Rotary compressor

Abstract

The rotary compressor of the present application includes a housing, a cylinder, a main bearing and a sub-bearing, a rotating shaft, a vane slot, and a roller provided with a back pressure chamber, and at least one vane. A spring insertion slot is formed on the roller at an inner side end portion in the slot direction of the vane slot, and a vane spring that supports the rear surface of the vane toward the inner peripheral surface side of the cylinder can be provided in the spring insertion slot. Thus, an elastic force is supplied to the rear surface of the vane, thereby suppressing the shaking phenomenon of the vane when the vane passes through the close approach portion during operation, reducing the initial start-up failure of the compressor, and suppressing the backflow of the refrigerant of the discharge stroke to the suction stroke, thereby improving the compressor efficiency. Furthermore, when applied to the compressor provided in an air conditioner, the refrigeration and heating effects are rapidly exhibited, thereby improving the efficiency of the air conditioner while improving the reliability.

Description

Technical Field

[0001] This invention relates to a vane rotary compressor in which the vanes slide into rotating rollers. Background Technology

[0002] Rotary compressors can be divided into two types: those in which the vanes slide into the cylinder to contact the rollers, and those in which the vanes slide into the rollers to contact the cylinder. Generally, the former is called a roller eccentric rotary compressor (hereinafter, rotary compressor), and the latter is called a vane concentric rotary compressor (hereinafter, vane rotary compressor).

[0003] In a rotary compressor, the blades inserted into the cylinder are drawn out towards the rollers under the action of elastic force or back pressure, thereby contacting the outer circumferential surface of the rollers. On the other hand, in a vane rotary compressor, the blades inserted into the rollers rotate together with the rollers and are drawn out towards the cylinders under the action of centrifugal force and back pressure, thereby contacting the inner circumferential surface of the cylinders.

[0004] With each rotation of the rollers, a rotary compressor independently forms compression chambers corresponding to the number of blades, and each chamber simultaneously performs the intake, compression, and discharge strokes. Conversely, with each rotation of the rollers, a vane-driven rotary compressor continuously forms compression chambers corresponding to the number of blades, and each chamber sequentially performs the intake, compression, and discharge strokes. Therefore, vane-driven rotary compressors achieve a higher compression ratio compared to rotary compressors. Consequently, vane-driven rotary compressors are more suitable for using high-pressure refrigerants with low ozone depletion potential (ODP) and global warming potential (GWP), such as R32, R410a, and CO2.

[0005] Such a rotary vane compressor is disclosed in Patent Document 1 (Japanese Patent Publication: JP2013-213438A). The rotary vane compressor disclosed in Patent Document 1 discloses the characteristics of a rotary vane compressor, namely, a low-pressure method for drawing in refrigerant by filling the internal space of the motor chamber, or a structure in which multiple vanes are slidably inserted into rotating rollers.

[0006] In Patent Document 1, back pressure chambers are formed at the rear ends of the blades, and these back pressure chambers are configured to communicate with a back pressure bag. The back pressure bag is divided into a first bag that forms an intermediate pressure and a second bag that forms an outlet pressure or an intermediate pressure close to the outlet pressure. Based on the direction from the intake side to the outlet side, the first bag is connected to the back pressure chamber located on the upstream side, and the second bag is connected to the back pressure chamber located on the downstream side.

[0007] However, in existing rotary vane compressors as described above, a vibration phenomenon may occur during operation, where the vanes are separated from the cylinder by the pressure difference between the front and rear sides, and then come into contact with the cylinder. In particular, this phenomenon occurs severely during the initial startup of the compressor, resulting in poor initial startup, which not only reduces compressor efficiency but may also delay cooling and heating effects when applied to air conditioning.

[0008] Furthermore, in existing rotary vane compressors, vane vibration occurs primarily around the contact point, potentially causing wear on the inner circumferential surface of the cylinder or the leading edge of the vanes. This not only increases vibration noise in specific areas but also, due to the connection between the discharge and intake compression chambers, leakage between them is possible. This leakage leads to an increase in the specific volume of the intake refrigerant, and as the amount of refrigerant drawn in decreases, intake losses may occur, reducing compressor efficiency.

[0009] In addition, in existing rotary vane compressors, the pressure of the oil supplied to the rear of the vanes is uneven, resulting in pressure pulsation. Consequently, the back pressure formed on the rear of the vanes is not constant, which may exacerbate the vane vibration phenomenon.

[0010] Furthermore, when using high-pressure refrigerants such as R32, R410a, and CO2, the aforementioned problems may become more severe. That is, if a high-pressure refrigerant is used, even if the number of blades is increased to reduce the volume of each compression chamber, the same level of cooling power can be achieved as with a relatively low-pressure refrigerant such as R134a. However, if the number of blades increases, the friction area between the blades and the cylinder will also increase accordingly. Therefore, if the bearing surface on the rotating shaft is reduced, the movement of the rotating shaft will become more unstable, further increasing mechanical friction losses. This may be more pronounced under low-temperature heating conditions, high pressure ratio conditions (Pd / Ps≥6), and high-speed operating conditions (above 80Hz). Summary of the Invention

[0011] The purpose of this invention is to provide a rotary compressor that suppresses the initial start-up delay of the compressor, thereby improving the compressor efficiency.

[0012] Furthermore, the object of the present invention is to provide a rotary compressor that suppresses refrigerant leakage near the contact point during compressor operation, thereby enabling rapid initial startup.

[0013] Furthermore, the present invention aims to provide a rotary compressor that suppresses refrigerant leakage near the contact point during compressor operation, while reducing frictional losses in areas other than the contact point, thereby further improving compressor efficiency.

[0014] Another object of the present invention is to provide a rotary compressor that can reduce vibration noise caused by the shaking of the blades during compressor operation.

[0015] Furthermore, another object of the present invention is to provide a rotary compressor that increases the force applied to the cylinder side by the blades near the contact point during compressor operation, thereby suppressing blade vibration.

[0016] Furthermore, another object of the present invention is to provide a rotary compressor that, when the compressor is in operation, uniformly applies pressure to the blades passing near the contact point, thereby suppressing unilateral wear of the blades.

[0017] Another object of the present invention is to provide a rotary compressor that can stably control the movement of blades inserted into rollers.

[0018] Furthermore, another object of the present invention is to provide a rotary compressor that reduces the effects caused by pressure pulsation behind the blades, thereby stabilizing the movement of the blades.

[0019] Furthermore, another object of the present invention is to provide a rotary compressor that can stabilize the movement of the blades, simplify the structure of supporting the blades toward the cylinder side, and obtain high blade support force.

[0020] Another objective of this invention is to provide a rotary compressor that can suppress blade vibration even when using high-pressure refrigerants such as R32, R410a, and CO2.

[0021] To achieve the objectives of this invention, a rotary compressor includes a housing, a cylinder, a main bearing and a secondary bearing, a rotating shaft, rollers, and at least one blade. The housing has a sealed internal space. The cylinder is fixed within the internal space of the housing to form a compression space. The main bearing and the secondary bearing are respectively disposed on opposite axial sides of the cylinder. The rotating shaft passes through the cylinder to support the main bearing and the secondary bearing. The roller is disposed on the rotating shaft, with its outer circumferential surface eccentrically positioned relative to the inner circumferential surface of the cylinder. The roller has at least one blade groove opening towards the outer circumferential surface. The blade is slidably inserted into the blade groove, with its leading edge contacting the inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers. The roller may include a roller body and a blade spring. The roller body may have a spring insertion groove formed at its inner end in the groove direction of the blade groove. The blade spring may be inserted into the spring insertion groove to support the trailing edge of the blade against the inner circumferential surface of the cylinder. Thus, an elastic force is supplied to the trailing edge of the blade, thereby enabling the leading edge of the blade near the contact point to press against the inner circumferential surface of the cylinder. In this way, blade vibration occurring near the compressor's contact area is suppressed during compressor operation, thus preventing refrigerant leakage between the compression chambers. This also suppresses poor initial compressor start-up, allowing the compressor to start quickly, while preventing refrigerant backflow from the discharge chamber into the suction chamber, thereby significantly reducing suction losses and improving compressor efficiency. Furthermore, when applied to air conditioner compressors, this technology allows for rapid heating and cooling, improving both the reliability and efficiency of the air conditioner.

[0022] As an example, the leaf spring can be implemented as a compression helical spring. Therefore, by placing the leaf spring as a compression helical spring on the rear side of the leaf, the leaf spring can be easily configured, and a relatively high elastic force can be obtained.

[0023] For example, the leaf spring may contact the leaf in a second interval and be separated from the leaf in a first interval outside the second interval, the second interval including the contact point where the outer circumferential surface of the roller approaches the inner circumferential surface of the cylinder. Thus, the leaf spring is stably held in the spring insertion slot, and only contacts the leaf spring when the leaf passes through a proximal portion including an ejection stroke (which may include a portion of an intake stroke or a portion of a compression stroke), thereby suppressing frictional losses during the intake and compression strokes other than the proximal portion.

[0024] Specifically, the spring insertion slot includes a first spring fixing surface and a second spring fixing surface spaced apart from each other at a predetermined interval along the groove direction of the blade groove. Within the first interval, both ends of the blade spring can be supported by the first spring fixing surface and the second spring fixing surface, respectively. This reduces frictional losses generated during the blade's intake and compression strokes.

[0025] As another example, the sealing distance between the spring insertion groove and the outer peripheral surface of the roller body can be formed to be greater than or equal to half the lateral width of the blade groove. Thus, a spring insertion groove is formed on the rear side of the blade, thereby suppressing leakage between the compression chambers caused by the spring insertion groove while the blade spring is installed.

[0026] As another example, at least a portion of the spring insertion slot can be formed to overlap the blade slot axially. The blade can have a spring support portion formed at the position where it overlaps with the spring insertion slot. Thus, while stably supporting the blade spring on the rear side of the supporting blade, the blade and the blade spring are separated in the area away from the proximal portion, thereby suppressing frictional losses that may occur when the blade spring is used due to excessive contact between the blades.

[0027] For example, the spring support portion can be formed in a stepped shape at a predetermined depth from one axial side connected to the rear side of the blade to the other axial side. This allows for easy formation of a spring insertion groove for mounting the blade spring, while smoothly guiding outward-pressurized or intermediate-pressurized oil towards the rear side of the blade, thereby providing more stable support for the blade.

[0028] Furthermore, the main bearing or the auxiliary bearing may have an outlet for discharging refrigerant from the compression chamber into the interior space of the housing. The spring support may be formed on the axial side facing the bearing with the outlet. Thus, by arranging the blade spring in the relatively high-pressure section of the compression chamber, blade retraction is effectively suppressed, thereby maintaining the surface pressure between the blade and the cylinder along the axial direction. Simultaneously, unilateral blade wear is suppressed, thereby improving compression efficiency.

[0029] Furthermore, the spring support portion can be recessed to a predetermined depth from the axial center of the rear side of the blade toward the front side of the blade. This stably supports one end of the blade spring, thereby improving compressor efficiency and reliability.

[0030] Additionally, the spring support may include a first support surface and a second support surface. The first support surface may extend towards the front of the blade, and the second support surface may extend from the first support surface to the axial side of the blade to support the end of the blade spring along the groove direction. The groove length of the first support surface may be less than half the groove length of the blade. Thus, the blade is only elastically supported by the blade spring when it passes the proximal portion, while ensuring a sealing distance when the blade passes the distal portion, thereby suppressing leakage between the compression chambers through the spring support. Simultaneously, it reduces vibration noise caused by blade wobble during compressor operation.

[0031] Furthermore, the axial depth of the second support surface can be greater than or equal to the axial depth of the spring insertion groove. This suppresses friction between the blade and the blade spring, thereby stabilizing the blade's movement.

[0032] In another embodiment, the roller body can be formed as a single piece. The spring insertion groove can be formed by recessing from one axial side of the roller body to the other axial side at a predetermined depth. This allows for easy formation of a roller with a spring insertion groove, thereby reducing manufacturing costs.

[0033] Furthermore, the lateral width of the spring insertion slot can be made larger than the lateral width of the blade slot. The outer diameter of the blade spring can be made larger than the lateral width of the blade slot. Therefore, the two ends of the blade spring inserted into the spring insertion slot can be stably fixed within the spring insertion slot.

[0034] Furthermore, the axial depth of the spring insertion slot can be greater than the outer diameter of the leaf spring, and less than or equal to half the axial height of the roller body. Thus, the axial opening of the spring insertion slot is covered by the main bearing (or secondary bearing), thereby enabling stable support of the leaf spring within the spring insertion slot.

[0035] Furthermore, the axial depth of the spring insertion groove can be greater than the outer diameter of the blade spring, and greater than half the axial height of the roller body. The blade spring can be positioned at the axial midpoint of the roller body. Thus, since the blade spring supports the blade in the middle, the surface pressure between the blade and the cylinder can be maintained uniformly along the axial direction. Simultaneously, unilateral wear of the blade is suppressed, thereby further improving compression efficiency.

[0036] Furthermore, a cover member covering at least a portion of the spring insertion slot can be provided on the axial side of the spring insertion slot. This suppresses the disengagement of the leaf spring, thereby improving reliability.

[0037] Furthermore, the inner circumferential surface of the spring insertion slot and the outer circumferential surface of the cover member can be separated by at least a portion to form an oil passage. This allows oil to flow smoothly towards the rear of the blade, thereby providing further stable support to the blade towards the cylinder side.

[0038] As another example, the roller body may include a first roller body and a second roller body. The first roller body may form one axial side. The second roller body may form the other axial side and may be coupled to one axial side of the first roller body. The spring insertion slot may be disposed between the first roller body and the second roller body. This allows for easy and stable installation of the blade spring. Simultaneously, during compressor operation, pressure is uniformly applied to the blades passing near the contact point, thereby suppressing unilateral wear of the blades.

[0039] Additionally, the spring insertion slot may include a first spring insertion slot and a second spring insertion slot. The first spring insertion slot may be disposed in the first roller body, and the second spring insertion slot may be disposed in the second roller body. The first spring insertion slot and the second spring insertion slot may be formed symmetrically with respect to the faces of the first roller body and the second roller body facing each other. This facilitates the manufacture of separate roller bodies, thereby reducing manufacturing costs.

[0040] Specifically, the first roller body may have a first blade groove and a first spring insertion groove, and the second roller body may have a second blade groove and a second spring insertion groove. The first blade groove and the second blade groove may be formed on the same axis, as may the first spring insertion groove and the second spring insertion groove. The first spring insertion groove may be formed such that at least a portion overlaps with the first blade groove axially, and is recessed to a predetermined depth from one axial side of the first roller body toward the other axial side. The second spring insertion groove may be formed such that at least a portion overlaps with the second blade groove axially, and is recessed to a predetermined depth from one axial side of the second roller body facing the first roller body toward the other axial side.

[0041] More specifically, the axial height of the first roller body and the axial height of the second roller body can be made the same, and the depth of the first spring insertion groove and the depth of the second spring insertion groove can be made the same. Thus, while easily manufacturing separate roller bodies, the leaf spring can be stably supported.

[0042] As another example, the roller may have a central bore into which the rotating shaft can be inserted for engagement. This allows for the easy fabrication of a roller into which a leaf spring is inserted. Furthermore, the roller can be made of a different material than the rotating shaft, facilitating the machining of the roller into which the leaf spring is inserted while simultaneously reducing the weight of the rotating body including the roller.

[0043] Furthermore, an anti-rotation groove can be formed on the inner circumferential surface of the shaft hole, and an anti-rotation key can be formed on the outer circumferential surface of the rotating shaft, which is inserted into the anti-rotation groove to be constrained in the circumferential direction. This suppresses the free-spinning phenomenon of the roller or rotating shaft, thereby enabling a stable connection between the roller and the rotating shaft.

[0044] As another example, the roller can extend from the outer circumferential surface of the rotating shaft as a single unit. Thus, the rotational force of the rotating shaft can be stably transmitted to the roller while eliminating the need for assembly work on the rotating shaft, including the roller.

[0045] As another example, the blade groove can be formed to be inclined at a predetermined angle relative to the radial direction of the roller. This allows the blade spring to be stably positioned on one side of the blade groove while ensuring the length of the blade groove.

[0046] As another example, the blade groove can be formed along the radial direction of the roller. This allows for easy formation of the blade groove while simultaneously enabling stable support of the blade using a blade spring.

[0047] As another example, at least one of the sliding surfaces of the main bearing facing one axial side of the roller and the sliding surfaces of the secondary bearing facing the other axial side of the roller can be circumferentially spaced to form a plurality of back pressure bags with different pressures. The plurality of back pressure bags can be formed to overlap axially with the spring insertion slots. Thus, while the blade spring is positioned on the rear side of the blade, oil from the back pressure bags is smoothly supplied to the rear side of the blade through the spring insertion slots, thereby effectively suppressing blade vibration even around the contact point.

[0048] As another example, in the sliding surface of the main bearing facing one axial side of the roller and the sliding surface of the secondary bearing facing the roller on the other axial side, the sliding surfaces of the main bearing and the secondary bearing, which overlap axially with the spring insertion groove, can be formed flat. Therefore, since the back pressure bag is excluded from the main and secondary bearings, not only are the main and secondary bearings easier to machine, but the bearing surfaces supporting the rotating shaft are also formed into a circle, thereby enabling more stable radial support of the rotating shaft.

[0049] For example, the leaf spring can be configured as a compression helical spring, with one end supported by the spring insertion slot and the other end supported by the rear of the blade. Thus, because the leaf spring continuously and elastically supports the blade, the back pressure bag can be removed from the main bearing and the secondary bearing.

[0050] In the rotary compressor of the present invention, the inner circumferential surface of the cylinder can be formed into an elliptical shape.

[0051] In the rotary compressor of the present invention, the inner circumferential surface of the cylinder can be formed into a circular shape. Attached Figure Description

[0052] Figure 1 This is a cross-sectional view showing an embodiment of the rotary blade compressor of the present invention.

[0053] Figure 2 It is decomposition Figure 1 The compression section is shown in a three-dimensional view.

[0054] Figure 3 It is assembly Figure 2 The compression section is shown in the top view.

[0055] Figure 4 It is decomposition Figure 2 The rotating shaft and rollers are shown in a three-dimensional diagram.

[0056] Figure 5 It is assembly Figure 4 The rotating shaft and rollers are shown in a three-dimensional diagram.

[0057] Figure 6 It is to expand Figure 5 A portion of the compression section is shown in a three-dimensional view.

[0058] Figure 7 yes Figure 6 Sectional view along line "Ⅳ-Ⅳ" in the diagram.

[0059] Figure 8 It shows the basis Figure 5 A schematic diagram showing the relationship between the position of the blades and the blade spring.

[0060] Figure 9a and Figure 9b It is to expand Figure 8 A schematic diagram showing the support status of the blades at various positions. Figure 9a This is a diagram showing the distal region. Figure 9b This is a diagram showing the proximal region.

[0061] Figure 10 This is shown for illustration. Figure 8A cross-sectional view of the support state of the blades near the contact point.

[0062] Figure 11 It is shown Figure 4 A cross-sectional view of another embodiment of the blade support structure.

[0063] Figure 12 It is shown Figure 4 A cross-sectional view of another embodiment of the blade support structure.

[0064] Figure 13 It is shown Figure 4 An exploded perspective view of another embodiment of the blade support structure.

[0065] Figure 14 It is magnification Figure 13 The blade support structure is shown in a cross-sectional view.

[0066] Figure 15 It is decomposition Figure 1 Another embodiment of the roller is shown in a perspective view.

[0067] Figure 16 It is assembly Figure 15 The rollers in the diagram are shown in a three-dimensional view.

[0068] Figure 17 yes Figure 16 The sectional view along line "V-V".

[0069] Figure 18 It is decomposition Figure 1 Another embodiment of the compression section is shown in a perspective view.

[0070] Figure 19 It is shown Figure 18 A cross-sectional view of another embodiment of the blade support structure.

[0071] Figure 20 It shows the basis Figure 18 A schematic diagram showing the relationship between the position of the blades and the blade spring.

[0072] Figure 21a and Figure 21b It is magnification Figure 20 A schematic diagram showing the support status of the blades at various positions. Figure 21a This is a diagram showing the distal region. Figure 21b This is a diagram showing the proximal region. Detailed Implementation

[0073] The blade rotary compressor according to the present invention will now be described in detail with reference to an embodiment shown in the accompanying drawings.

[0074] This invention provides a vane spring on the roller, which can also be applied to vane rotary compressors in which the vanes are slidably inserted into the roller. For example, it is applicable not only to vane rotary compressors with an elliptical cylinder (hereinafter referred to as an asymmetrical elliptical) whose inner circumferential surface is configured with a plurality of curvatures, but also to vane rotary compressors with a circular cylinder whose inner circumferential surface is configured with a single curvature. Furthermore, it is applicable not only to vane rotary compressors in which the vane grooves for slidably inserted vanes are formed at a predetermined angle relative to the radial direction of the roller, but also to vane rotary compressors in which the vane grooves are formed along the radial direction of the roller. Hereinafter, an example in which the inner circumferential surface of the cylinder is an asymmetrical elliptical shape and the vane grooves are inclined relative to the radial direction of the roller will be described as a representative example.

[0075] Figure 1 This is a cross-sectional view showing an embodiment of a rotary vane compressor according to the present invention. Figure 2 It is decomposition Figure 1 The compression section is shown in a three-dimensional view. Figure 3 It is assembly Figure 2 The compression section is shown in a top view.

[0076] Reference Figure 1 The rotary blade compressor of this embodiment includes a housing 110, a drive motor 120, and a compression unit 130. The drive motor 120 is disposed in the upper inner space 110a of the housing 110, and the compression unit 130 is disposed in the lower inner space 110a of the housing 110. The drive motor 120 and the compression unit 130 are connected by a rotating shaft 123.

[0077] The outer casing 110 forms the exterior of the compressor and can be classified as either longitudinal or transverse depending on the compressor's mounting configuration. A longitudinal configuration has the drive motor 120 and the compressor unit 130 arranged axially on the upper and lower sides, while a transverse configuration has the drive motor 120 and the compressor unit 130 arranged on the left and right sides. This embodiment will be described using a longitudinal configuration as an example.

[0078] The outer shell 110 includes: an intermediate shell 111 formed in a cylindrical shape; a lower shell 112 covering the lower end of the intermediate shell 111; and an upper shell 113 covering the upper end of the intermediate shell 111.

[0079] The drive motor 120 and the compressor unit 130 are inserted into and fixedly connected to the intermediate housing 111. The suction pipe 115 can pass through the intermediate housing 111 and be directly connected to the compressor unit 130. The lower housing 112 is sealed to the lower end of the intermediate housing 111. An oil storage space 110b can be formed on the lower side of the compressor unit 130, which stores the oil to be supplied to the compressor unit 130. The upper housing 113 is sealed to the upper end of the intermediate housing 111. An oil separation space 110c can be formed on the upper side of the drive motor 120 to separate oil from the refrigerant discharged from the compressor unit 130.

[0080] The drive motor 120 is a component of the electric motor unit, providing power to drive the compression unit 130. The drive motor 120 includes a stator 121, a rotor 122, and a rotating shaft 123.

[0081] The stator 121 is fixedly disposed inside the housing 110 and is fixed by pressing it into the inner circumferential surface of the housing 110 through heat fitting or the like. For example, the stator 121 can be fixed by pressing it into the inner circumferential surface of the intermediate housing 111.

[0082] The rotor 122 is rotatably inserted into the stator 121, and the rotating shaft 123 can be pressed into the center of the rotor 122 and engaged. Therefore, the rotating shaft 123 will rotate concentrically with the rotor 122.

[0083] An oil flow path 125 is formed in the shape of a hollow hole at the center of the rotating shaft 123. Oil through holes 126a and 126b are formed through the middle of the oil flow path 125, extending towards the outer peripheral surface of the rotating shaft 123. The oil through holes 126a and 126b are composed of a first oil through hole 126a belonging to the main bushing portion 1312 (described later) and a second oil through hole 126b belonging to the secondary bushing portion 1322. One or more of each of the first and second oil through holes 126a and 126b may be formed. This embodiment shows an example where multiple of each type are formed.

[0084] An oil suction device 127 may be provided at the middle or lower end of the oil flow path 125. The oil suction device 127 may be a gear pump, a viscous pump, a centrifugal pump, etc. This embodiment shows an example of using a centrifugal pump. Therefore, when the rotating shaft 123 rotates, the oil filling the oil storage space 110b of the housing 110 is pumped by the oil suction device 127. The oil can be drawn upward along the oil flow path 125, and then supplied to the secondary bearing surface 1322b of the secondary bushing part 1322 through the second oil through hole 126b, and supplied to the main bearing surface 1312b of the main bushing part 1312 through the first oil through hole 126a.

[0085] Additionally, a roller 134, described later, may be provided on the rotating shaft 123. The roller 134 may extend integrally from the rotating shaft 123, or the rotating shaft 123 and the roller 134 may be manufactured separately and then assembled. In this embodiment, the rotating shaft 123 is inserted into the roller 134 and then assembled. For example, a shaft hole 134a located at the center of the roller 134 extends axially, and the rotating shaft 123 can be inserted into and engaged with the shaft hole 134a.

[0086] In this configuration, an anti-rotation key 123b can be formed on the outer circumferential surface of the rotating shaft 123, and an anti-rotation groove 1341c can be formed on the inner circumferential surface of the roller 134, i.e., the inner circumferential surface of the shaft hole 134a. The anti-rotation key 123b can protrude radially, and the anti-rotation groove 1341c can be recessed radially to allow the anti-rotation key 123b to be inserted and engaged. Therefore, the rotating shaft 123 and the roller 134 can mutually constrain each other in the circumferential direction.

[0087] The anti-rotation key 123b and the anti-rotation groove 1341c can be formed as a single unit as shown in the figure, or multiple units can be formed at equal intervals along the circumference, depending on the situation. The relationship between the rotating shaft 123 and the roller 134 will be explained again later along with the roller 134.

[0088] The compression section 130 includes: a main bearing 131, a secondary bearing 132, a cylinder 133, rollers 134, and a plurality of blades 1351, 1352, and 1353. The main bearing 131 and the secondary bearing 132 are respectively disposed on the upper and lower sides of the cylinder 133, thereby forming a compression space V together with the cylinder 133. The rollers 134 are rotatably disposed in the compression space V, and the blades 1351, 1352, and 1353 are slidably inserted into the rollers 134, thereby dividing the compression space V into a plurality of compression chambers.

[0089] Reference Figures 1 to 3 The main bearing 131 can be fixedly disposed in the intermediate shell 111 of the outer casing 110. For example, the main bearing 131 can be inserted into and welded to the intermediate shell 111.

[0090] The main bearing 131 can be closely attached to and engaged with the upper end of the cylinder 133. Therefore, the main bearing 131 forms the upper side of the compression space V, supporting the upper surface of the roller 134 axially and the upper half of the rotating shaft 123 radially.

[0091] The main bearing 131 may include a main plate portion 1311 and a main bushing portion 1312. The main plate portion 1311 covers the upper side of the cylinder 133 and is engaged with the cylinder 133, and the main bushing portion 1312 extends axially from the center of the main plate portion 1311 toward the drive motor 120 and supports the upper half of the rotating shaft 123.

[0092] The main board portion 1311 is formed in a disc shape, and its outer peripheral surface can be tightly attached to and fixed to the inner peripheral surface of the intermediate shell 111. One or more discharge ports 1313a, 1313b, and 1313c can be formed in the main board portion 1311. A plurality of discharge valves 1361, 1362, and 1363 for opening and closing each discharge port 1313a, 1313b, and 1313c can be provided on the upper surface of the main board portion 1311. A discharge silencer 137 with a discharge space (not marked) can be provided on the upper side of the main board portion 1311 to accommodate the discharge ports 1313a, 1313b, and 1313c and the discharge valves 1361, 1362, and 1363. The discharge ports will be described later.

[0093] On the two axial sides of the main board portion 1311, the lower surface of the main board portion 1311, which faces the upper surface of the roller 134, namely the main sliding surface 1311a, can be formed with a first main back pressure bag 1315a and a second main back pressure bag 1315b.

[0094] The first main back pressure bag 1315a and the second main back pressure bag 1315b can be formed in an arc shape and are spaced apart from each other in the circumferential direction by a predetermined interval. The inner circumferential surfaces of the first main back pressure bag 1315a and the second main back pressure bag 1315b are formed in a circular shape, and the outer circumferential surfaces can be formed in an elliptical shape, taking into account the blade groove described later.

[0095] The first main back pressure bag 1315a and the second main back pressure bag 1315b can be formed within the outer diameter range of the roller 134. Therefore, the first main back pressure bag 1315a and the second main back pressure bag 1315b can be separated from the compression space V. However, as long as no additional sealing member is provided between the main sliding surface 1311a, which is the lower surface of the main plate portion 1311, and the upper surface of the roller 134 facing it, the first main back pressure bag 1315a and the second main back pressure bag 1315b can be slightly connected through the gap between the two sides.

[0096] The first main back pressure bag 1315a forms a lower pressure than the second main back pressure bag 1315b, for example, an intermediate pressure between the suction pressure and the discharge pressure. Oil (refrigerant oil) can flow into the first main back pressure bag 1315a through a narrow passage between the upper surface of the first main bearing protrusion 1316a and the roller 134 (described later). The first main back pressure bag 1315a can be formed within the compression chamber that constitutes the intermediate pressure in the compression space V. Therefore, the first main back pressure bag 1315a will maintain the intermediate pressure.

[0097] The second main back pressure bag 1315b generates a higher pressure than the first main back pressure bag 1315a, for example, an output pressure or an intermediate pressure between the intake and output pressures, close to the output pressure. Oil flowing into the main bearing bore 1312a of the main bearing 1312 through the first oil through-hole 126a can flow into the second main back pressure bag 1315b. The second main back pressure bag 1315b can be formed within the compression chamber that constitutes the output pressure in the compression space V. Therefore, the second main back pressure bag 1315b will maintain the output pressure.

[0098] Furthermore, on the inner circumferential sides of the first main back pressure bag 1315a and the second main back pressure bag 1315b, a first main bearing protrusion 1316a and a second main bearing protrusion 1316b are respectively formed extending from the main bearing surface 1312b of the main bushing portion 1312. Therefore, while sealing the first main back pressure bag 1315a and the second main back pressure bag 1315b relative to the outside, the rotating shaft 123 can be stably supported.

[0099] The first main bearing protrusion 1316a and the second main bearing protrusion 1316b can be formed to have the same height or to have different heights.

[0100] For example, when 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 on the end face of the second main bearing protrusion 1316b to connect the inner and outer peripheral surfaces of the second main bearing protrusion 1316b. Therefore, high-pressure oil (refrigerant oil) flowing into the inner side of the main bearing surface 1312b can flow into the second main back pressure bag 1315b through the oil communication groove (not shown) or the oil communication hole (not shown).

[0101] On the other hand, when the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are formed at different heights, the height of the second main bearing protrusion 1316b can be made lower than the height of the first main bearing protrusion 1316a. Therefore, high-pressure oil (refrigerant oil) flowing into the inside of the main bearing bore 1312a can flow over the second main bearing protrusion 1316b into the second main back pressure bag 1315b.

[0102] Furthermore, the main bushing portion 1312 can be formed as a hollow bushing shape, and a first oil groove 1312c can be formed on the inner circumferential surface of the main bearing hole 1312a constituting the inner circumferential surface of the main bushing portion 1312. The first oil groove 1312c is a straight line or an oblique line between the upper and lower ends of the main bushing portion 1312, and can communicate with the first oil passage hole 126a.

[0103] Reference Figures 1 to 3The secondary bearing 132 can be closely attached to and engaged with the lower end of the cylinder 133. Therefore, the secondary bearing 132 forms the lower side of the compression space V, supporting the lower surface of the roller 134 axially and the lower half of the rotating shaft 123 radially.

[0104] The secondary bearing 132 may include a secondary plate portion 1321 and a secondary bushing portion 1322. The secondary plate portion 1321 covers the lower side of the cylinder 133 and is engaged with the cylinder 133, and the secondary bushing portion 1322 extends axially from the center of the secondary plate portion 1321 toward the lower housing 112 and supports the lower half of the rotating shaft 123.

[0105] The sub-plate 1321 can be formed into a disk shape in the same way as the main plate 1311, and the outer peripheral surface of the sub-plate 1321 can be separated from the inner peripheral surface of the intermediate shell 111.

[0106] On the two axial sides of the subplate portion 1321, a first sub-back pressure bag 1325a and a second sub-back pressure bag 1325b can be formed on the upper surface of the subplate portion 1321 facing the lower surface of the roller 134, i.e., the sub-sliding surface 1321a.

[0107] The first secondary back pressure bag 1325a and the second secondary back pressure bag 1325b can be formed symmetrically with the first primary back pressure bag 1315a and the second primary back pressure bag 1315b described above, with the roller 134 as the center.

[0108] For example, the first auxiliary back pressure bag 1325a can be symmetrical to the first main back pressure bag 1315a, and the second auxiliary back pressure bag 1325b can be symmetrical to the second main back pressure bag 1315b. Therefore, a first auxiliary bearing protrusion 1326a can be formed on the inner circumferential side of the first auxiliary back pressure bag 1325a, and a second auxiliary bearing protrusion 1326b can be formed on the inner circumferential side of the second auxiliary back pressure bag 1325b.

[0109] The descriptions of the first secondary back pressure bag 1325a and the second secondary back pressure bag 1325b, the first secondary bearing protrusion 1326a and the second secondary bearing protrusion 1326b will be replaced by the descriptions of the first main back pressure bag 1315a and the second main back pressure bag 1315b, the first main bearing protrusion 1316a and the second main bearing protrusion 1316b.

[0110] However, depending on the circumstances, the first auxiliary back pressure bag 1325a and the second auxiliary back pressure bag 1325b can be formed asymmetrically with respect to the first main back pressure bag 1315a and the second main back pressure bag 1315b, respectively, with the roller 134 as the center. For example, the first auxiliary back pressure bag 1325a and the second auxiliary back pressure bag 1325b can be formed deeper than the first main back pressure bag 1315a and the second main back pressure bag 1315b.

[0111] Furthermore, the secondary bushing portion 1322 can be formed as a hollow bushing shape, and an oil groove (not shown) can be formed on the inner circumferential surface of the secondary bearing hole 1322a constituting the inner circumferential surface of the secondary bushing portion 1322. The oil groove (not shown) is a straight line or an oblique line between the upper and lower ends of the secondary bushing portion 1322, and can communicate with the second oil passage hole 126b of the rotating shaft 123.

[0112] Although not illustrated, back pressure bags 1315a and 1315b, 1325a and 1325b may also be formed on either side of the main bearing 131 and the secondary bearing 132.

[0113] Additionally, as mentioned above, the discharge port 1313 can be formed in the main bearing 131. However, the discharge port can also be formed in the auxiliary bearing 132, or it can be formed in both the main bearing 131 and the auxiliary bearing 132, or it can be formed between the inner and outer circumferential surfaces of the cylinder 133. This embodiment will be described with an example where the discharge port 1313 is formed in the main bearing 131.

[0114] There may be only one discharge port 1313. However, in this embodiment, a plurality of discharge ports 1313a, 1313b, and 1313c may be formed at predetermined intervals along the compression direction (or the rotation direction of the roller).

[0115] Typically, in a rotary vane compressor, as the roller 134 is eccentrically positioned relative to the compression space V, a near-contact contact point P is formed between the outer circumferential surface 1341 of the roller 134 and the inner circumferential surface 1332 of the cylinder 133. The discharge port 1313 is formed adjacent to the contact point P on the opposite side of the suction port 1331, centered on the contact point P. Therefore, the closer the compression space V is to the contact point P, the smaller the distance between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134, making it difficult to ensure the area of ​​the discharge port 1313.

[0116] Therefore, in this embodiment, the discharge port 1313 is divided into a plurality of discharge ports 1313a, 1313b, and 1313c with small inner diameters. The plurality of discharge ports 1313a, 1313b, and 1313c can be configured to be spaced apart from each other at a predetermined interval along the circumferential direction, i.e., the rotation direction of the roller 134.

[0117] Alternatively, the plurality of discharge ports 1313a, 1313b, and 1313c may each be formed as one, or as shown in this embodiment, two may be formed as a pair. For example, the discharge ports 1313 may be arranged in the order of first discharge port 1313a, second discharge port 1313b, and third discharge port 1313c, starting from the discharge port closest to the proximal portion 1332a.

[0118] The spacing between each of the discharge ports 1313a, 1313b, and 1313c can be approximately the same. For example, the first spacing 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 approximately the same as the second spacing between the rear end of the second discharge port 1313b and the front end of the third discharge port 1313c.

[0119] Furthermore, the arc length of the discharge port 1313, from the front end to the rear end, can be formed to be approximately 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 1313c can be formed to be approximately similar to the arc length of each compression chamber V1, V2, V3, from the interval between the preceding and following blades.

[0120] However, depending on the circumstances, the arc length from the front end of the first discharge port 1313a to the rear end of the third discharge port 1313c can be made larger than the arc length of the interval between the preceding and following blades, 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 overcompression and / or pressure pulsation.

[0121] Although not illustrated, when the blade grooves 1346a, 1346b, and 1346c described later are formed at non-equidistant intervals, the circumferential lengths of each compression chamber V1, V2, and V3 can be formed to be different, and a plurality of discharge outlets can be connected to one compression chamber, or a plurality of compression chambers can be connected to one discharge outlet.

[0122] Alternatively, in this embodiment, the discharge port 1313 may also extend to form a discharge groove 1314. The discharge groove 1314 may extend in an arc shape along the compression travel direction (the rotation direction of the rollers). Therefore, refrigerant that has not been discharged from the previous compression chamber is guided through the discharge groove 1314 to the discharge port 1313, which communicates with the next compression chamber, so that it can be discharged together with the refrigerant compressed in the next compression chamber. Thus, overcompression can be suppressed by minimizing the residual refrigerant in the compression space V, thereby improving compressor efficiency.

[0123] The discharge slot 1314 described above can be formed to extend from the final discharge port (e.g., the third discharge port) 1313. Typically, in a rotary vane compressor, the compression space V is divided into an intake chamber and a discharge chamber on both sides by a proximal portion (contact point) 1332a. Therefore, considering the seal between the intake and discharge chambers, the discharge port 1313 cannot overlap with the contact point P located at the proximal portion 1332a. Consequently, a residual space S is formed circumferentially between the contact point P and the discharge port 1313, separating the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134. In this residual space S, refrigerant cannot be discharged through the final discharge port 1313 and remains. The residual refrigerant increases the pressure in the final compression chamber, thereby potentially causing low compression efficiency due to overcompression.

[0124] However, as shown in this embodiment, when the discharge trough 1314 extends from the final discharge port 1313 to the residual space S, the refrigerant remaining in the residual space S is discharged in reverse through the discharge trough 1314 to the final discharge port 1313, thus effectively suppressing the low compression efficiency caused by overcompression in the final compression chamber.

[0125] Although not shown in the figure, a residual discharge hole (not shown) can be further formed in the residual space S outside the discharge slot 1314. The inner diameter of the residual discharge hole is smaller than that of the discharge outlet. Unlike the discharge outlet, the residual discharge hole is not opened or closed by the discharge valve and can be formed to be always open.

[0126] Furthermore, a plurality of discharge ports 1313a, 1313b, and 1313c can be opened and closed via the previously described discharge valves 1361, 1362, and 1363. Each discharge valve 1361, 1362, and 1363 can be constructed as a cantilevered reed valve, with one end forming a fixed end and the other a free end. Such discharge valves 1361, 1362, and 1363 are widely known in conventional rotary compressors, and therefore their description will be omitted.

[0127] Reference Figures 1 to 3 In this embodiment, the cylinder 133 can be tightly attached to the lower surface of the main bearing 131 and can be fastened to the main bearing 131 together with the auxiliary bearing 132 using screws. Therefore, the cylinder 133 can be fixedly connected to the housing 110 through the main bearing 131.

[0128] The cylinder 133 can be formed as an annular structure with a central empty space to constitute a compression space V. The empty space is sealed by the main bearing 131 and the secondary 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.

[0129] The cylinder 133 can be formed by penetrating from the outer circumferential surface to the inner circumferential surface. However, the intake port can also be formed by penetrating the main bearing 131 or the auxiliary bearing 132.

[0130] The intake port 1331 can be formed on one circumferential side with the contact point P as the center. The discharge port 1313 described above can be formed on the main bearing 131 on the other circumferential side opposite to the intake port 1331 with the contact point P as the center.

[0131] The inner circumferential surface 1332 of the cylinder 133 can be formed into an elliptical shape. In this embodiment, the inner circumferential surface 1332 of the cylinder 133 can be formed by combining a plurality of ellipses, for example, four ellipses with different aspect ratios in a manner with two dots, thereby forming an asymmetrical elliptical shape.

[0132] For example, the inner circumferential surface 1332 of the cylinder 133 in this embodiment can be formed to have the center of the roller 134 described later or the rotation center (shaft center or outer diameter center of the cylinder) Or, or a first dot O biased from the center toward the first position on the contact point P side, and a second dot O' biased toward the second position on the contact point P side relative to the first dot O.

[0133] The XY plane centered on the first point O will form the third quadrant Q3 and the fourth quadrant Q4, and the XY plane centered on the second point O' will form the first quadrant Q1 and the second quadrant Q2. The third quadrant Q3 is formed by the third ellipse, the fourth quadrant Q4 is formed by the fourth ellipse, the first quadrant Q1 is formed by the first ellipse, and the second quadrant Q2 is formed by the second ellipse.

[0134] Additionally, the inner circumferential surface 1332 of the cylinder 133 in this embodiment may include a proximal portion 1332a, a distal portion 1332b, and a curved portion 1332c. The proximal portion 1332a is the part closest to the outer circumferential surface (or the rotation center of the roller) 1341 of the roller 134, the distal portion 1332b is the part furthest from the outer circumferential surface 1341 of the roller 134, and the curved portion 1332c is the part connecting the proximal portion 1332a and the distal portion 1332b.

[0135] In the proximal portion 1332a, the closest position between the cylinder 133 and the roller 134 can be defined as the contact point P, which can be divided into the first quadrant Q1 and the fourth quadrant Q4, as described above, with the proximal portion 1332a as the center. On both sides centered on the proximal portion 1332a, an intake port 1331 can be formed in the first quadrant Q1, and an exhaust port 1313 can be formed in the fourth quadrant Q4. Therefore, when the blades 1351, 1352, and 1353 pass through the contact point P, the compression surface on the rotational direction side of the blades 1351, 1352, and 1353 will be subjected to a low intake pressure, while the compression back side, on the opposite side, will be subjected to a high exhaust pressure. Therefore, during the process of the roller 134 passing through the contact point P, the front surfaces 1351a, 1352a, 1353a of each blade 1351, 1352, 1353 that are in contact with the inner circumferential surface of the cylinder 133 and the rear surfaces 1351b, 1352b, 1353b of each blade 1351, 1352, 1353 that are facing the back pressure chambers 1347a, 1347b, 1347c will bear the greatest variable pressure, so the blades 1351, 1352, 1353 may vibrate significantly.

[0136] Therefore, in this embodiment, each blade 1351, 1352, 1353 has a blade spring 1342a, 1342b, 1342c (described later) on its rear surface 1351b, 1352b, 1353 to suppress the phenomenon of each blade 1351, 1352, 1353 being pushed rearward around the contact point P, thereby preventing the blades 1351, 1352, 1353 from shaking around the contact point P in advance. The blade springs 1342a, 1342b, 1342c will be described again later.

[0137] Reference Figures 1 to 3 In this embodiment, the roller 134 is rotatably disposed in the compression space V of the cylinder 133, and the plurality of blades 1351, 1352, and 1353, described later, can be inserted into the roller 134 at predetermined intervals along the circumference. Therefore, the compression space V can be divided into compression chambers according to the number of blades 1351, 1352, and 1353. In this embodiment, the plurality of blades 1351, 1352, and 1353 are configured as three, so the description will focus on an example where the compression space V is divided into three compression chambers V1, V2, and V3.

[0138] As previously described, the roller 134 can extend integrally from the rotating shaft 123, or it can be manufactured separately from the rotating shaft 123 and then assembled. In this embodiment, the example of the roller 134 being assembled with the rotating shaft 123 will be described in detail.

[0139] However, even when the roller 134 extends integrally with the rotating shaft 123, the rotating shaft 123 and the roller 134 can be formed similarly to those in this embodiment, and the resulting basic effects can be almost similar to those in this embodiment. However, as shown in this embodiment, when the roller 134 is subsequently assembled with the rotating shaft 123, the roller 134 can be formed from a different material than the rotating shaft 123, for example, a harder material that is lighter than the rotating shaft 123. In this case, the roller body 1341, which is equipped with the blade springs 1342a, 1342b, and 1342c described later, can be easily machined while reducing the weight of the rotating body including the roller 134, thereby improving compressor efficiency.

[0140] In this embodiment, the roller 134 can be formed as a single unit, that is, an integral roller consisting of a single roller body 1341. However, the roller 134 does not necessarily have to be formed as a single unit. For example, the roller 134 can also be formed as a separate roller that is separated into a plurality of roller bodies 1341. This will be described later with reference to other embodiments. In this embodiment, the description focuses on the integral roller 134 that is configured as a single unit. Separate rollers will be described later with reference to other embodiments.

[0141] Reference Figures 1 to 3 In this embodiment, the roller 134 may include a roller body 1341 and a plurality of leaf springs 1342a, 1342b, and 1342c.

[0142] The roller body 1341 can be formed as an annular ring with a shaft hole 134a at its center. For example, the roller body 1341 has an inner circumferential surface 1341a and an outer circumferential surface 1341b, and the inner circumferential surface 1341a and the outer circumferential surface 1341b of the roller body 1341 can each be formed as a circle.

[0143] The inner circumferential surface 1341a of the roller body 1341 that forms the shaft hole 134a can be formed as a continuous surface. In this case, the rotating shaft 123 is pressed into the shaft hole 134a of the roller body 1341, thereby enabling integral bonding.

[0144] However, as shown in this embodiment, the rotating shaft 123 can be inserted axially into the shaft hole 134a of the roller body 1341. In this case, anti-spinning portions 1341c and 123b of the roller 134 or the rotating shaft 123 can be formed between the inner circumferential surface 1341a of the roller body 1341 and the outer circumferential surface 123a of the rotating shaft 123. Therefore, the inner circumferential surface 1341a of the roller body 1341 constituting the shaft hole 134a can be formed as a discontinuous surface.

[0145] For example, such as Figure 2 and Figure 3As shown, an anti-rotation key 123b is radially protruding from the outer circumferential surface 123a of the rotating shaft 123, and an anti-rotation groove 1341a is radially recessed from the inner circumferential surface 1341a of the corresponding roller body 1341. The anti-rotation key 123b and the anti-rotation groove 1341a can be formed in corresponding shapes; for example, the anti-rotation key 123b and the anti-rotation groove 1341c can be formed in an axially elongated rectangular shape. Therefore, the anti-rotation key 123b is inserted into the anti-rotation groove 1341c to overlap circumferentially, thereby suppressing the free-spinning phenomenon of the rotating shaft 123 relative to the roller 134.

[0146] The axial length of the anti-rotation key 123b can be less than or equal to the axial length of the anti-rotation groove 1341c. For example, the axial length of the anti-rotation key 123b can be about 0.5 times smaller than the axial length of the anti-rotation groove 1341c. Therefore, the rotating shaft 123 can slide axially relative to the roller 134.

[0147] As described above, when the anti-rotation key 123b is shorter axially than the anti-rotation groove 1341c, the roller 134 will not move axially along the rotation shaft 123 even if the rotating shaft 123 moves axially together with the rotor 122. Therefore, damage caused by friction or impact between the roller 134 and the main sliding surface 1311a of the main bearing 131 and / or the secondary sliding surface 1321a of the secondary bearing 132 can be suppressed, and compression efficiency can be improved.

[0148] Although not shown in the figure, the anti-rotation key 123b and the anti-rotation groove 1341a can also be composed of multiple pairs, formed at equal intervals along the circumference. In this case, the roller 134 is more firmly connected to the rotating shaft 123, thereby enabling the rotational force of the rotating shaft 123 to be transmitted to the roller 134 more stably.

[0149] Additionally, although not shown in the figures, the outer peripheral surface 123a of the rotating shaft 123 and the inner peripheral surface 1341a of the roller body 1341 can also be formed into a D-cut shape for engagement and assembly. In this case, the aforementioned separate anti-rotation key and anti-rotation groove may not be formed.

[0150] Furthermore, the outer peripheral surface 1341b of the roller body 1341 can be formed as a discontinuous surface. For example, in the roller body 134, the blade grooves 1346a, 1346b, and 1346c (described later) can be formed to open outwards. Therefore, the outer peripheral surface 1341b of the roller body 1341 is provided with the opening surfaces of the blade grooves 1346a, 1346b, and 1346c, thereby enabling it to be formed as a discontinuous surface.

[0151] The outer peripheral surface 1341b of the roller body 1341 can be formed as a circle as described above, and the rotation center Or of the roller body 1341 can be formed on the same axis as the axis center (not marked) of the rotation shaft 123. Therefore, the roller body 1341 will rotate concentrically together with the rotation shaft 123.

[0152] However, as mentioned earlier, since the inner circumferential surface 1332 of the cylinder 133 is formed into an asymmetrical elliptical shape biased in a specific direction, the rotation center Or of the roller body 134 can be eccentrically positioned relative to the outer diameter center Oc of the cylinder 133. Therefore, one side of the outer circumferential surface 1341b of the roller body 134 is in near contact with the inner circumferential surface 1332 of the cylinder 133, specifically, the proximal portion 1332a, thereby forming a contact point P.

[0153] As previously mentioned, the contact point P can be formed at the proximal portion 1332a. Therefore, the imaginary line passing through the contact point P can be equivalent to the minor axis of the elliptic curve constituting the inner circumferential surface 1332 of the cylinder 133.

[0154] The roller body 134 has a plurality of blade grooves 1346a, 1346b, and 1346c. Blades 1351, 1352, and 1353, described later, can be slidably inserted into and engaged in each blade groove 1346a, 1346b, and 1346c. The plurality of blade grooves 1346a, 1346b, and 1346c are formed at predetermined intervals in the circumferential direction. The outer circumferential surface 1341b of the roller body 134 has a radially open opening. Back pressure chambers 1347a, 1347b, and 1347c, described later, and spring insertion grooves 1348a, 1348b, and 1348c, described later, are respectively provided on the inner end opposite to the opening, thereby forming a radially blocked shape.

[0155] A plurality of blade grooves 1346a, 1346b, and 1346c are defined as first blade groove 1346a, second blade groove 1346b, and third blade groove 1346c along the compression direction (rotation direction of the roller). The first blade groove 1346a, second blade groove 1346b, and third blade groove 1346c can be formed in the same manner along the circumferential direction at equal or non-equal intervals.

[0156] For example, each blade groove 1346a, 1346b, and 1346c is formed at a predetermined angle relative to the radial direction, thereby ensuring the lengths of blades 1351, 1352, and 1353. Therefore, even when the inner circumferential surface 1332 of the cylinder 133 is formed into an asymmetrical elliptical shape, the distance from the outer circumferential surface 1341b of the roller body 1341 to the inner circumferential surface 1332 of the cylinder 133 increases, preventing blades 1351, 1352, and 1353 from detaching from the blade grooves 1346a, 1346b, and 1346c. This not only increases the design freedom of the inner circumferential surface 1332 of the cylinder 133 but also increases the design freedom of the roller 134.

[0157] The direction in which the blade grooves 1346a, 1346b, and 1346c are inclined can preferably be opposite to the rotation direction of the roller 134. That is, the front surfaces 1351a, 1352a, and 1353a of each blade 1351, 1352, and 1353 that are in contact with the inner circumferential surface 1332 of the cylinder 133 are inclined toward the rotation direction of the roller 134. This can pull the compression initiation angle toward the rotation direction of the roller 134, thereby enabling rapid compression to begin.

[0158] The inner ends of each blade slot 1346a, 1346b, 1346c can be configured to communicate with each back pressure chamber 1347a, 1347b, 1347c. Each back pressure chamber 1347a, 1347b, 1347c is a space that accommodates oil (or refrigerant) at discharge pressure or intermediate pressure on the rear side of each blade 1351, 1352, 1353, i.e., the rear side 1351c, 1352c, 1353c of the blades 1351, 1352, 1353. Under the pressure of the oil (or refrigerant) filling the back pressure chambers 1347a, 1347b, 1347c, each blade 1351, 1352, 1353 can apply pressure to the inner circumferential surface of the cylinder 133. The following explanation will be based on the direction of blade movement, defining the direction toward the inner circumference of the cylinder as the front and the opposite side as the rear.

[0159] Although not shown in the figures, the plurality of blade grooves 1346a, 1346b, and 1346c can also be formed radially, i.e., radially, relative to the rotation center Or of the roller 134. Even in this case, blade springs 1342a, 1342b, and 1342c, described later, can be respectively provided on the rear side of the blades 1351, 1352, and 1353. The resulting effect is similar to that of the embodiment described later, in which the plurality of blade grooves 1346a, 1346b, and 1346c are formed at an angle relative to the rotation center Or of the roller 134; therefore, the description thereon will be replaced by a description of the embodiment described later.

[0160] Back pressure chambers 1347a, 1347b, and 1347c can be configured to be sealed by the main bearing 131 and the auxiliary bearing 132, respectively. Back pressure chambers 1347a, 1347b, and 1347c can be independently connected to each of the back pressure bags 1315a and 1315b, 1325a and 1325b, or they can be configured to be connected to each other through the back pressure bags 1315a and 1315b, 1325a and 1325b.

[0161] Spring insertion slots 1348a, 1348b, and 1348c, respectively, for inserting leaf springs 1342a, 1342b, and 1342c (described later), can be formed on one axial side of the back pressure chambers 1347a, 1347b, and 1347c. For example, a first spring insertion slot 1348a is formed at the inner end of the first leaf groove 1346a in the groove direction, a second spring insertion slot 1348b is formed at the inner end of the second leaf groove 1346b in the groove direction, and a third spring insertion slot 1348c is formed at the inner end of the third leaf groove 1346c in the groove direction. The first leaf spring 1342a (described later) can be inserted into the first spring insertion slot 1348a, the second leaf spring 1342b (described later) can be inserted into the second spring insertion slot 1348b, and the third leaf spring 1342c (described later) can be inserted into the third spring insertion slot 1348c.

[0162] The first spring insertion groove 1348a can be formed between the first blade groove 1346a and the first back pressure chamber 1347a, the second spring insertion groove 1348b can be formed between the second blade groove 1346b and the second back pressure chamber 1347b, and the third spring insertion groove 1348c can be formed between the third blade groove 1346c and the third back pressure chamber 1347c.

[0163] These first spring insertion slots 1348a, second spring insertion slots 1348b, and third spring insertion slots 1348c can be respectively formed to overlap axially with their respective blade slots 1346a, 1346b, 1346c and their respective back pressure chambers 1347a, 1347b, 1347c on one side of the roller body 1341. Therefore, the rear surfaces 1351b, 1352b, 1353b of the blades 1351, 1352, 1353 inserted into the blade slots 1346a, 1346b, 1346c can be elastically supported by their respective blade springs 1342a, 1342b, 1342c from their respective blade slots 1346a, 1346b, 1346c toward the inner circumferential surface 1332 of the cylinder 133 along the slot length direction (hereinafter, the slot direction). The spring insertion slots 1348a, 1348b, and 1348c will be described again together with the leaf springs 1342a, 1342b, and 1342c.

[0164] Reference Figures 1 to 3 In this embodiment, a plurality of blades 1351, 1352, and 1353 can be slidably inserted into each blade groove 1346a, 1346b, and 1346c. Therefore, the plurality of blades 1351, 1352, and 1353 can be formed to have a shape substantially the same as that of each blade groove 1346a, 1346b, and 1346c.

[0165] For example, a plurality of blades 1351, 1352, and 1353 can be defined as first blade 1351, second blade 1352, and third blade 1353 according to the rotation direction of roller 134. First blade 1351 can be inserted into first blade groove 1346a, second blade 1352 can be inserted into second blade groove 1346b, and third blade 1353 can be inserted into third blade groove 1346c.

[0166] The plurality of blades 1351, 1352, and 1353 can be formed into substantially the same shape. For example, the plurality of blades 1351, 1352, and 1353 can each be formed into a substantially cuboid shape, and the leading surfaces 1351a, 1352a, and 1353a of the blades 1351, 1352, and 1353 that are in contact with the inner circumferential surface 1332 of the cylinder 133 can be formed into curved surfaces along the circumferential direction. Therefore, the leading surfaces 1351a, 1352a, and 1353a of the blades 1351, 1352, and 1353 will be in line contact with the inner circumferential surface 1332 of the cylinder 133, thereby reducing frictional losses.

[0167] Reference Figure 2 and Figure 3 In this embodiment, the leaf springs 1342a, 1342b, and 1342c are each composed of a compression coil spring and can be inserted into their respective spring insertion slots 1348a, 1348b, and 1348c. Therefore, the leaf springs 1342a, 1342b, and 1342c can elastically support the rear sides 1351b, 1352b, and 1353b of each blade 1351, 1352, and 1353 towards the front.

[0168] The first ends 1342a1, 1342b1, and 1342c1 at the rear ends of each leaf spring 1342a, 1342b, and 1342c1 can respectively contact and be supported by the first spring fixing surface 1349a of each spring insertion slot 1348a, 1348b, and 1348c. The second ends 1342a2, 1342b1, and 1342c1 at the front ends of each leaf spring 1342a, 1342b, and 1342c... 2. 1342c2 can contact and be supported by the second spring fixing surface 1349b of each spring insertion slot 1348a, 1348b, 1348c according to the position of the corresponding blades 1351, 1352, 1353, or contact the rear surfaces 1351b, 1352b, 1353b of each blade 1351, 1352, 1353 respectively, and elastically support the corresponding blades 1351, 1352, 1353. The blade springs 1342a, 1342b, 1342c will be explained again later along with the spring insertion slots 1348a, 1348b, 1348c.

[0169] The unexplained symbol 1351d in the diagram is the oil supply tank.

[0170] In a rotary vane compressor having a mixing cylinder as described above, when power is supplied to the drive motor 120, the rotor 122 of the drive motor 120 and the rotating shaft 123 coupled to the rotor 122 will rotate, and the roller 134 coupled to or integrally formed with the rotating shaft 123 will rotate together with the rotating shaft 123.

[0171] In that case, under the centrifugal force generated by the rotation of the roller 134 and the back pressure of the back pressure chambers 1347a, 1347b, 1347c supporting the rear surfaces 1351, 1352, 1353 of the plurality of blades, the blades 1351, 1352, 1353 will be drawn out from their respective blade slots 1346a, 1346b, 1346c and come into contact with the inner circumferential surface 1332 of the cylinder 133.

[0172] Then, the compression space V of the cylinder 133 is divided into compression chambers (including suction chambers or discharge chambers) V1, V2, V3 by a plurality of blades 1351, 1352, 1353, corresponding to the number of blades 1351, 1352, 1353. Each compression chamber V1, V2, V3 will repeatedly undergo the following series of processes: each compression chamber V1, V2, V3 moves with the rotation of the roller 134, and its volume changes according to the shape of the inner circumferential surface 1332 of the cylinder 133 and the eccentricity of the roller 134. The refrigerant sucked into each compression chamber V1, V2, V3 is compressed while moving along the roller 134 and the blades 1351, 1352, 1353, and is discharged into the internal space of the outer casing 110.

[0173] Furthermore, as mentioned earlier, in the rotary vane compressor of this embodiment, in the section from the contact point P between the cylinder 133 and the roller 134 to the suction port 1331, the leading surfaces 1351a, 1352a, and 1353a of each vane 1351, 1352, and 1353 are simultaneously subjected to compression pressure and suction pressure. Therefore, the vibration of each vane 1351, 1352, and 1353 caused by pressure imbalance in the aforementioned section may be greater than in other sections. Due to the vibration of blades 1351, 1352, and 1353, leakage may occur between the compression chambers, impact noise and vibration may occur between the cylinder 133 and each blade 1351, 1352, and 1353, and wear may occur on the inner circumferential surface 1332 of the cylinder 133 or the leading surfaces 1351a, 1352a, and 1353a of each blade 1351, 1352, and 1353, which may aggravate intake loss and compression loss.

[0174] Therefore, in this embodiment, by providing blade springs 1342a, 1342b, and 1342c inside the roller 134 to elastically support the blades 1351, 1352, and 1353 to the inner circumferential surface 1332 of the cylinder 133, the blades 1351, 1352, and 1353 are prevented from being pushed backward, thereby suppressing the vibration phenomenon of the blades 1351, 1352, and 1353.

[0175] Figure 4 It is decomposition Figure 2 A three-dimensional diagram showing the rotating shaft and rollers. Figure 5 It is assembly Figure 4 The rotating shaft and rollers are shown in a three-dimensional diagram.

[0176] Reference Figure 4 and Figure 5 At the inner end of each blade groove 1346a, 1346b, 1346c in the groove direction, that is, at the end opposite to the opening surface of each blade groove 1346a, 1346b, 1346c, spring insertion grooves 1348a, 1348b, 1348c can be formed between each blade groove 1346a, 1346b, 1346c and each back pressure chamber 1347a, 1347b, 1347c.

[0177] For example, the respective spring insertion grooves 1348a, 1348b, and 1348c can be formed such that they are recessed to a predetermined depth on the axial upper surface of the roller body 1341 and overlap axially with respect to the respective blade grooves 1346a, 1346b, and 1346c and the respective back pressure chambers 1347a, 1347b, and 1347c.

[0178] Leaf springs 1342a, 1342b, and 1342c can be inserted into their respective spring insertion slots 1348a, 1348b, and 1348c. The leaf springs 1342a, 1342b, and 1342c elastically support the rear surfaces 1351b, 1352b, and 1353b of each leaf 1351, 1352, and 1353 along the groove direction (centrifugal force direction) toward the inner circumferential surface 1332 of the cylinder 133.

[0179] In this case, spring support portions 1351c, 1352c, and 1353c, respectively, which are supported by one end of the blade springs 1342a, 1342b, and 1342c, can be formed on the rear sides 1351b, 1352b, and 1353b of the blades 1351, 1352, and 1353c. Each spring support portion 1351c, 1352c, and 1353c can be formed in a stepped shape to correspond to its respective spring insertion slot 1348a, 1348b, and 1348c.

[0180] The leaf springs 1342a, 1342b, and 1342c can be constructed from compression helical springs having the same elastic force. For example, each leaf spring 1342a, 1342b, and 1342c can be formed to have the same wire diameter, free length, and maximum compressed length. Therefore, the surface pressure generated on the same inner circumferential surface 1332 of the cylinder 133 between the cylinder 133 and the leaf springs 1351, 1352, and 1353 can be maintained constant.

[0181] Furthermore, the respective leaf springs 1342a, 1342b, and 1342c can be formed to have the same outer diameter. Therefore, not only can the respective spring insertion slots 1348a, 1348b, and 1348c be easily machined, but the respective blades 1351, 1352, and 1353 can also be easily inserted into the respective spring insertion slots 1348a, 1348b, and 1348c.

[0182] These blade slots 1346a, 1346b, 1346c and spring insertion slots 1348a, 1348b, 1348c, including the blades 1351, 1352, 1353 of the spring support portions 1351c, 1352c, 1353c and the blade springs 1342a, 1342b, 1342c, each forming a pair. These pairs of blade slots 1346a, 1346b, 1346c and spring insertion slots 1348a, 1348b, 1348c, including the blades 1351, 1352, 1353 of the spring support portions 1351c, 1352c, 1353c and the blade springs 1342a, 1342b, 1342c can be formed to have the same shape and specifications as each other.

[0183] Hereinafter, the first group, comprising the first spring insertion slot 1348a paired with the first blade slot 1346a, the first blade spring 1342a, and the first blade 1351, is defined as a representative example and will be described accordingly. However, it should be understood that this is not limited to the first group including the first blade 1351, but also applies to the second group including the second blade 1352 and the third group including the third blade 1353. This can also be understood as meaning that it applies equally even when the number of blades is greater.

[0184] Figure 6 It is magnification Figure 5 A portion of the compression section is shown in a three-dimensional view. Figure 7 yes Figure 6 Sectional view along line "Ⅳ-Ⅳ" in the middle. Figure 8 It shows the basis Figure 5 A schematic diagram showing the relationship between the position of the blades and the blade spring.

[0185] Reference Figure 6 and Figure 7 As described above, the first spring insertion groove 1348a in this embodiment can be formed such that the upper half of the roller body 1341, that is, the upper surface of the roller 134 facing the discharge port 1313, is recessed axially to a predetermined depth.

[0186] The first spring insertion groove 1348a can be formed at a position that overlaps axially with the first back pressure chamber 1347a, so as to communicate with the rear end of the first blade groove 1346a. Therefore, the first spring insertion groove 1348a communicates with the first main back pressure bag 1315a and the second main back pressure bag 1315b provided in the main bearing 131, so that the first spring insertion groove 1348a can function as the first back pressure chamber 1347a.

[0187] The first spring insertion groove 1348a is formed into a quadrangular cross-section shape when projected axially, so the major axis direction (or minor axis direction) can be arranged in the same or parallel direction as the groove direction. Therefore, the inner and outer surfaces of the first spring insertion groove 1348a can be formed to be orthogonal to the groove direction on both sides of the groove direction.

[0188] For example, the first spring insertion slot 1348a in this embodiment may include a first spring fixing surface 1349a disposed on one side of the slot direction and a second spring fixing surface 1349b disposed on the other side of the slot direction.

[0189] The first spring fixing surface 1349a can form the inner side of the first spring insertion groove 1348a and can be positioned adjacent to the rotation center Or of the roller body 1341. The second spring fixing surface 1349b can form the outer side of the first spring insertion groove 1348a and can be positioned further away from the center of the roller body 1341 than the first spring fixing surface 1349a.

[0190] The first spring fixing surface 1349a and the second spring fixing surface 1349b are formed to be orthogonal to the groove direction, and the lateral width (length of the direction orthogonal to the groove direction) L21 of the first spring fixing surface 1349a and the second spring fixing surface 1349b can be formed to be greater than the lateral width L1 of the first blade groove 1346a.

[0191] In this case, the second spring fixing surface 1349b is preferably spaced from the outer peripheral surface of the roller 134 to a degree that ensures an appropriate sealing distance L3. For example, the sealing distance L3 can be formed to be greater than or equal to half the lateral width L1 of the first blade groove 1346a. Specifically, the sealing distance can preferably be formed to be approximately 1.5 to 2 mm or more. This can suppress leakage between the compression chambers through the first spring insertion groove 1348a.

[0192] Furthermore, the groove spacing (same as the groove length of the spring insertion groove) L22 between the first spring fixing surface 1349a and the second spring fixing surface 1349b can be formed to be greater than the maximum compressed length of the first leaf spring 1342a. Therefore, the first end 1342a1 of the first leaf spring 1342a inserted into the first spring insertion groove 1348a can be supported on the first spring fixing surface 1349a, and the second end 1342a2 of the first leaf spring 1342a can be supported on the second spring fixing surface 1349b.

[0193] At this time, as mentioned above, since the groove direction distance L22 between the first spring fixing surface 1349a and the second spring fixing surface 1349b is less than or equal to the free state length of the first leaf spring 1342a, the two ends of the first leaf spring 1342a can be tightly fixed to the first spring fixing surface 1349a and the second spring fixing surface 1349b respectively.

[0194] Reference Figure 6 and Figure 7 As described above, the first blade 1351 of this embodiment can be formed as a rectangular hexahedron, and the rear side 1351b of the first blade 1351 facing the first back pressure chamber 1347a can be formed in a stepped manner.

[0195] For example, the first blade 1351 may have a first spring support portion 1351c formed in a stepped manner on the upper edge of the side surface (upper surface) connecting the rear side 1351b of the first blade 1351 and the axial side surface. Therefore, the first spring support portion 1351c may overlap axially with the second end 1342a2 of the first blade spring 1342a in the second interval α2 described later.

[0196] The first spring support portion 1351c can be formed to correspond to the aforementioned first spring insertion slot 1348a. For example, the first spring support portion 1351c can be formed into a right-angle shape with a stepped upper edge on the rear side of the first blade 1351.

[0197] Specifically, the first spring support portion 1351c in this embodiment may include a first support surface 1351c1 and a second support surface 1351c2. The first support surface 1351c1 may extend in the groove direction, and the second support surface 1351c2 may extend from the front end of the first support surface 1351c1 toward the axial upper surface of the first blade 1351.

[0198] The first support surface 1351c1 can be formed as a plane or as a curved surface to correspond to the outer peripheral surface of the first leaf spring 1342a.

[0199] The groove direction length of the first support surface 1351c1 can be defined as the groove direction length L41 of the first spring support portion 1351c. The groove direction length L41 of the first support surface 1351c1 can be formed such that, in the interval outside a certain interval, the second support surface 1351c2 is located inside the first blade groove 1346a, while in the specific interval, the second support surface 1351c2 protrudes outward from the first blade groove 1346a.

[0200] For example, when the front surface 1351a of the first blade 1351 passes through the first interval α1 including the distal portion 1332b of the cylinder 133, the second support surface 1351c2 is located inside the first blade groove 1346a, and when the front surface 1351a of the first blade 1351 passes through the second interval α2 including the proximal portion 1332a of the cylinder 133, the second support surface 1351c2 protrudes outward from the first blade groove 1346a, thereby being formed to be located inside the first spring insertion groove 1348a.

[0201] In other words, the groove-direction length L41 of the first spring support portion 1351c can be formed such that, in the first interval α1 including the intake stroke and the compression stroke, it does not protrude further rearward than the second spring fixing surface 1349b of the first spring insertion groove 1348a, but in the second interval α2 including the discharge stroke (or, a part of the compression stroke and a part of the intake stroke), it protrudes further rearward than the second spring fixing surface 1349b of the first spring insertion groove 1348a. Therefore, in the first interval α1, the first blade 1351 can be separated from the first blade spring 1342a, while in the second interval α2, the first blade 1351 can be elastically supported by the first blade spring 1342a. Thus, in the second interval α2, the first blade 1351 can be supported along the groove direction by the combined pressure F of the centrifugal force F1, the back pressure F2 of the first back pressure chamber 1347a, and the elastic force F3 of the first blade spring 1342a inserted into the first spring insertion groove 1348a.

[0202] Furthermore, the groove length L41 of the first support surface 1351c1 can be formed to be less than half the groove length of the first blade 1351, and can be formed to a length such that in the first interval α1, the second support surface 1351c2 does not protrude beyond the opening surface of the roller but is located inside the first blade groove 1346a. Therefore, leakage between the compression chambers through the first spring support portion 1351c can be suppressed.

[0203] The second support surface 1351c2 can be formed as a plane to closely adhere to the second end 1342a2 of the first leaf spring 1342a.

[0204] The axial depth L42 of the second support surface 1351c2 can be formed to be greater than or equal to the axial depth L23 of the first spring insertion groove 1348a. Therefore, by suppressing the contact between the first support surface 1351c1 of the first spring support portion 1351c and the first leaf spring 1342a inserted into the first spring insertion groove 1348a, the reliability of the first leaf 1351 and the first leaf spring 1342a can be improved.

[0205] For example, the axial depth L42 of the second support surface 1351c2 can be formed to be smaller than the axial height H1 of the first blade 1351 or roller 134, and as... Figure 7 As shown, it can be formed to be less than 1 / 2 of the axial height H1 of the first blade 1351 or the roller. Therefore, the axial height H2 of the first blade spring 1342a can be located at a position higher than the middle of the first blade 1351.

[0206] In other words, the first spring support 1351c can be formed as the edge between the upper surface of the first blade 1351 facing the main bearing and the rear surface 1351b. Therefore, even if the pressure on the upper half of the first blade 1351 adjacent to the discharge port 1313 is relatively higher than the pressure on the lower half of the first blade 1351 on the opposite side, the upper half of the first blade 1351 can be elastically supported by the first blade spring 1342a, thereby balancing the pressure F on both sides of the first blade 1351 axially. Thus, by suppressing the tilting of the first blade 1351 to prevent unilateral wear in advance, refrigerant leakage can be more effectively suppressed.

[0207] Reference Figure 6 and Figure 7 In this embodiment, the first leaf spring 1342a can be constructed from a compression helical spring. For example, the first leaf spring 1342a has a first end 1342a1 and a second end 1342a2. The maximum length between the first end 1342a1 and the second end 1342a2, i.e., the free-state length of the first leaf spring 1342a, can be formed to be greater than or equal to the slot direction distance L22 between the first spring fixing surface 1349a and the second spring fixing surface 1349b. Therefore, the first end 1342a1 of the first leaf spring 1342a is in close contact with the first spring fixing surface 1349a, and the second end 1342a2 of the first leaf spring 1342a is in close contact with the second spring fixing surface 1349b, thereby preventing the first leaf spring 1342a from detaching.

[0208] The outer diameter of the first leaf spring 1342a can be formed to a size that prevents it from getting stuck inside the first leaf groove 1346a. For example, the outer diameter of the first leaf spring 1342a can be formed to be larger than the lateral width L1 of the first leaf groove 1346a. More specifically, the outer diameter of the first leaf spring 1342a can be formed to be larger than half of the lateral width L1 of the first spring fixing surface 1349a. Therefore, even if the second end 1342a2 of the first leaf spring 1342a is twisted relative to the groove direction, it can prevent the second end 1342a2 of the first leaf spring 1342a from getting stuck in the first leaf groove 1346a, so that the first leaf spring 1342a can stably support the first leaf 1351.

[0209] Although not shown in the figure, the outer diameter of the first leaf spring 1342a can also be made smaller than the lateral width L1 of the first leaf groove 1346a. In this case, the first leaf spring 1342a is inserted into the first leaf groove 1346a, so that the first leaf 1351 can be supported only by the first leaf spring 1342a. In that case, the aforementioned back pressure bags 1315a and 1315b, 1325a and 1325b can be excluded from the respective bearings 131 and 132, thereby simplifying the structure of the compression section. Moreover, the bearing surface supporting the rotating shaft can be formed into an annular shape, thereby providing more stable support for the rotating shaft.

[0210] Although not shown in the figures, even when the outer diameter of the first leaf spring 1342a is larger than the lateral width L1 of the first leaf groove 1346a, the first spring insertion groove 1348a can extend along the groove direction and form on the inner sides of both rear sides of the first leaf groove 1346a. In this case, the first leaf spring 1342a is inserted into the first leaf groove 1346a, so that the first leaf 1351 can only be supported by the first leaf spring 1342a. The effect in this case is similar to that in the aforementioned embodiment.

[0211] As described above, in the rotary vane compressor of this embodiment, when the first vane 1351 passes through most of the distal portion 1332b and the curved portion 1332c of the cylinder 133 including the first interval α1, it separates from the first vane spring 1342a to suppress friction loss. When the first vane 1351 passes through the proximal portion 1332c including the second interval α2, it contacts the first vane spring 1342a and applies pressure to the inner circumferential surface of the cylinder 133, thus suppressing vane vibration as pressure is applied.

[0212] Figure 9a and Figure 9b It is magnification Figure 8 A schematic diagram showing the support status of the blades at various positions. Figure 9a This is a diagram showing the distal region. Figure 9b This is a diagram showing the proximal region. Figure 10 It is used for explanation Figure 8 A cross-sectional view showing the support state of the blades near the contact point.

[0213] First, when the compressor stops, the first end 1342a1 of the first blade spring 1342a is in close contact with the first spring fixing surface 1349a of the first spring insertion slot 1348a, and the second end 1342a2 of the first blade spring 1342a is in close contact with the second spring fixing surface 1349b of the first spring insertion slot 1348a, thereby maintaining the fixed initial state. Therefore, the first blade spring 1342a is able to remain in the initial state without disengaging from the first spring insertion slot 1348a.

[0214] Subsequently, when the compressor is running, depending on the position of the first blade 1351, the second end 1342a2 of the first blade spring 1342a remains in close contact with the second spring fixing surface 1349b of the first spring insertion groove 1348a, or contacts the rear surface 1351b of the first blade 1351, so that the first blade 1351 is elastically supported to apply pressure toward the inner circumferential surface 1332 of the cylinder 133.

[0215] Specifically, such as Figure 8 and Figure 9a As shown, when the first blade 1351 passes through the distal portion 1332b and the curved portion 1332c constituting the first interval α1, the first blade 1351 is pushed away from the rotation center Or of the roller 134. In this case, the rear surface 1351b of the first blade 1351, specifically the first spring support portion 1351c, will be hidden within the first blade groove 1346a. In this case, the first end 1342a1 of the first blade spring 1342a will remain in its initial state, tightly abutting the second spring fixing surface 1349b of the first spring insertion groove 1348a.

[0216] On the contrary, such as Figure 8 and Figure 9b As shown, when the first blade 1351 passes through the proximal portion 1332c constituting the second interval α2, the first blade 1351 is pushed into the rotation center Or side near the roller 134. In this case, the first spring support portion 1351c provided on the rear surface 1351b of the first blade 1351 will be pushed out of the first blade groove 1346a, in other words, pushed into the inner side of the first spring insertion groove 1348a. Then, the second support surface 1351c2 of the first spring support portion 1351c will contact the second end 1342a2 of the first blade spring 1342a.

[0217] Reference Figure 10 As the first blade 1351 gradually approaches the contact point P, it gradually approaches the rotation center Or side of the roller 134. The second end 1342a2 of the first blade spring 1342a, separated from the second spring fixing surface 1349b of the first spring insertion slot 1348a, transmits the elastic force F3 to the first blade 1351. In this case, the first blade 1351, in addition to the centrifugal force F1 and the back pressure F2, is also subjected to a force combining the elastic force F3 of the first blade spring 1342a, i.e., pressure F, thereby being pressurized in the direction toward the inner circumferential surface 1332 of the cylinder 133.

[0218] As previously described, the first blade 1351, the first spring insertion slot 1348a, and the first blade spring 1342a can be formed to be identical to the second blade 1352 and the third blade 1353, the second spring insertion slot 1348b and the third spring insertion slot 1348c, and the second blade spring 1342b and the third blade spring 1342c, respectively. Therefore, the second blade 1352 and the third blade 1353 can also be elastically supported towards the inner circumferential surface of the cylinder 133 by the second blade spring 1342b and the third blade spring 1342c when passing through the second interval α2.

[0219] Thus, the rotary vane compressor of this embodiment, by providing an additional elastic force to the rear of the vanes in addition to the back pressure, can suppress vane vibration that occurs when the vanes pass through the proximal portion during operation. In particular, vane vibration, which may be more severe during the initial startup of the compressor, can be effectively suppressed, thereby preventing poor initial startup and improving compressor efficiency. Furthermore, when applied to air conditioning, it can quickly achieve cooling or heating effects, thus improving reliability.

[0220] Furthermore, the rotary vane compressor of this embodiment suppresses vane vibration around the contact point, thereby preventing wear on the inner circumferential surface of the cylinder or the leading edge of the vanes around the contact point. Thus, while reducing vibration noise around the contact point, it can suppress leakage between compression chambers and improve compression efficiency.

[0221] Furthermore, the rotary vane compressor of this embodiment can further homogenize the pressure on the vanes by utilizing the elastic force provided on the rear side of the vanes. This allows for more effective suppression of vane vibration. Moreover, since the rear side of the vanes is provided with both back pressure from the oil and elastic force from the vane springs, the burden on the back pressure is reduced, thereby simplifying the back pressure structure for supplying oil to the rear side of the vanes.

[0222] Furthermore, the aforementioned effects can be further expected when the rotary compressor of this embodiment uses high-pressure refrigerants such as R32, R410a, and CO2.

[0223] In addition, another embodiment of the blade support structure of the present invention is as follows.

[0224] That is, in the aforementioned embodiment, the spring support portion is formed to be less than half of the axial height of the blade, but depending on the circumstances, the spring support portion may also be formed to be more than half of the axial height of the blade.

[0225] Figure 11 It is shown Figure 4 A cross-sectional view of another embodiment of the blade support structure. Figure 12 It is shown Figure 4 A cross-sectional view of another embodiment of the blade support structure.

[0226] Reference Figure 11 The basic structure and function of the roller 134 including the first blade groove 1346a and the first spring insertion groove 1348a, the first blade 1351 including the first spring support part 1351c, and the first blade spring 1342a in this embodiment are almost the same as those in the aforementioned embodiment.

[0227] In other words, the first spring insertion groove 1348a is formed to communicate with the first blade groove 1346a on the upper surface of the roller 134, and the first spring support portion 1351c is formed in a stepped manner on the upper edge of the rear side 1351b of the first blade 1351. The first blade spring 1342a is composed of a compression helical spring, thereby maintaining the state of the first blade spring 1342a inserted into the first spring insertion groove 1348a in the first interval α1, or supporting the first spring support portion 1351c in the second interval α2, thereby pressurizing the first blade 1351 toward the cylinder 1332.

[0228] However, in this embodiment, the axial depth L23 of the first spring insertion groove 1348a can be formed to be more than half of the axial height H1 of the roller 134, and the axial depth L42 of the first spring support portion 1351c can be formed to be more than half of the axial height H1 of the first blade 1351. Since the axial height H1 of the roller 134 and the axial height H1 of the first blade 1351 are almost the same, it is possible that the axial depth L23 of the first spring insertion groove 1348a and the axial depth L42 of the first spring support portion 1351c can be defined based on the same reference, i.e., based on the axial height H1 of the roller 134 or the axial height H1 of the first blade 1351.

[0229] For example, the axial depth L23 of the first spring insertion groove 1348a can be formed such that the upper surface of the roller 134 is recessed by more than half, approximately 2 / 3, of the axial height H1 of the roller 134. In this case, the axial depth L42 of the first spring support portion 1351c can be formed to be greater than or equal to the degree of the first spring insertion groove 1348a. In other words, the first spring support portion 1351c can be formed on the upper edge of the rear surface 1351b of the first blade 1351, and the depth of the second support surface 1351c2 can be formed such that the upper surface of the first blade 1351 is recessed axially by more than half, approximately 2 / 3.

[0230] As described above, when the first spring insertion slot 1348a and / or the first spring support portion 1351c are formed to be more than half of the axial height H1 of the roller 134 and / or the first blade 1351, the first blade spring 1342a can be located at a height close to the axial middle of the roller 134.

[0231] For example, such as Figure 11 As shown, when the first spring insertion groove 1348a and / or the first spring support portion 1351c are formed to be more than 2 / 3 of the axial height H1 of the roller 134 and / or the first blade 1351, the axial height H2' of the first blade spring 1342a can be located at the middle position of the first blade 1351, that is, the axial middle height of the first blade 1351.

[0232] In this way, the elastic force F3 generated by the first leaf spring 1342a is supplied equally along the axial direction of the first leaf 1351, thereby ensuring a constant pressure F applied to the first leaf 1351 toward the inner circumferential surface 1332 of the cylinder 133 along the axial direction. As a result, a constant surface pressure is maintained between the leading surface 1351a of the first leaf 1351 and the inner circumferential surface 1332 of the cylinder 133 opposite thereto, thereby suppressing unilateral friction or unilateral wear in the first leaf 1351 and / or the cylinder 133.

[0233] Alternatively, the first spring support portion 1351c may also form a groove shape on the rear side 1351b of the first blade 1351. For example, as Figure 12 As shown, the first spring support portion 1351c can also be formed to be recessed to a predetermined depth from the rear side 1351b of the first blade 1351 in the direction toward the front side 1351a.

[0234] In this configuration, the first spring support portion 1351c can have first support surfaces 1351c1 formed on both axial sides of the second support surface 1351c2. Therefore, the second end 1342a2 of the first leaf spring 1351 can be supported along the groove direction by the second support surface 1351c2 of the first spring support portion 1351c, while the outer peripheral surface of the second end 1342a2 of the first leaf spring 1351 can be supported on both axial sides by the first support surfaces 1351c1 of the first spring support portion 1351c. Thus, the second end 1342a2 of the first leaf spring 1351 can be stably supported relative to the axial direction.

[0235] As described above, even when the first spring support portion 1351c is recessed in a square or conical shape on the rear side 1351b of the first blade 1351, the first spring support portion 1351c can still function as described above. Figure 7 The shape shown is eccentric to the side adjacent to the outlet 1313, or it can be as follows: Figure 11The image shows the middle height of the rear surface 1351b of the first blade 1351. The resulting effects are respectively related to... Figure 7 and Figure 11 As explained in the text.

[0236] Another embodiment of the blade support structure of the present invention is as follows.

[0237] That is, in the foregoing embodiments, the spring insertion slot is open, but depending on the circumstances, at least a portion of the spring insertion slot may also be closed.

[0238] Figure 13 It is shown Figure 4 An exploded perspective view of another embodiment of the blade support structure. Figure 14 It is magnification Figure 13 The blade support structure is shown in a cross-sectional view.

[0239] Reference Figure 13 and Figure 14 The basic structure and function of the roller 134, including the first blade groove 1346a and the first spring insertion groove 1348a, the first blade 1351 including the first spring support portion 1351c, and the first blade spring 1342a in this embodiment are almost the same as those in the aforementioned embodiments. For example, the axial depth L42 of the first spring insertion groove 1348a and the first spring support portion 1351c can be formed to be the same as that of the roller 1346a and the first spring insertion groove 1348a. Figure 11 The embodiments are the same.

[0240] In this situation, a wide gap is formed between the main sliding surface 1311a of the first leaf spring 1342a and the main bearing 131, which is axially opposite to the first leaf spring 1342a. This can cause twisting during the extension and retraction of the first leaf spring 1342a. If the first leaf spring 1342a undergoes large twisting during extension and retraction, the elastic force F3 transmitted to the first leaf 1351 cannot be maintained constantly, and the surface pressure between the first leaf 1351 and the cylinder 133 may become uneven. In that case, wear between the leading surface 1351a of the first leaf 1351 and the inner circumferential surface 1332 of the cylinder 133 may increase.

[0241] Therefore, in this embodiment, at the upper end of the first spring insertion groove 1348a, i.e., when the first leaf spring 1342a is inserted, a first cover member (stop member) 1343a can be provided on the upper side of the first leaf spring 1342a. For example, a first cover insertion groove 1345a is formed in a stepped manner at the upper end of the first spring insertion groove 1348a, and the first cover member 1343a can be inserted and fixed in the first cover insertion groove 1345a.

[0242] The first cover member 1343a is constructed as a plug or spring stop, which can be pressed into or screwed into the upper end of the first spring insertion groove 1348a for fixation. In this embodiment, an example of the first cover member 1343a being pressed into the first spring insertion groove 1348a is illustrated.

[0243] The first cover member 1343a is formed with the same shape along the axial direction as the first spring insertion groove 1348a, that is, a right hexahedron shape, so that it can also be pressed into the first spring insertion groove 1348a. Therefore, the outer peripheral surface of the first cover member 1343a and the inner peripheral surface of the opposite first spring insertion groove 1348a can be tightly attached to each other circumferentially.

[0244] However, the outer peripheral surface of the first cover member 1343a and the inner peripheral surface of the opposite first spring insertion groove 1348a may be at least partially separated circumferentially. For example, the width of the first cover member 1343a may be smaller than the width of the first spring insertion groove 1348a, and a first oil passage 1343a1 may be formed between the outer peripheral surface of the first cover member 1343a and the inner peripheral surface of the opposite first spring insertion groove 1348a.

[0245] The first oil passage 1343a1 can be connected to the first main back pressure bag 1315a or the second main back pressure bag 1315b. Therefore, the oil contained in the first main back pressure bag 1315a or the second main back pressure bag 1315b can flow into the interior of the first spring insertion groove 1348a through the first oil passage 1343a1.

[0246] The symbols 1343b and 1343c, which are not explained in the figure, are the second cover component and the third cover component, respectively. 1343b1 and 1343c1 are the second oil passage and the third oil passage, respectively.

[0247] As described above, when the first cover member 1343a is attached to the upper end of the first spring insertion groove 1348a, deformation of the first leaf spring 1342a during extension and contraction can be suppressed, as previously mentioned. Consequently, the elastic force F3 supplied to the first leaf 1351 is maintained uniformly, allowing the surface pressure between the first leaf 1351 and the cylinder 133 to be maintained uniformly along the axial direction.

[0248] Furthermore, with the first leaf spring 1342a inserted into the first spring insertion slot 1348a, covering the first spring insertion slot 1348a with the first cover member 1343a can prevent the first leaf spring 1342a from detaching from the first spring insertion slot 1348a. Therefore, when the first leaf spring 1342a is inserted into the first spring insertion slot 1348a, both ends of the first leaf spring 1342a do not need to be excessively pressed against the first spring fixing surface 1349a and the second spring fixing surface 1349b of the first spring insertion slot 1348a. This not only prevents the first leaf spring 1342a from detaching but also simplifies the assembly of the first leaf spring 1342a.

[0249] Although not shown in the figure, a cover insertion slot (not shown) including a plurality of spring insertion slots 1348a can be formed in an annular shape on the upper surface of the roller 134, and a cover member (not shown) can be inserted into the cover insertion slot to cover the plurality of spring insertion slots. In this case, in addition to the basic effects of the cover member mentioned above, the assembly of the cover member can be simplified, thereby reducing the manufacturing cost of the cover member.

[0250] Another embodiment of the roller of the present invention is as follows.

[0251] That is, in the aforementioned embodiments, the roller is formed as a single unit, but depending on the circumstances, the roller may also be composed of a plurality of roller bodies. In this case, the first spring insertion groove 1348a may be formed on either side of the roller body, or it may be formed on both sides of the roller body. In this embodiment, the description will focus on an example in which the roller is composed of a plurality of roller bodies, and the first spring insertion groove 1348a is formed on a portion of each of the respective roller bodies.

[0252] Figure 15 It is decomposition Figure 1 Another embodiment of the roller is shown in a perspective view. Figure 16 It is assembly Figure 15 The rollers in the diagram are shown in a three-dimensional view. Figure 17 yes Figure 16 The sectional view along line "V-V".

[0253] Reference Figures 15 to 17The compression section 130 in this embodiment is similar to the compression section 130 in the previous embodiment. For example, the compression section 130 includes a main bearing 131, a secondary bearing 132, a cylinder 133, a roller 134, and a plurality of blades 1351, 1352, and 1353. The roller 134 includes a roller body 1341 and a plurality of blade springs 1342a, 1342b, and 1342c. These main bearings 131, secondary bearings 132, cylinders 133, rollers 134, and blades 1351, 1352, and 1353 are similar to those in the previous embodiment.

[0254] However, in this embodiment, the roller 134 may be composed of a plurality of roller bodies 1341, for example, a first roller body 1345a and a second roller body 1345b. The first roller body 1345a may be located on the upper side adjacent to the drive motor 120 along the axial direction, and the second roller body 1345b may be located on the lower side of the first roller body 1345a.

[0255] The first roller body 1345a and the second roller body 1345b are fastened together by screws, thereby forming a roller 134. For example, at least one fastening hole 1341d is provided in the first roller body 1345a and the second roller body 1345b, specifically between the blade grooves 1346a, 1346b, and 1346c, so that it can be fastened with a fastening screw 1344.

[0256] The axial height of the first roller body 1345a and the axial height of the second roller body 1345b can be made to be the same. Therefore, the first leaf spring 1342a can be positioned at the middle height of the roller body 1341.

[0257] Although not shown in the figure, the axial height of the first roller body 1345a and the axial height of the second roller body 1345b can be different from each other. In this case, a spring insertion groove 1348a can be formed on either side of the first roller body 1345a and the second roller body 1345b, and the other side can be formed into a flat plate shape.

[0258] The first roller body 1345a and the second roller body 1345b can be formed symmetrically about their opposing axial sides. For example, the first roller body 1345a can be formed with a first roller side groove 1346a1 forming part of the first blade groove 1346a, a first roller side chamber 1347a1 forming part of the first back pressure chamber 1347a, and a first roller side insertion groove 1348a1 forming part of the first spring insertion groove 1348a. The second roller body 1345b can be formed with a second roller side groove 1346a2 forming another part of the first blade groove 1346a, a second roller side chamber 1347a2 forming another part of the first back pressure chamber 1347a, and a second roller side insertion groove 1348a2 forming another part of the first spring insertion groove 1348a.

[0259] In this configuration, the first roller side groove 1346a1 and the second roller side groove 1346a2 can be symmetrical to each other on the same axis, the first roller side chamber 1347a1 and the second roller side chamber 1347a2 can be symmetrical to each other on the same axis, and the first roller side insertion groove 1348a1 and the second roller side insertion groove 1348a2 can be symmetrical to each other on the same axis. Therefore, if the first roller body 1345a and the second roller body 1345b are combined, then the first blade groove 1346a, the first back pressure chamber 1347a, and the first spring insertion groove 1348a can each form one. Of course, even in this configuration, the second blade groove 1346b and the third blade groove 1346c, the second back pressure chamber 1347b and the third back pressure chamber 1347c, and the second spring insertion groove 1348b and the third spring insertion groove 1348c can each form one.

[0260] The first blade groove 1346a and the first back pressure chamber 1347a are similar to the first blade groove 1346a in the aforementioned embodiment. For example, the first blade groove 1346a is formed to tilt at a predetermined angle relative to the radial direction, and the first back pressure chamber 1347a may be formed to communicate with the rear end of the first blade groove 1346a.

[0261] The first blade groove 1346a and the first back pressure chamber 1347a can be formed through the roller 134 axially. However, since the first spring insertion groove 1348a in the aforementioned embodiment is formed on one side of the roller 134 axially, the first back pressure chamber 1347a is eccentrically formed on the other side of the roller 134 axially where the first spring insertion groove 1348a is not formed. But in this embodiment, since the first spring insertion groove 1348a is formed at the middle height of the roller 134, the first back pressure chamber 1347a can be formed on both sides of the roller 134 axially.

[0262] The first spring insertion groove 1348a can be formed at the middle height of the roller 134, i.e., the middle height of the first back pressure chamber 1347a, as described above. For example, the first spring insertion groove 1348a can be composed of a first roller side insertion groove 1348a1 provided in the first roller body 1345a and a second roller side insertion groove 1348a2 provided in the second roller body 1345b.

[0263] The first roller-side insertion groove 1348a1 can be recessed axially to a predetermined depth from the lower surface of the first roller body 1345a toward the upper surface, and the second roller-side insertion groove 1348a2 can be recessed axially to a predetermined depth from the upper surface of the second roller body 1345b toward the lower surface. Therefore, the lower end of the first roller-side insertion groove 1348a1 and the upper end of the opposite second roller-side insertion groove 1348a2 are open, while a first roller-side stepped surface 1348a3 can be formed at the upper end of the opposite first roller-side insertion groove 1348a1, and a second roller-side stepped surface 1348a4 can be formed at the lower end of the opposite second roller-side insertion groove 1348a2. The first roller-side stepped surface 1348a3 and the second roller-side stepped surface 1348a4 can be formed to connect the aforementioned first roller-side chamber 1347a1 and second roller-side chamber 1347a2, respectively.

[0264] As described above, even when the roller body 1341 is composed of a separable first roller body 1345a and a second roller body 1345b and subsequently assembled, its effect is similar to that of the aforementioned embodiment. However, in this embodiment, since a first leaf spring 1342a is inserted between the first roller body 1345a and the second roller body 1345b disposed on both axial sides, the first leaf spring 1342a can be easily disposed in the axial middle of the roller 134.

[0265] Furthermore, in this embodiment, since the upper end of the first roller-side insertion groove 1348a1 and the lower end of the second roller-side insertion groove 1348a2 are respectively formed with stepped first roller-side stepped surfaces 1348a3 and second roller-side stepped surfaces 1348a4, the axial deformation of the first leaf spring 1342a inserted into the first spring insertion groove 1348a can be restricted. Therefore, it is not necessary to... Figure 13 The embodiments show that multiple cover components 1343a, 1343b, and 1343c can be assembled separately, so that even when the roller 134 is separated into multiple parts for assembly, the roller can be easily manufactured.

[0266] Furthermore, in this embodiment, as described above, since the first roller body 1345a and the second roller body 1345b are formed symmetrically along the axial direction when the first spring insertion groove 1348a is located in the middle of the roller 134, the center of gravity of the roller 134 can be located at the rotation center Or of the roller 134. Therefore, during compressor operation, vibration of the rotating body including the roller 134 is reduced, thereby reducing refrigerant leakage and improving compressor performance while reducing frictional losses or wear.

[0267] Another embodiment of the blade support structure of the present invention is as follows.

[0268] That is, in the aforementioned embodiment, the back pressure bag is disposed on both side bearings, but depending on the situation, the back pressure bag may also be excluded from the two side bearings. In this case, the inner circumferential surface of the cylinder can be formed as circular or non-circular (e.g., asymmetrical elliptical shape), but in this embodiment, a circular cylinder is used as an example for explanation.

[0269] Figure 19 It is shown Figure 18 A cross-sectional view of another embodiment of the blade support structure. Figure 20 It shows the basis Figure 18 A schematic diagram showing the relationship between the position of the blades and the blade spring. Figure 21a It shows through Figure 20 A schematic diagram of the support state of the blades in the first section. Figure 21b It shows through Figure 20 A schematic diagram of the support state of the blades in the second section.

[0270] Reference Figures 19 to 21b The compression section 130 in this embodiment is similar to the compression section 130 in the previous embodiment. For example, the compression section 130 includes a main bearing 131, a secondary bearing 132, a cylinder 133, a roller 134, and a plurality of blades 1351, 1352, and 1353. The roller 134 includes a roller body 1341 and a plurality of blade springs 1342a, 1342b, and 1342c. These main bearings 131, secondary bearings 132, cylinders 133, rollers 134, and blades 1351, 1352, and 1353 are similar to those in the previous embodiment. In addition, the overall structure and function of the roller body 1341 and the blade springs 1342a, 1342b, and 1342c constituting the roller 134 can be similar to those in the previous embodiment, and this is also true for the blades 1351, 1352, and 1353. In this regard, the first blade 1351 and its related parts will be described as an example below.

[0271] However, in the roller body 1341 of this embodiment, the groove direction length (which is the same as the groove direction spacing between the spring fixing surfaces) L22' of the first spring insertion groove 1348a and the free state length of the first leaf spring 1342a based thereon can be made longer than in the aforementioned embodiment.

[0272] In other words, in the aforementioned embodiment, the rear end of the first blade 1351, more precisely, the first spring support 1351c, is hidden in the first blade groove 1346a in the first interval α1 of the cylinder 133 and will not be exposed to the first spring insertion groove 1348a. Therefore, in the first interval α1, the first blade 1351 is separated from the first blade spring 1342a.

[0273] However, in this embodiment, the groove direction length L22' of the first spring insertion groove 1348a and the free state length of the first leaf spring 1342a can be extended so that the first leaf 1351 can be exposed in the first spring insertion groove 1348a throughout the entire range of the cylinder 133 including the first range α1.

[0274] In other words, even when the first blade 1351 passes through the section (i.e., the first section) α1 where it protrudes the most from the first blade groove 1346a of the roller 134, the first spring support portion 1351c of the first blade 1351 remains inside the first spring insertion groove 1348a. Therefore, even in the first section α1, the second end 1342a2 of the first blade spring 1342a can contact the rear end of the first blade 1351, i.e., the second support surface 1351c2 of the first spring support portion 1351c. Thus, the first blade 1351 can be elastically supported by the first blade spring 1342a throughout the entire section of the cylinder 133.

[0275] As described above, when the first blade 1351 is elastically supported by the first blade spring 1342a throughout the entire range of the cylinder 133, it is not necessary to provide back pressure to the first blade 1351, or its necessity can be reduced. Therefore, in this embodiment, the main bearing 131 and the secondary bearing 132 may not form or may have their respective back pressure pockets reduced. In other words, the main sliding surface 1311a of the main bearing 131 and the secondary sliding surface 1321a of the secondary bearing 132 may be formed flat, respectively.

[0276] This simplifies the machining of the main bearing 131 and the auxiliary bearing 132, reducing manufacturing costs. Furthermore, by removing or reducing the back pressure bag and back pressure chamber in the main bearing 131 and the auxiliary bearing 132, pressure pulsations that may occur in the back pressure bag and back pressure chamber are eliminated or reduced, thereby stabilizing blade movement.

[0277] Furthermore, as mentioned earlier, when the groove length L22' of the first spring insertion groove 1348a is extended, it is necessary to ensure a minimum sealing distance between the first spring insertion groove 1348a and the outer peripheral surface of the roller 134. If the groove end of the first spring insertion groove 1348a, i.e., the second spring fixing surface 1349b, is excessively close to the outer peripheral surface of the roller 134, the sealing distance becomes shorter, thereby allowing leakage to occur between the compression chambers of the first spring insertion groove 1348a.

[0278] Taking this into consideration, such as Figure 20 As shown, it may be more advantageous for the inner circumferential surface 1332 of the cylinder 133 to be circular than non-circular. That is, the inner circumferential surface 1332 of the cylinder 133 in this embodiment can be formed as a circle or as a non-circular shape such as an asymmetrical ellipse.

[0279] However, refer to Figure 21a and Figure 21b When the inner circumferential surface 1332 of the cylinder 133 is circular (hereinafter referred to as the circular case), the maximum distance between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1341b of the roller 134 is shorter compared to the case where the inner circumferential surface 1332 of the cylinder 133 is non-circular (hereinafter referred to as the non-circular case). Therefore, when the inner circumferential surface 1332 of the cylinder 133 is circular, the groove direction length L22' of the spring insertion grooves 1348a, 1348b, and 1348c is relatively shorter than in the non-circular case. Simultaneously, the blade springs 1342a, 1342b, and 1342c embedded in the roller 134 can elastically support the blades 1351, 1352, and 1353 throughout the entire range of the cylinder 133. Therefore, when the inner circumferential surface 1332 of the cylinder 133 is circular, the aforementioned sealing distance L3' can be easily ensured compared to the non-circular case.

[0280] In other words, regardless of whether the inner circumferential surface 1332 of the cylinder 133 is circular or non-circular, the blades 1351, 1352, and 1353 can be supported without forming their respective back pressure pockets in the main bearing 131 and the secondary bearing 132. However, the circular case with a relatively small protrusion rate of the blades 1351, 1352, and 1353 may be more advantageous for application in this embodiment.

[0281] Furthermore, the rotary vane compressor of this embodiment may be more effective when using high-pressure refrigerants such as R32, R410a, and CO2. For example, when using a high-pressure refrigerant, compared to using a medium- or low-pressure refrigerant such as R134a, the pressure difference between the compression surfaces and compression back surfaces of each vane 1351, 1352, and 1353 is greater between the contact point P and the suction port 1331. Therefore, although the vibration of the vanes 1351, 1352, and 1353 between the contact point P and the suction port 1331 may increase when using a high-pressure refrigerant, as shown in this embodiment, by increasing the pressure on the vanes in the corresponding range, the vibration of the vanes 1351, 1352, and 1353 can be effectively suppressed. This suppresses leakage between the compression chambers and reduces noise and wear caused by vane vibration.

[0282] Additionally, although not shown in the figures, leaf springs 1342a, 1342b, and 1342c can also be used in addition to the aforementioned compression coil springs. For example, leaf springs 1342a, 1342b, and 1342c are formed with a V-shaped cross-section, allowing them to be inserted into the inner circumferential surfaces of back pressure chambers 1347a, 1347b, and 1347c. In this case, slit-shaped bearing insertion grooves 1348a, 1348b, and 1348c are formed on the inner circumferential surfaces of each back pressure chamber 1347a, 1347b, and 1347c, respectively. The two ends of the V-shaped leaf springs 1342a, 1342b, and 1342c are inserted into and fixed in the width direction of their respective bearing insertion grooves 1348a, 1348b, and 1348c. However, as described above, when the leaf springs are made of leaf springs, it is not only difficult to insert and fix the small and thin leaf springs 1342a, 1342b, and 1342c at both ends in the width direction within the narrow bearing insertion slots 1348a, 1348b, and 1348c, but even if the respective leaf springs 1342a, 1342b, and 1342c are installed between the leaf springs 1351, 1352, and 1353 and the back pressure chambers 1347a, 1347b, and 1347c, the width of the leaf springs 1342a, 1342b, and 1342c is relatively small, and therefore the elastic force that can be obtained may not be large. Therefore, compared with leaf springs, a greater effect can be obtained when the leaf springs 1351, 1352, and 1353 are used as compression coil springs as shown in the aforementioned embodiments.

[0283] Although not shown in the figure, the discharge port may not be formed on the main bearing and the secondary bearing, but on the cylinder. Even in this case, the aforementioned blade support structure using a compression helical spring can still be applied.

Claims

1. A rotary compressor, wherein, include: case; The cylinder is fixed inside the housing to form a compression space; The main bearing and the auxiliary bearing are respectively located on both sides of the cylinder barrel along its axial direction; A rotating shaft passes through the cylinder to be supported by the main bearing and the auxiliary bearing; A roller is disposed on the rotating shaft, the outer peripheral surface of the roller being eccentrically arranged relative to the inner peripheral surface of the cylinder, and the roller having at least one blade groove opening toward the outer peripheral surface. as well as Blades are slidably inserted into the blade slots, with the leading edge of the blades contacting the inner circumferential surface of the cylinder to divide the compression space into a plurality of compression chambers. The rollers include: The roller body has a spring insertion groove formed at the inner end of the blade groove in the groove direction; and A leaf spring is inserted into the spring insertion slot to support the rear face of the leaf blade toward the inner circumferential surface of the cylinder. The leaf spring contacts the leaf in a second interval and is separated from the leaf in a first interval outside the second interval. The second interval includes the contact point where the outer circumferential surface of the roller contacts the inner circumferential surface of the cylinder. At least a portion of the spring insertion slot is formed to overlap the blade slot axially. The blade has a spring support portion formed at the position where it overlaps with the spring insertion slot. The spring support portion includes: A first support surface extends toward the forward side of the blade; and A second support surface extends from the first support surface along the axial side of the blade to support the end of the blade spring in the groove direction. The groove length of the first support surface is less than half the groove length of the blade.

2. The rotary compressor according to claim 1, wherein, The leaf spring is configured as a compression helical spring.

3. The rotary compressor according to claim 2, wherein, The spring insertion slot includes a first spring fixing surface and a second spring fixing surface that are spaced apart from each other at a predetermined interval along the groove direction of the blade groove. In the first interval, the two ends of the leaf spring are supported by the first spring fixing surface and the second spring fixing surface, respectively.

4. The rotary compressor according to claim 1, wherein, The sealing distance between the spring insertion groove and the outer peripheral surface of the roller body is greater than or equal to half the lateral width of the blade groove.

5. The rotary compressor according to claim 1, wherein, The spring support portion is formed in a stepped shape at a predetermined depth from one side of the axial direction connected to the rear side of the blade toward the other side of the axial direction.

6. The rotary compressor according to claim 5, wherein, The main bearing or the secondary bearing has an outlet for discharging refrigerant from the compression chamber into the interior space of the housing. The spring support is formed on the axial side facing the bearing on which the discharge port is formed.

7. The rotary compressor according to claim 1, wherein, The spring support is formed to be recessed to a predetermined depth from the axial middle of the rear side of the blade toward the front side of the blade.

8. The rotary compressor according to claim 1, wherein, The axial depth of the second support surface is greater than or equal to the axial depth of the spring insertion groove.

9. The rotary compressor according to claim 1, wherein, The roller body is formed as a single unit. The spring insertion groove is formed by recessing from one side of the roller body along the axial direction toward the other side of the axial direction to a predetermined depth.

10. The rotary compressor according to claim 9, wherein, The lateral width of the spring insertion slot is greater than the lateral width of the blade slot. The outer diameter of the blade spring is formed to be larger than the lateral width of the blade groove.

11. The rotary compressor according to claim 9, wherein, The axial depth of the spring insertion groove is greater than the outer diameter of the blade spring, and is less than or equal to 1 / 2 of the axial height of the roller body.

12. The rotary compressor according to claim 9, wherein, The axial depth of the spring insertion groove is greater than the outer diameter of the blade spring, and is greater than 1 / 2 of the axial height of the roller body. The blade spring is positioned at the axial midpoint of the roller body.

13. The rotary compressor according to claim 9, wherein, A cover member covering at least a portion of the spring insertion groove is also provided on one axial side of the spring insertion groove.

14. The rotary compressor according to claim 13, wherein, The inner circumferential surface of the spring insertion slot and the outer circumferential surface of the cover member are spaced apart by at least a portion to form an oil passage.

15. The rotary compressor according to claim 1, wherein, The roller body includes: The first roller body forms one side axially; and The second roller body forms the other side of the axial direction and is attached to one side of the first roller body. The spring insertion slot is disposed between the first roller body and the second roller body.

16. The rotary compressor according to claim 1, wherein, The blade groove is formed to be inclined at a predetermined angle relative to the radial direction of the roller.

17. The rotary compressor according to claim 1, wherein, The blade groove is formed along the radial direction of the roller.

18. The rotary compressor according to claim 1, wherein, At least one of the sliding surfaces of the main bearing facing the roller on one axial side and the sliding surfaces of the secondary bearing facing the roller on the other axial side is circumferentially spaced apart by a plurality of back pressure bags having different pressures from each other. The plurality of back pressure bags are formed to overlap the spring insertion slots axially.

19. The rotary compressor according to claim 1, wherein, In the sliding surface of the main bearing facing one axial side of the roller and the sliding surface of the secondary bearing facing the other axial side of the roller, The sliding surfaces of the main bearing and the secondary bearing, which overlap axially with the spring insertion groove, are formed in a flat manner.

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