression space (Vc) is compressed in the compression space (Vc) by the rotational movement of the roller (34), and this compressed refrigerant is discharged into the discharge space (37a) of the discharge cover (37) through the discharge port (311) provided in the main bearing (31).

[0075] The refrigerant discharged into this discharge space (37a) is discharged into the internal space (more precisely, the oil separation space) (10c) of the casing (10) and repeats a series of processes of circulating through the refrigeration cycle.

[0076] Meanwhile, in the process of compressing the refrigerant in the compression space (Vc) as described above, the vane (35) generates a gas force (F1) in the direction in which the roller (34) rotates. This gas force (F1) acts on the discharge chamber side (hereinafter, compression side) (332a1) of the vane (35) to pressurize the vane (35) from the discharge chamber toward the suction chamber, that is, toward the side where the suction port (331) is formed. At this time, due to the pressing force applied to the compression side (35a) of the vane (35), the vane (35) may excessively adhere to the circumferential inner side (hereinafter, suction side) (332a2) of the vane slot (332) adjacent to the suction port (331) or the behavior of the vane (35) may become unstable. Then, the motor efficiency may be lowered due to friction loss between the vane slot (332), which may lower the compression performance, or abnormal noise may increase due to collision between the vane slot (332).

[0077] Accordingly, in the present embodiment, a pressurized passage (335) is formed on the compression surface (35a) side of the vane (35) so that relatively high pressure oil and / or refrigerant is supplied to the compression surface (35a) side of the vane (35), thereby suppressing the compression back surface (35b) of the vane (35) from excessively contacting the suction side surface (332a2) of the vane slot (332). Hereinafter, the compression surface (35a) of the vane (35) may be understood to refer to the side toward the discharge port (311), and the compression back surface (35b) may be understood to refer to the side toward the suction port (331), respectively.

[0078] However, in this case, in order to ensure that the oil discharge pressure is evenly applied to the compression surface (35a) of the vane (35), it may be advantageous to form the cross-sectional area of ​​the pressurized passage (335) as large as possible or to form it as close as possible to the upper and lower ends of the vane (35) based on the axial direction of the rotational shaft (23) (or the height direction of the vane slot). In consideration of this, as in the present embodiment, the pressurized passage (335) may be formed to be close to the upper and lower ends of the vane slot (332) in the height direction, that is, based on the axial direction of the rotational shaft (23). Hereinafter, the height direction of and / or the vane slot (332) may be defined as the axial direction of the rotational shaft (23), and the reciprocating direction of the vane (35) and / or the longitudinal direction of the vane slot (332) may be defined as the radial direction of the rotational shaft (23). In addition, in the following description, the discharge side can be defined as the opposite side of the suction port (331) based on the vane slot (332), and the suction side can be defined as the side toward the suction port (331).

[0079] FIG. 4 is a plan view showing a state in which a vane is positioned at top dead center in a compression section to which a pressurized passage according to the present embodiment is applied, FIG. 5 is a cross-sectional view taken along the line “Ⅴ-Ⅴ” of FIG. 4, and FIG. 6 is a schematic diagram showing a change in the state of a vane according to the pressurized passage according to the present embodiment.

[0080] Referring to FIGS. 4 to 6, the cylinder (33) according to the present embodiment is formed in an annular shape as described above, but the inner peripheral surface (33a) of the cylinder (33) is cut by the vane slot (332), whereas the outer peripheral surface (33b) of the cylinder (33) is connected along the circumferential direction even on the outer side of the vane slot (332). In other words, when projected in the axial direction, the inner peripheral surface (33a) of the cylinder (33) forms an incomplete curved surface, whereas the outer peripheral surface (33b) of the cylinder (33) forms a complete curved surface.

[0081] However, the vane slot (332) of the cylinder (33) may be connected to the internal space (more precisely, the oil storage space) (10a) of the casing (10) through the pressurized passage (335). For example, the pressurized passage (335) according to the present embodiment may penetrate the interior of the cylinder (33), and one end of the pressurized passage (335) may be connected to the internal space (10a) of the casing (10) through the outer circumferential surface (33b) of the cylinder (33), and the other end of the pressurized passage (335) may be connected to the discharge side surface (332a1) of the vane slot (332) through the discharge side surface (332a1) of the vane slot (332). Accordingly, oil and / or refrigerant in the storage space (10b) of the casing (10) that creates a relatively high pressure can flow through the pressurized passage (335) toward the discharge side (332a1) of the vane slot (332) to pressurize the vane (35) toward the suction side (332a2) of the vane slot (332).

[0082] In addition, it may be preferable that the pressurized passage (335) according to the present embodiment be formed as close to the upper and lower ends of the vane (35) as possible. For example, the pressurized passage (335) may be formed such that the length (L11) between the two ends in the height direction of the vane slot (332) is greater than the length (L12) between the two ends in the reciprocating direction of the vane (35). In other words, when the height direction of the vane slot (332) (or the axial direction of the rotational axis) is referred to as the longitudinal direction and the reciprocating direction of the vane (35) (or the radial direction of the rotational axis) is referred to as the transverse direction, the longitudinal length (L11) of the pressurized passage (335) may be formed to be greater than the transverse length (L12). Accordingly, high-pressure oil and / or refrigerant flowing into the vane slot (332) through the pressurized passage (335) supports both ends of the vane (35) in the height direction or near both ends, thereby supporting the vane (35) more stably.

[0083] In this case, the pressurized passage (335) according to the present embodiment may be formed at both ends of the vane slot (332) along the height direction of the vane slot (332) with a preset first sealing distance (L21)(L22). For example, the first pressurized passage (3351) may be formed at one end of the vane slot (332) in the height direction with a first sealing distance (L21) of approximately 2 mm, and the second pressurized passage (2232) may be formed at the other end of the vane slot (332) in the height direction with a first sealing distance (L22) of approximately 2 mm. In other words, the first sealing distances (L21)(L22) provided at both ends of the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to be identical to each other. Accordingly, high-pressure oil and / or refrigerant flowing into the vane slot (332) through the pressurized passage (335) pressurizes the same position from both ends of the vane (35), thereby supporting the vane (35) more stably.

[0084] In addition, it may be preferable that the pressurized passage (335) according to the present embodiment be formed as close to the rear side of the vane (35) as possible, that is, as close to the outer end of the vane (35), but positioned within the reciprocating range of the vane (35). For example, the pressurized passage (335) may be formed to overlap the compression surface (35a) of the vane (35) at the bottom dead point (P1) of the vane (35), that is, when the vane (35) is maximally extended from the vane slot (332) toward the roller (34). Accordingly, the pressurized passage (335) can be prevented from being exposed to the outside during the reciprocating movement of the vane (35). This can suppress high-pressure oil and / or refrigerant flowing into the vane slot (332) through the pressurized passage (335) during the backward movement of the vane (35) from interfering with the reciprocating movement of the vane (35).

[0085] In this case, a spring fixing groove (35c) is formed at the rear end of the vane (35), into which the inner end of the vane spring (36) is radially inserted and fixed, and the pressure passage (335) can be formed at a position where the spring fixing groove (35c) and the vane slot (332) overlap in the height direction at the bottom dead point (P1) of the vane (35). However, even in this case, the pressure passage (335) can be formed at a position where it overlaps with the bottom dead point (P1) of the vane (35), that is, so as to be spaced apart from the spring fixing groove (35c) by a preset distance on both the upper and lower sides. Accordingly, while the spring fixing groove (35c) is formed at the rear end of the vane (35), the pressure passage (335) can be formed as close as possible to the bottom dead point (P1) of the vane (35).

[0086] In addition, the pressurized passage (335) according to the present embodiment may be formed of a plurality of pressurized holes spaced apart by a preset interval along the height direction of the vane slot (332) (or the axial direction of the rotation axis). For example, the pressurized passage (335) may be formed of a first pressurized passage (3351) and a second pressurized passage (3352), and the first pressurized passage (3351) and the second pressurized passage (3352) may be spaced apart by a preset interval along the height direction of the vane slot (332).

[0087] In this case, the first pressurized passage (3351) and the second pressurized passage (3352) may each be formed by one hole, or may each be formed by a plurality of identical holes. In the former case, the pressurized passages (3351)(3352) can be easily processed while securing the cross-sectional area of ​​the pressurized passages (3351)(3352), and in the latter case, the cross-sectional area of ​​the pressurized passages (3351)(3352) can be minimized to lower the surface pressure on the vane slot (332). This embodiment illustrates an example in which the first pressurized passage (3351) and the second pressurized passage (3352) are each formed by one hole.

[0088] For example, the first pressurized passage (3351) and the second pressurized passage (3352) can be formed on both upper and lower sides with respect to the spring receiving groove (332c) provided in the vane slot (332). In other words, spring receiving grooves (332c) are formed on the discharge side (332a1) and the suction side (332a2) forming the slot portion (332a) of the vane slot (332) so that the vane spring (36) is inserted, and the first pressurized passage (3351) and the second pressurized passage (3352) can be formed on both upper and lower sides with a preset interval centered on the spring receiving groove (332c) provided in the discharge side (332a1) of the vane slot (332). Accordingly, the first pressurized passage (3351) and the second pressurized passage (3352) are separated from each other with the spring receiving groove (332c) in between, and can respectively connect the internal space (more precisely, the oil storage space) (10a) of the casing (10) and the vane slot (332).

[0089] Specifically, the first pressurized passage (3351) may be formed on one side (e.g., the upper side) in the height direction of the vane slot (332) with respect to the spring receiving groove (332c), and the second pressurized passage (3352) may be formed on the other side (e.g., the lower side) in the height direction of the vane slot (332). Accordingly, the upper half of the vane (35) may be pressurized by the oil and / or refrigerant introduced through the first pressurized passage (3351), while the lower half of the vane (35) may be pressurized by the oil and / or refrigerant introduced through the first pressurized passage (3351). Through this, the vane (35) may be supported more stably while the upper and lower ends are pressurized inside the vane slot (332).

[0090] In this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed symmetrically along the height direction of the vane slot (332) based on the mid-height of the vane slot (332). For example, the first pressurized passage (3351) and the second pressurized passage (3352) may be spaced apart from each other by the same interval along the height direction of the vane slot (332) based on the mid-height of the vane slot (332), that is, the first center line (CL1) passing through the center of the spring receiving groove (332c) in the reciprocating direction of the vane (35), and the outlet (3351a) of the first pressurized passage (3351) and the outlet (3352a) of the second pressurized passage (3352) may be formed to have the same shape and / or cross-sectional area (A11)(A12). Accordingly, the first pressure (F21) transmitted to through the first pressure passage (3351) and the second pressure (F22) transmitted to through the second pressure passage (3352) are formed to have almost the same size, thereby supporting the vane (35) more stably.

[0091] Although not shown in the drawing, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed asymmetrically along the height direction of the vane slot (332) with respect to the middle height of the vane slot (332). For example, the second pressurized passage (3352) may be located further away from the first pressurized passage (3351) with respect to the center of the spring receiving groove (332c) (e.g., the first center line), or the sealing distance (L22) on the second pressurized passage (3352) may be formed shorter than the sealing distance (L21) on the first pressurized passage (3351), or the cross-sectional area (A12) of the second pressurized passage (3352) may be formed larger than the cross-sectional area (A11) of the first pressurized passage (3351). Accordingly, the second pressure (F22) of the second pressure passage (3352) is formed to be relatively greater than the first pressure (F21) of the first pressure passage (3351), so that the vane (35) that is sagging toward the second pressure passage (3352) due to its own weight can be stably supported.

[0092] In addition, the pressurized passage (335) may be formed so that the length (L11) in the height direction of each vane slot (332) is approximately less than or equal to 1 / 4 of the height (H1) of the cylinder (33). For example, the inner diameters (D1) (D2) of the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to be 1 / 4 or less of the height (H2) of the vane slot (332). Accordingly, it is possible to suppress the high-pressure oil and / or refrigerant filled in the internal space (10a) of the casing (10) from excessively flowing into the vane slot (332) toward the compression surface (35a) of the vane (35) through the pressurized passage (3351) (3352). Through this, it is possible to suppress the compression back surface (35b) of the vane (35) from being excessively pressed against the suction side surface (332a2) of the vane slot (332) by high-pressure oil and / or refrigerant flowing in through the pressurized passage (3351)(3352), thereby increasing friction loss.

[0093] In addition, the pressurized passage may be formed symmetrically on both sides along the reciprocating direction of the vane (35) with respect to the height direction of the vane slot (332) (or the axial direction of the rotation axis). For example, the first pressurized passage (3351) and the second pressurized passage (3352) may each be formed with one hole, and may be formed in a circular shape or a square shape. Accordingly, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed symmetrically on both sides along the reciprocating direction of the vane (35) with respect to the second center line (CL2) passing through the center of the first pressurized passage (3351) and the center of the second pressurized passage (3352) in the height direction of the vane slot (332). Through this, the optimal cross-sectional area of ​​the first pressurized passage (3351) and the second pressurized passage (3352) can be secured while easily processing these pressurized passages (335).

[0094] In addition, the pressurized passage (335) according to the present embodiment can be formed as short as possible. For example, the first pressurized passage (3351) and the second pressurized passage (3352) can be formed in parallel, and the third center line (CL3) passing through the center of the first pressurized passage (3351) and the center of the second pressurized passage (3352) can be formed in a direction orthogonal to the first center line (CL1) passing through the longitudinal direction of the vane slot (332) (or the reciprocating direction of the vane). Accordingly, the length of the first pressurized passage (3351) and / or the second pressurized passage (3352) can be minimized to allow the oil and / or refrigerant of the casing (10) to quickly flow into the vane slot (332).

[0095] In the case where a pressurized passage (335) is formed between the internal space (10a) of the casing (10) and the vane slot (332) as described above, more high-pressure (discharge pressure) oil and / or refrigerant filled in the internal space (10a) of the casing (10) can flow between the compression surface (35a) of the vane (35) and the discharge side (332a1) of the vane slot (332) facing it through the first pressurized passage (3351) (335) and the second pressurized passage (3352). Then, while forming a high back pressure on the compression surface (35a) of the vane (35), the rear side of the vane (35) can be pushed from the compression surface (e.g., discharge port) (35a) of the vane (35) to the compression back surface (e.g., suction port) (35b). Then, the gas force (F1) applied to the front side of the compression surface (35a) of the vane (35) by the pressure of the compression chamber can be offset by the pressure force (F21)(F22) applied to the rear side of the compression surface (35a) of the vane (35) through the pressure passage (335). Then, the inclination of the vane (35) is corrected, and the straightness of the vane (35) is restored, so that the friction loss between the vane slot (332) can be reduced.

[0096] In particular, in the case where the first pressurized passage (3351) and the second pressurized passage (3352) are respectively arranged on both sides in the height direction of the vane slot (332) as in the present embodiment, the high-pressure oil and / or refrigerant flowing through the first pressurized passage (3351) and the second pressurized passage (3352) support the upper and lower ends or the vicinity of the upper and lower ends of the vane (35), thereby supporting the vane (35) more stably than supporting the center of the vane (35).

[0097] Meanwhile, it may be advantageous for the first pressurized passage (3351) and the second pressurized passage (3352) to be spaced apart from the inner surface (33a) of the cylinder (33) by an appropriate distance to seal between the inner space (10a) of the casing (10) and the compression chamber (V).

[0098] Fig. 7 is a plan view showing a state in which a vane is positioned at top dead center in a compression section to which a pressurized passage according to the present embodiment is applied, and Fig. 8 is a cross-sectional view along the line “Ⅷ-Ⅷ” of Fig. 7.

[0099] Referring to FIGS. 7 and 8, the pressurized passage (335) according to the present embodiment may be formed apart from the inner surface (33a) of the cylinder (33) by a second sealing distance (L31) (L32) set respectively along the reciprocating direction of the vane (35). For example, the first pressurized passage (3351) may be formed apart from the inner surface (33a) of the cylinder (33) by a second sealing distance (L31) along the reciprocating direction of the vane (35), and the second pressurized passage (3352) may be formed apart from the inner surface (33a) of the cylinder (33) by a second sealing distance (L31) along the reciprocating direction of the vane (35). Accordingly, it is possible to effectively suppress oil and / or refrigerant flowing into the vane slot (332) through the pressurized passage (3351)(3352) from flowing into the compression chamber (V), or to effectively suppress refrigerant in the compression chamber (V) from flowing back toward the pressurized passage (3351)(3352) toward the vane slot (332) while moving to the top dead center (P2) and / or near the top dead center (P2) of the vane (35) as shown in FIG. 8.

[0100] In this case, the second sealing distances (L31) (L32) can be formed to be the same. For example, the second sealing distances from the inner surface (33a) of the cylinder (33) to the first pressurized passage (3351) and the second pressurized passage (3352) can be formed to be approximately 4.5 mm. In other words, the second sealing distances (L31) (L32) can be formed to be larger than the first sealing distances (L21) (L22), which are the distances from both ends of the vane slot (332) to each pressurized passage (3351) (3352). Accordingly, the refrigerant flow due to the pressure difference between the vane slot (or pressurized passage) (332) and the compression chamber (V) can be effectively suppressed.

[0101] In this way, since the pressurized passage is formed to support the compression surface of the vane near the bottom dead center of the vane, the straightness of the vane can be secured during the reciprocating motion of the vane. In addition, since the pressurized passage is spaced apart from the inner surface of the cylinder by a preset sealing distance, it is possible to effectively suppress oil and / or refrigerant flowing through the pressurized passage from flowing into the compression chamber or refrigerant in the compression chamber from flowing back toward the pressurized passage at and / or near the top dead center of the vane.

[0102] In addition, since the pressurized passages are formed at the upper and lower ends or near the ends of the vane corresponding to the height-wise ends of the vane slot, the moment generated during the reciprocating motion of the vane can be effectively reduced, thereby stably supporting the vane.

[0103] In addition, the high-pressure oil and / or refrigerant contained in the internal space of the casing can be supplied between the vane slot and the vane while forming a discharge pressure and / or a pressure close to the discharge pressure and in a stable state where the pulsating pressure in the internal space of the casing is offset, thereby supporting the vane more stably. In other words, the oil and / or refrigerant contained in the internal space of the casing can be supplied between the vane slot and the vane while forming a discharge pressure and / or a pressure close to the discharge pressure, thereby stably supporting the vane. Accordingly, the pressure supporting the side surface of the vane becomes stable, thereby supporting the vane more stably.

[0104] Meanwhile, there are other embodiments of the pressurized passage as follows.

[0105] That is, in the embodiment described above, the pressurized passage is formed symmetrically on the inside and outside with respect to the second center line, but in some cases, the pressurized passage may be formed asymmetrically on the inside and outside with respect to the second center line.

[0106] Fig. 9 is a side view showing another example of a pressurized passage, and Fig. 8 is a side view showing another embodiment of a pressurized passage.

[0107] Referring back to FIGS. 4 and 7, the basic configuration and the resulting operational effects of the pressurized passage (335) according to the present embodiment are similar to those of the above-described embodiment. For example, the pressurized passage (335) includes a first pressurized passage (3351) and a second pressurized passage (3352), and the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to be spaced apart from each other along the height direction of the vane slot (332). In this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to be symmetrical to each other by the same interval with respect to the first center line (CL1) passing through the center of the spring receiving groove (332c) in the reciprocating direction of the vane (35). In addition, in this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed at the upper and lower ends of the vane slot (332) with a sealing distance (L21)(L22), respectively, and may be formed as close as possible to the upper and lower ends of the vane slot (332). In addition, in this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to overlap with the bottom dead point (P1) of the vane (35). Accordingly, when the vane (35) reciprocates, the straightness of the vane (35) is secured, and at the same time, the moment generated during the reciprocating motion of the vane (35) is effectively reduced, so that the vane (35) can be supported more stably.

[0108] However, in the present embodiment, as shown in FIGS. 9 and 10, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed asymmetrically with respect to the second center line (CL2) passing through the center of the spring receiving groove (332c) in the height direction of the vane slot (332). For example, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed such that the cross-sectional areas (A11)(A21) of the side located on one side of the reciprocating direction of the vane (35) with respect to the second center line (CL2) are different from the cross-sectional areas (A12)(A22) of the side located on the other side of the reciprocating direction of the vane (35).

[0109] Specifically, the first pressurized passage (3351) and the second pressurized passage (3352) are each formed by one hole, and the outer circumferential cross-sectional area (A11) (A21) adjacent to the outer circumferential surface (33b) of the cylinder (33) with respect to the second center line (CL2) may be formed to be larger than the inner circumferential cross-sectional area (A12) (A22) adjacent to the inner circumferential surface (33a) of the cylinder (33). In other words, the cross-sectional areas (A1) (A2) of the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to become wider as they go toward the bottom dead point (P1) of the vane (35). Accordingly, the support area of ​​the vane slot (332) supporting both sides (35a) (35b) of the vane (35) is secured widely, while the center of pressure (Op) of the pressure passage (335) is made as close as possible to the bottom dead point (P1) of the vane (35), thereby supporting the vane (35) more stably.

[0110] In this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed in a non-circular shape or may have different numbers of passages. For example, as shown in FIG. 9, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed in a semicircular shape (or a triangular shape), but may have a larger outer circumferential cross-sectional area (A11) (A21) than an inner circumferential cross-sectional area (A12) (A22). In addition, as shown in FIG. 10, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed as a plurality of holes having the same inner diameter, but may have a larger number of pressurized passages (335a) located on the outer circumferential side than the number of pressurized passages (335b) located on the inner circumferential side based on the second center line (CL2). Accordingly, as described above, while securing the support area of ​​the vane slot (332), the center of pressure (Op) of the pressure passage (335) is brought closer to the bottom dead point (P1) of the vane (35), thereby supporting the vane (35) more stably.

[0111] Meanwhile, another embodiment of the pressurized passage is as follows.

[0112] That is, in the above-described embodiment, the pressurized passage is applied to a rotary compressor of a conventional rotating roller type, but in some cases, it can be equally applied to a rotary compressor of a hinged vane type in which a vane is hingedly connected to a roller or a vane and a roller are connected.

[0113] Fig. 11 is a plan view showing an example of a pressurized passage applied to another embodiment of a rotary compressor.

[0114] Referring back to FIG. 4, the basic configuration and the resulting operational effects of the pressurized passage (335) according to the present embodiment are similar to those of the above-described embodiment. For example, the pressurized passage (335) includes a first pressurized passage (3351) and a second pressurized passage (3352), and the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to be spaced apart from each other along the height direction of the vane slot (332). In this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to be symmetrical to each other by the same interval with respect to the first center line (CL1) passing through the center of the spring receiving groove (332c) in the reciprocating direction of the vane (35). In addition, in this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed at the upper and lower ends of the vane slot (332) with a sealing distance (L21)(L22), respectively, and may be formed as close as possible to the upper and lower ends of the vane slot (332). In addition, in this case, the first pressurized passage (3351) and the second pressurized passage (3352) may be formed to overlap with the bottom dead point (P1) of the vane (35). Accordingly, when the vane (35) reciprocates, the straightness of the vane (35) is secured, and at the same time, the moment generated during the reciprocating motion of the vane (35) is effectively reduced, so that the vane (35) can be supported more stably.

[0115] However, in the present embodiment, the front end of the vane (35) may be hinge-connected to the outer surface of the roller (34) so ​​as to be rotatable, as shown in FIG. 9. In this case, the vane (35) may also come into close contact with the suction side (332a2) of the vane slot (332) forming the partition wall (333) under the pressure load of the discharge chamber. As a result, the compression back surface (35b) of the vane (35) and the suction side surface (332a2) of the vane slot (332) facing it may come into excessive close contact, thereby increasing friction loss, which may lower the compressor efficiency or cause noise to be generated due to abnormal behavior of the vane (35). This may occur more significantly in the hinge vane method in which the vane (35) is connected to or integrally formed with the roller (34), as in the present embodiment.

[0116] Accordingly, in the case where a pressurized passage (335) is formed to connect the vane slot (332) to the internal space (10a) of the casing (10) as in the present embodiment, high-pressure oil and / or refrigerant contained in the internal space (10a) of the casing (10) can be directly supplied between the compression surface (35a) of the vane (35) and the discharge side (332a1) of the vane slot (332) facing it through the pressurized passage (335). Then, the inclination of the vane (35) is corrected, and the straightness of the vane (35) is maintained and / or restored, so that friction loss and / or abnormal noise between the vane slot (332) can be effectively reduced.

[0117] Even in this case, when the first pressurized passage (3351) and the second pressurized passage (3352) forming the pressurized passage (335) are respectively arranged on both sides in the height direction of the vane slot (332), the high-pressure oil and / or refrigerant flowing in through the first pressurized passage (3351) and the second pressurized passage (3352) support the upper and lower ends or the vicinity of the upper and lower ends of the vane, thereby supporting the vane more stably than supporting the center of the vane (35).

[0118] Meanwhile, in the above-described embodiments, the pressure passage was applied to a single-stage rotary compressor, but the same can be applied to a double-stage rotary compressor.

Claims

1. Casing; A cylinder having an intake passage and an exhaust passage, and a vane slot provided between the intake passage and the exhaust passage; A bearing plate provided on each of the axial sides of the cylinder to support the rotating shaft and form a compression chamber together with the cylinder; A roller provided inside the cylinder and rotating together with the rotation axis; and It includes a vane that is inserted into the vane slot of the cylinder and performs reciprocating motion, The above cylinder is formed with a plurality of pressurized passages that connect the vane slots to the internal space of the casing, The above multiple pressurized passages are: A rotary compressor that penetrates the discharge side of the vane slot from the outer surface of the cylinder and is formed to be spaced apart from each other along the height direction of the vane slot.

2. In paragraph 1, The above multiple pressurized passages are: A rotary compressor spaced apart from the middle height of the above vane slot by a preset interval on both sides along the height direction of the vane slot.

3. In paragraph 1, The above multiple pressurized passages are: A rotary compressor formed symmetrically with respect to the mid-height of the above vane slots.

4. In paragraph 3, Each of the above multiple pressurized passages is: A rotary compressor formed by one hole at a time.

5. In paragraph 3, Each of the above multiple pressurized passages is: A rotary compressor formed by multiple holes.

6. In paragraph 1, Each of the above multiple pressurized passages is: A rotary compressor formed so that the length of the vane slot in the height direction is less than 1 / 4 of the total height of the vane slot.

7. In paragraph 1, The above multiple pressurized passages are: A rotary compressor in which the length between the two ends of the vane slot in the height direction is formed to be greater than the length between the two ends of the vane in the reciprocating direction.

8. In paragraph 1, Each of the above multiple pressurized passages is: A rotary compressor formed by spacing out a preset first sealing distance from both ends of the vane slot along the height direction of the vane slot.

9. In paragraph 8, The above first sealing distance is, A rotary compressor formed with equal spacing between each end of the above vane slot.

10. In paragraph 1, Each of the above multiple pressurized passages is: A rotary compressor in which the inner surface of the cylinder is spaced apart from the reciprocating direction of the vane by a preset second sealing distance.

11. In paragraph 10, Each of the above multiple pressurized passages is: It is spaced apart from both ends of the vane slot by a preset first ceiling distance along the height direction of the vane slot, The above second ceiling distance is, A rotary compressor formed to be larger than the first sealing distance.

12. In paragraph 1, Each of the above multiple pressurized passages is: A rotary compressor formed so as to overlap the side surface of the vane at the lower dead point of the vane.

13. In paragraph 1, Each of the above multiple pressurized passages is: A rotary compressor in which both sides are formed symmetrically along the reciprocating direction of the vane based on the height direction of the vane slot.

14. In paragraph 1, Each of the above multiple pressurized passages is: A rotary compressor in which the outer circumferential cross-sectional area adjacent to the outer circumferential surface of the cylinder is formed larger than the inner circumferential cross-sectional area adjacent to the inner circumferential surface of the cylinder based on the height direction of the vane slot.

15. In paragraph 1, Each of the above multiple pressurized passages is: A rotary compressor formed in a direction orthogonal to the reciprocating direction of the above vane.

16. In any one of paragraphs 1 to 15, The above vane is supported by an elastic member while slidingly contacting the outer surface of the roller, and a spring receiving groove is formed by being sunken to a preset depth on both sides of the vane slot facing both sides of the vane so that the elastic member can be inserted. The above multiple pressurized passages are: A rotary compressor formed on both sides with a predetermined interval in the height direction of the vane slot centered on the spring receiving groove.

17. In paragraph 16, The above multiple pressurized passages are: A rotary compressor formed at equal intervals from the center of the above spring receiving groove.

18. In any one of paragraphs 1 to 15, The above vane is rotatably coupled to the outer surface of the roller, and both sides of the vane slot facing both sides of the vane are formed flat, The above multiple pressurized passages are: A rotary compressor formed by spacing out equal intervals at the mid-height of the above vane slots.

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