Rotary compressor

Abstract

A rotary compressor according to the present embodiment includes: a main bearing and a sub bearing, which are respectively provided at both axial sides of a cylinder and are respectively provided with guide grooves; a roller, which is accommodated in the cylinder and rotates together with a rotating shaft; at least one vane, which is slidably inserted into the roller; a guide protrusion of the vane, which is slidably inserted into the guide groove in a circumferential direction and extends in an axial direction; and a bearing member, which is provided between the guide groove of at least any one of the main bearing and the sub bearing and the guide protrusion of the vane, whereby compressor efficiency can be improved by reducing friction loss between the vane or the roller and the main bearing or the sub bearing facing the same.

Description

Technical Field

[0001] This invention relates to a vane rotary compressor in which vanes are coupled to rotating rollers. Background Technology

[0002] Rotary compressors can be divided into two types: those in which the vanes can be slidably inserted into the cylinder and in contact with the rollers, and those in which the vanes can be slidably inserted into the rollers and in contact with the cylinder. Generally, the former is called a roller eccentric rotary compressor (hereinafter referred to as a rotary compressor), and the latter is called a vane concentric rotary compressor (hereinafter referred to as a 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 and come into contact with 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 and come into contact with the inner circumferential surface of the cylinders.

[0004] In a rotary compressor, a number of compression chambers, equivalent to the number of blades, are formed independently with each rotation of the rollers, and each chamber simultaneously performs the suction, compression, and discharge strokes. Conversely, in a rotary vane compressor, a number of compression chambers, equivalent to the number of blades, are formed continuously with each rotation of the rollers, and each chamber sequentially performs the suction, compression, and discharge strokes. Therefore, rotary vane compressors achieve a higher compression ratio than rotary compressors. Consequently, rotary vane compressors are more suitable for high-pressure refrigerants with lower ozone depletion potential (ODP) and global warming potential (GWP) values, such as R32, R410a, and CO2.

[0005] Typically, because the multiple blades of this type of rotary compressor rotate together with the rollers and slide while the sealing surface of the blade is in contact with the inner circumferential surface of the cylinder, the friction loss is increased compared to that of a conventional rotary compressor.

[0006] Patent Document 1 (US Patent Publication: US2015-0064042A1) discloses a rotary vane compressor. The rotary vane compressor disclosed in Patent Document 1 is a low-pressure type in which the internal space of the motor chamber is filled with suction refrigerant, and discloses the feature of a rotary vane compressor with a structure in which a plurality of vanes are slidably inserted into rotating rollers.

[0007] In the rotary vane compressor disclosed in Patent Document 1, the inner circumferential surface of the cylinder constituting the compression space is composed of a plurality of curves. For example, the inner circumferential surface of the cylinder disclosed in Patent Document 1 can be formed as an asymmetrical ellipse with respect to the axis of rotation. Thus, the inner circumferential surface of the cylinder is provided with a proximal portion closest to the axis and a remote portion furthest from the axis, and the proximal portion and the remote portion are connected by curved surfaces having different aspect ratios.

[0008] On the other hand, the roller is formed from a perfect circle with a constant outer circumferential curvature and is arranged to be concentric with respect to the axis of rotation. A plurality of blade grooves of a predetermined depth are formed at equal intervals along the outer circumferential surface of the roller.

[0009] In the rotary vane compressor described above, the inner circumferential surface of the cylinder and the front end of the vane (i.e., the sealing surface) can move relative to each other by always being in contact or by being separated by an oil film, thereby increasing the mechanical friction loss between the cylinder and the vane.

[0010] In response, Patent Document 2 (Korean Patent Publication No. 10-2011-0095155) discloses a structure that suppresses mechanical friction loss between the blade and the cylinder by restricting the radial movement of the blade. Specifically, in Patent Document 2, a ring is provided in the main bearing or secondary bearing, and a pin is provided in the blade that slides circumferentially along the ring. Thus, the blade only rotates with the rollers, and its radial movement towards the cylinder is restricted. Therefore, the blade can remain in its original position relative to the cylinder, thereby suppressing friction between the cylinder and the blade.

[0011] In the rotary vane compressor described above, since the vane position is determined by the ring, if there are large machining or assembly errors, the vanes and cylinder may be excessively close together, or conversely, excessively spaced. Furthermore, frictional losses will still occur between the axial sides of the rollers and the axial sides of the bearings facing them.

[0012] To address this, Patent Document 3 (Japanese Patent Publication No. 2012-167578) discloses a structure in which the leading end (sealing surface) of the blade does not contact the cylinder but can move radially. Specifically, Patent Document 3 provides a circular blade guide groove eccentric to the bearing, and a semi-circular blade guide is used in this groove and rotates along it. Thus, the blade can move radially relative to the inner circumferential surface of the cylinder, or it can remain in a non-contact state with the inner circumferential surface of the cylinder. Therefore, mechanical friction losses between the cylinder and the blade can be reduced by shortening the contact area between them.

[0013] However, in the existing rotary vane compressors described above, mechanical friction loss occurs between the vane guide and the vane guide groove because the vane guide slides along the inner circumferential surface of the vane guide groove.

[0014] In addition, in existing rotary vane compressors, mechanical friction losses also occur between the axial side of the roller and the axial side of the main or secondary bearing facing it. Summary of the Invention

[0015] The problem that the invention aims to solve

[0016] The purpose of this invention is to provide a rotary compressor that can reduce mechanical friction losses caused by blade rotation.

[0017] Furthermore, the present invention aims to provide a rotary compressor that limits the blade extension by utilizing a main bearing and / or a secondary bearing, thereby reducing mechanical friction losses between the main bearing and / or the secondary bearing and the blade.

[0018] Furthermore, the present invention aims to provide a rotary compressor in which a bearing member is provided between the main bearing, the auxiliary bearing, and the blades, thereby reducing mechanical friction loss between the main bearing and / or the auxiliary bearing and the blades.

[0019] Another object of the present invention is to provide a rotary compressor capable of reducing mechanical friction loss caused by the rotation of rollers.

[0020] Furthermore, the object of the present invention is to provide a rotary compressor capable of reducing mechanical friction loss between the main bearing and / or the secondary bearing and the rollers facing the main bearing and / or the secondary bearing.

[0021] Furthermore, the object of the present invention is to provide a rotary compressor in which a bearing member is provided between the main bearing and / or the auxiliary bearing and the roller, thereby reducing mechanical friction loss between the main bearing and / or the auxiliary bearing and the roller.

[0022] Technical solutions to the problem

[0023] To achieve the objectives of this invention, a rotary compressor is provided in which at least one of the main bearing and the secondary bearing has a guide groove formed on the axial side facing the roller. A guide protrusion extends axially at the axial end of the blade facing the guide groove, the guide protrusion having a contact surface for insertion into the guide groove and sliding along its inner circumferential surface. A bearing member is disposed between the inner circumferential surface of the guide groove and the contact surface of the guide protrusion facing the inner circumferential surface of the guide groove. This reduces radial mechanical friction losses between the blade and the main or secondary bearing supporting the blade.

[0024] Furthermore, to achieve the objectives of this invention, guide grooves can be formed in the main bearing and the secondary bearing supporting the rotating shaft, and guide protrusions can be formed in the blade slidably inserted into the roller. These guide protrusions are slidably inserted into the guide grooves and radially restricted. A ball bearing is disposed between the guide grooves and the guide protrusions. This allows for easy installation of bearing components between the blade and the main or secondary bearing supporting the blade.

[0025] As an example, the inner wheel constituting the ball bearing may also be provided with a rotating plate extending between the main bearing and the roller, and between the secondary bearing and the roller. This reduces axial mechanical friction losses between the roller and the main or secondary bearing facing the roller.

[0026] As another example, the rotating plate can be rotatably inserted into the inner circumferential surface of the cylinder. This allows for a more effective reduction of axial mechanical friction losses between the rollers and the main or secondary bearings facing the rollers.

[0027] Furthermore, to achieve the objectives of this invention, a rotary compressor can be provided in which guide grooves are formed in the main bearing and the secondary bearing supporting the rotating shaft, and guide protrusions are formed in the blades slidably inserted into the rollers. The guide protrusions are slidably inserted into the guide grooves and radially restricted. A first bearing portion is provided between the guide grooves and the guide protrusions, and a second bearing portion is provided between the main bearing and the rollers and / or between the secondary bearing and the rollers. The first bearing portion and the second bearing portion are integrally formed. This reduces radial friction loss between the blades and the main or secondary bearings, as well as axial friction loss between the rollers and the main or secondary bearings.

[0028] As an example, the first bearing portion and the second bearing portion can be formed as a single unit. This allows for the easy manufacture of bearing components capable of reducing radial and axial frictional losses.

[0029] As another example, the outer peripheral surface of the second bearing portion can be configured to face the inner peripheral surface of the cylinder, and a sealing portion is formed on the outer peripheral surface of the second bearing portion. Thus, the second bearing portion can rotate within the cylinder and effectively suppress refrigerant leakage in the compression space.

[0030] Furthermore, to achieve the objectives of this invention, the inner circumferential surface of the cylinder can be formed as an annular shape. A main bearing and a secondary bearing, respectively disposed on opposite axial sides of the cylinder, can form a compression space together with the cylinder, and a guide groove is provided on the side forming the compression space. A roller housed in the cylinder can be configured to rotate together with a rotating shaft. A guide protrusion of at least one blade slidably inserted into the roller can extend axially, and the guide protrusion is slidably inserted into the guide groove in the circumferential direction. A bearing member can be provided between the guide groove of at least one of the main bearings and the secondary bearing and the guide protrusion of the blade. Thus, compressor efficiency can be improved by reducing frictional losses between the blade and the main or secondary bearing supporting the blade.

[0031] Specifically, the bearing component may include: an outer wheel inserted into the inner circumferential surface of the guide groove; an inner wheel disposed inside the outer wheel, the inner circumferential surface of which slidably contacts the contact surface of the guide protrusion; and a sliding member disposed between the outer wheel and the inner wheel, allowing the outer wheel and the inner wheel to move relative to each other. This allows for more effective reduction of mechanical friction loss between the blade and the main or secondary bearing supporting the blade, while also facilitating easy installation of the bearing component.

[0032] As an example, either the outer wheel or the inner wheel may also be provided with a rotating plate extending between the roller and the main bearing and the secondary bearing facing the roller. This allows for a more effective reduction in axial mechanical friction losses between the roller and the main or secondary bearing facing the roller.

[0033] As an example, the bearing component may include: a first bearing portion disposed between at least one of the main bearing and the secondary bearing and a blade radially facing the at least one of the bearings; and a second bearing portion disposed between at least one of the main bearing and the secondary bearing and a roller axially facing the at least one of the bearings. This reduces radial friction loss between the blade and the main or secondary bearing, as well as axial friction loss between the roller and the main or secondary bearing.

[0034] As another example, the first bearing portion and the second bearing portion can be formed as a single unit. This allows for the easy manufacture of bearing components capable of reducing radial and axial friction losses.

[0035] As another example, the second bearing portion can be formed to be thicker than the first bearing portion. This allows for easy formation of a sealing portion on the outer circumferential surface of the second bearing portion while ensuring the sealing area between the cylinder and the bearing component.

[0036] As another example, the first bearing portion can be formed in a ring shape, and the second bearing portion can be formed in a circular plate shape.

[0037] As another example, the first bearing portion may include: an outer wheel inserted into a guide groove of at least one of the main bearing and the secondary bearing; an inner wheel disposed inside the outer wheel, its inner circumferential surface slidably contacting the guide protrusion of the blade; and a sliding member disposed between the outer wheel and the inner wheel, allowing the outer wheel and the inner wheel to move relative to each other. The second bearing portion may extend radially from one end of the inner wheel of the first bearing portion or one end of the outer wheel of the first bearing portion and be disposed between the axial side of the roller and the axial sides of the main bearing and the secondary bearing facing the axial side of the roller. This reduces radial friction loss between the blade and the main bearing or secondary bearing, as well as axial friction loss between the roller and the main bearing or secondary bearing.

[0038] As another example, the axial side of the second bearing portion can be separated from the axial side of the main bearing or the auxiliary bearing facing the axial side of the second bearing portion. This allows for effective reduction of frictional losses by suppressing contact between the second bearing portion and the main bearing or auxiliary bearing.

[0039] As another example, the second bearing portion can be inserted into the cylinder barrel with its outer circumferential surface facing the inner circumferential surface of the cylinder barrel. This allows for effective reduction of refrigerant leakage in the compression chamber by forming a sealing surface between the second bearing portion and the inner circumferential surface of the cylinder barrel.

[0040] As another example, a sealing portion can be provided between the outer peripheral surface of the second bearing portion and the inner peripheral surface of the cylinder barrel. This allows the second bearing portion to be separated from the cylinder barrel and also more effectively suppresses refrigerant leakage in the compression space.

[0041] As another example, the outer peripheral surface of the second bearing portion can be formed with the same shape as the inner peripheral surface of the cylinder. This allows for the suppression of relative movement between the roller and the second bearing portion by rotating the second bearing portion inside the cylinder.

[0042] As an example, the bearing member can be disposed between at least one of the main bearing and the secondary bearing and the blade radially facing the at least one of the bearings. The axial side of the roller can slidably contact the axial side of the main bearing and the axial side of the secondary bearing facing the axial side of the roller. This suppresses mechanical friction loss between the second bearing portion and the roller.

[0043] As another example, the inner circumferential surface of the cylinder can be formed into a circular or elliptical shape. An outlet can be formed on at least one of the axial side surfaces of the main bearing and the secondary bearing. Thus, overcompression can be suppressed by forming the inner circumferential surface of the cylinder in a variety of shapes and by creating a longer compression cycle.

[0044] As an example, bushing grooves can be formed in the rollers, into which a pair of rocker bushings can be rotatably inserted, and the blades can be slidably inserted between the rocker bushings. Thus, the sealing area between the cylinder and the blades can be ensured by forming the leading edge of the blade with the same curvature as the inner circumferential surface of the cylinder.

[0045] Invention Effects

[0046] In this embodiment, the rotary compressor can have a bearing member disposed between the guide grooves provided in the main bearing and the auxiliary bearing and the guide protrusions of the blades facing the guide grooves of the main bearing and the auxiliary bearing. This allows for improved compressor efficiency by reducing frictional losses between the blades and the main or auxiliary bearings supporting the blades.

[0047] Furthermore, in this embodiment, the rotary compressor can have a ball bearing, consisting of an outer wheel, an inner wheel, and a sliding member, installed between the inner circumferential surface of the guide groove and the guide protrusion facing the inner circumferential surface of the guide groove. This allows for more effective reduction of mechanical friction losses between the blades and the main or secondary bearing supporting the blades, while also facilitating the installation of the bearing components.

[0048] Furthermore, in this embodiment, either the outer or inner wheel of the ball bearing constituting the rotary compressor may be provided with a rotating plate extending between the main bearing and the counter-bearing bearing facing the roller. This allows for a more effective reduction of axial mechanical friction losses between the roller and the main or counter-bearing bearing facing the roller.

[0049] Furthermore, the rotary compressor of this embodiment may include: a first bearing portion disposed between the main bearing and the auxiliary bearing and blades radially facing the main bearing and the auxiliary bearing; and a second bearing portion disposed between the main bearing and the auxiliary bearing and rollers axially facing the main bearing and the auxiliary bearing. This reduces radial friction loss between the blades and the main bearing or auxiliary bearing, as well as axial friction loss between the rollers and the main bearing or auxiliary bearing.

[0050] Furthermore, the first bearing portion and the second bearing portion of the rotary compressor in this embodiment can be formed as a single unit. This allows for the easy manufacture of bearing components capable of reducing radial and axial frictional losses.

[0051] Furthermore, in this embodiment, the second bearing portion of the rotary compressor can be formed to be thicker than the first bearing portion. This ensures a sufficient sealing area between the cylinder and the bearing components while also allowing for easy formation of a sealing portion on the outer circumferential surface of the second bearing portion.

[0052] Furthermore, in this embodiment, the axial side of the second bearing portion of the rotary compressor can be separated from the axial side of the main bearing or auxiliary bearing facing the axial side of the second bearing portion. This allows for effective reduction of frictional losses by suppressing contact between the second bearing portion and the main bearing or auxiliary bearing.

[0053] Furthermore, in this embodiment, the second bearing portion of the rotary compressor can be inserted into the cylinder barrel with its outer peripheral surface facing the inner peripheral surface of the cylinder barrel. This allows for effective reduction of refrigerant leakage in the compression chamber by forming a sealing surface between the second bearing portion and the inner peripheral surface of the cylinder barrel.

[0054] Furthermore, in this embodiment, a sealing portion can be formed between the outer peripheral surface of the second bearing section and the inner peripheral surface of the cylinder barrel in the rotary compressor. This allows the second bearing section to be separated from the cylinder barrel and more effectively suppresses refrigerant leakage in the compression chamber.

[0055] Furthermore, the inner circumferential surface of the cylinder of the rotary compressor in this embodiment can be formed as a circle or an ellipse, and an outlet is formed on at least one of the axial side of the main bearing and the axial side of the secondary bearing. This allows for diverse shapes of the inner circumferential surface of the cylinder and enables a longer compression cycle to suppress overcompression.

[0056] Furthermore, in this embodiment, the rotary compressor may have bushing grooves formed on the rollers, into which a pair of rocker bushings are rotatably inserted, and blades are slidably inserted between the rocker bushings. This allows for ensuring a sufficient sealing area between the cylinder and the blades by forming the leading edge of the blades with the same curvature as the inner circumferential surface of the cylinder. Attached Figure Description

[0057] Figure 1 This is a longitudinally sectional view showing an example of the rotary blade compressor of the present invention.

[0058] Figure 2 It is to decompose and show Figure 1 A three-dimensional view of the compression section in the middle.

[0059] Figure 3 It is assembled and shown Figure 2 A three-dimensional view of the compression section.

[0060] Figure 4 yes Figure 3 Top view,

[0061] Figure 5 It is shown in magnification Figure 1 A cross-sectional view of the compression section in the middle.

[0062] Figure 6 It is cut open and shown Figure 5 A three-dimensional diagram of the blade bearing in the image.

[0063] Figure 7 It is shown Figure 6 A cross-sectional view of the blade bearing installed in the main bearing.

[0064] Figure 8 and Figure 9 It is shown Figure 5 A cross-sectional view of another embodiment of the sealing portion of the blade bearing.

[0065] Figure 10 This is a cross-sectional view showing another embodiment of the blade bearing.

[0066] Figure 11 This is a cross-sectional view showing yet another embodiment of the blade bearing. Detailed Implementation

[0067] The rotary vane compressor of the present invention will now be described in detail with reference to an embodiment shown in the accompanying drawings. For reference, the vane grooves of the rollers of the present invention can also be applied to rotary vane compressors in which vanes are slidably inserted into the rollers. For example, as in this embodiment, it can be applied not only to examples of radially formed vane grooves but also to examples of obliquely formed vane grooves.

[0068] Figure 1 This is a longitudinally sectional view showing an example of the rotary blade compressor of the present invention. Figure 2 It is to decompose and show Figure 1 A three-dimensional view of the compression section in the middle. Figure 3 It is assembled and shown Figure 2 A three-dimensional view of the compression section. Figure 4 yes Figure 3 Top view.

[0069] 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.

[0070] The housing 110 is the part that constitutes the exterior of the compressor, and it can be divided into vertical or horizontal types depending on the installation configuration of the compressor. A vertical housing has the drive motor 120 and the compressor unit 130 arranged axially on the upper and lower sides, while a horizontal housing has the drive motor 120 and the compressor unit 130 arranged on the left and right sides. In this embodiment, the housing can be formed as a vertical housing.

[0071] The housing 110 includes: an intermediate outer shell 111, which is formed in a cylindrical shape; a lower outer shell 112, which covers the lower end of the intermediate outer shell 111; and an upper outer shell 113, which covers the upper end of the intermediate outer shell 111. The drive motor 120 and the compression unit 130 can be inserted into and fixedly connected to the intermediate outer shell 111, and the suction pipe 115 passes through the intermediate outer shell 111 and is directly connected to the compression unit 130.

[0072] The lower outer casing 112 can be sealed to the lower end of the intermediate outer casing 111, and an oil storage space 110b for storing oil supplied to the compression section 130 can be formed on the lower side of the compression section 130. The upper outer casing 113 can be sealed to the upper end of the intermediate outer casing 111, and 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 compression section 130.

[0073] The drive motor 120 is part of the electric motor unit, which provides power for driving the compression unit 130. The drive motor 120 includes a stator 121, a rotor 122, and a rotating shaft 123.

[0074] The stator 121 is fixedly disposed inside the housing 110 and can be pressed into and fixed to the inner circumferential surface of the cylindrical housing 110 by means of thermoforming or other methods. For example, the stator 121 can be pressed into and fixed to the inner circumferential surface of the intermediate outer shell 111.

[0075] The rotor 122 is rotatably inserted into the stator 121, and the rotating shaft 123 is pressed into the center of the rotor 122. Thus, the rotating shaft 123 and the rotor 122 rotate concentrically together.

[0076] A hollow oil supply passage 125 can be formed at the center of the rotating shaft 123, and oil through holes 126a and 126b can be formed in the middle of the oil supply passage 125, extending through 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 bearing portion 1312 (described later) and a second oil through hole 126b belonging to the second bearing portion 1322. One or more of the first oil through hole 126a and the second oil through hole 126b can be formed. This embodiment shows an example where multiple holes are formed.

[0077] An oil suction device 127 can be installed in the middle or at the lower end of the oil supply passage 125. The oil suction device 127 can be a gear pump, a viscous pump, a centrifugal pump, etc. This embodiment shows an example using a centrifugal pump. Thus, if the rotating shaft 123 rotates, the oil filling the oil storage space 110b of the housing 110 can be pumped through the oil suction device 127. This oil is drawn upwards along the oil supply passage 125 and supplied to the secondary bearing surface 1322a of the secondary bearing section 1322 through the second oil through-hole 126b, and to the main bearing surface 1312a of the main bearing section 1312 through the first oil through-hole 126a. This will be explained later.

[0078] 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 and together with the cylinder 133 form a compression space V. The rollers 134 are rotatably mounted in the compression space V. The blades 1351, 1352, and 1353 are slidably inserted into the rollers 134 and divide the compression space V into a plurality of compression chambers.

[0079] Reference Figure 1 and Figure 2 The main bearing 131 can be fixedly mounted to the intermediate housing 111 of the housing 110. For example, the main bearing 131 can be inserted into and welded to the intermediate housing 111.

[0080] The main bearing 131 can be closely attached to and engaged with the upper end of the cylinder 133. Thus, the main bearing 131 forms the upper side of the compression space V, axially supporting the top surface of the roller 134 while radially supporting the upper half of the rotating shaft 123.

[0081] The main bearing 131 may include a main plate portion 1311 and a main bearing portion 1312. The main plate portion 1311 covers the upper side of the cylinder 133 and is connected to the cylinder 133. The main bearing 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.

[0082] The main board portion 1311 can be formed in the shape of a circular plate, and the outer peripheral surface of the main board portion 1311 is closely attached to and fixed to the inner peripheral surface of the intermediate housing 111. The bottom surface of the main board portion 1311, that is, the axial bottom surface facing the axial top surface of the roller 134, has a main guide groove 1311a to accommodate the guide protrusion 1351d described later.

[0083] The main guide groove 1311a can accommodate the main bearing bore 1312a, which will be described later, and is eccentrically formed relative to the bearing bore center (axis center or roller rotation center) (not shown) constituting the center of the main bearing bore 1312a. For example, the center Og of the inner circumferential surface 1311a1 constituting the main guide groove 1311a and the center Ov of the compression space V constituting the inner circumferential surface 1331 of the cylinder 133 can be formed to be located on the same axis. Thus, the center Og of the main guide groove 1311a and the center Ov of the compression space V can be eccentrically formed relative to the rotation center Or of the roller 134.

[0084] In other words, as in this embodiment, when the blade bearings 136 and 137, described later, rotate together with the first bearing portion 1365 and the second bearing portion 1366, as described above, the center Og of the main guide groove 1311a and the center Ov of the compression space V are formed to be located on the same axis and are eccentrically formed relative to the rotation center Or of the roller 134.

[0085] However, if the second bearing section 1366 is excluded or the second bearing section 1366 is fixed, the center Og of the main guide groove 1311a and the center Ov of the compression space V can also be formed eccentrically to each other.

[0086] The main guide groove 1311a can be formed to a nearly uniform depth and communicate with the oil supply passage 125 provided on the rotating shaft 123. For example, as the main guide groove 1311a is formed in a stepped shape at the inner circumferential corner of the main plate portion 1311 or the lower corner of the main bearing 1312, the main guide groove 1311a can be formed at a position that directly communicates radially with the first oil through hole 126a of the rotating shaft 123 or is formed to communicate through the main bearing surface 1312a1 that constitutes the inner circumferential surface of the main bearing hole 1312a. Thus, discharge pressure or corresponding oil flows into the interior of the main guide groove 1311a.

[0087] The inner circumferential surface of the main guide groove 1311a can be formed at a position that does not communicate with the compression space V. For example, the inner circumferential surface 1311a1 of the main guide groove 1311a can be formed between the main bearing surface 1312a1, which forms the inner circumferential surface of the main bearing bore 1312a, and the outer circumferential surface 1341 of the roller 134. This ensures a sealing distance between the main bearing 131 and the roller 134, preventing the flow of discharge pressure or corresponding oil into the compression space V even if it flows into the interior of the main guide groove 1311a.

[0088] The inner circumferential surface 1311a1 of the main guide groove 1311a can be formed with the same shape as the outer circumferential surface 1341 of the roller 134 described later. For example, the inner circumferential surface 1311a1 of the main guide groove 1311a can be formed as a circle with the same shape as the outer circumferential surface 1341 of the roller 134 described later. Thus, the sealing surface (or sealing distance) between the main guide groove 1311a and the outer circumferential surface of the roller can be formed uniformly along the circumferential direction.

[0089] The main bearing bore 1312a of the main bearing section 1312 can penetrate along the axial direction and be formed into a hollow bushing shape. An oil groove (not shown) is formed on the main bearing surface 1312a1, which is the inner circumferential surface of the main bearing bore 1312a.

[0090] Reference Figure 1 and Figure 2 The secondary bearing 132 can be closely attached to and engaged with the lower end of the cylinder 133. Thus, the secondary bearing 132 forms the lower side of the compression space V, axially supporting the bottom surface of the roller 134 while radially supporting the lower half of the rotating shaft 123.

[0091] The secondary bearing 132 can be formed similarly to the primary bearing 131 described above. For example, the secondary bearing 132 in this embodiment may include a secondary plate portion 1321 and a secondary bearing portion 1322.

[0092] The sub-plate portion 1321 covers the lower side of the cylinder 133 and is combined with the cylinder 133. The sub-bearing portion 1322 extends axially from the center of the sub-plate portion 1321 toward the lower outer casing 112 and supports the lower half of the rotating shaft 123.

[0093] The sub-plate portion 1321 can be formed into a circular plate shape in the same manner as the main plate portion 1311, and its outer diameter is nearly the same as that of the cylinder 133. Thus, the outer peripheral surface of the sub-plate portion 1321 can be separated from the inner peripheral surface of the intermediate outer shell 111.

[0094] A secondary guide groove 1321a may be formed on the axial top surface of the secondary plate portion 1321. Since the secondary guide groove 1321a is formed symmetrically with respect to the main guide groove 1311a described above with respect to the roller 134, the description of the secondary guide groove 1321a is replaced by the description of the main guide groove 1312a.

[0095] The secondary bearing hole 1322a of the secondary bearing portion 1322 can extend axially and be formed into a hollow bushing shape. An oil groove (not shown) is formed on the secondary bearing surface 1322a1, which is the inner circumferential surface of the secondary bearing hole 1322a.

[0096] Reference Figures 1 to 3In this embodiment, the cylinder 133 can be tightly attached to the bottom surface of the main bearing 131 and bolted together with the auxiliary bearing 132 to the main bearing 131. Thus, the cylinder 133 can be fixedly connected to the housing 110 through the main bearing 131.

[0097] The cylinder 133 can be formed as an annular shape with a compression space V at its center. For example, the inner circumferential surface 1331 of the cylinder 133 constituting the compression space V can be formed as a perfect circle with the same inner diameter along the circumferential direction, and the center of the compression space V ( Figure 4 As shown) Ov is relative to the constituting axis ( Figure 4 As shown) the rotation center of roller 134 of Os ( Figure 4 As shown, the cylinder 133's inner circumferential surface 1331 is eccentrically formed relative to the roller 134's outer circumferential surface 1341. A proximity point (or contact point) P is formed between the cylinder 133's inner circumferential surface 1331 and the roller 134's outer circumferential surface 1341, where the inner circumferential surface 1331 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134 are in near contact.

[0098] The cylinder 133 can have an intake port 1332 and an exhaust port 1333a and 1333b respectively formed on both sides of the circumference with the approach point P as the center. Thus, the intake port 1332 and the exhaust port 1333a and 1333b can be separated from each other by means of the approach point P.

[0099] The suction port 1332 can be directly connected to the suction pipe 115 penetrating the housing 110, and the discharge ports 1333a and 1333b communicate with the internal space 110a of the housing 110 and are indirectly connected to the discharge pipe 116 penetrating the housing 110. Thus, refrigerant can be directly drawn into the compression space V through the suction port 1332, and the compressed refrigerant is discharged into the internal space 110a of the housing 110 through the discharge ports 1333a and 1333b and then discharged into the discharge pipe 116. Therefore, the internal space 110a of the housing 110 can be maintained at a high pressure that constitutes the discharge pressure.

[0100] Alternatively, an additional suction valve may not be installed at the suction inlet 1332. Instead, each discharge outlet 1333a, 1333b may be equipped with a discharge valve 1335a, 1335b that opens and closes each outlet 1333a, 1333b respectively. Each discharge valve 1335a, 1335b may be configured as a reed valve with one end fixed and the other end free. However, in addition to reed valves, each discharge valve 1335a, 1335b may also be configured as a piston valve or other valve as needed.

[0101] Furthermore, when each discharge valve 1335a, 1335b is a reed valve, valve receiving grooves 1334a, 1334b can be formed on the outer circumferential surface of the cylinder 133 to accommodate each discharge valve 1335a, 1335b. This minimizes the length of the discharge ports 1333a, 1333b, thereby reducing unnecessary volume. Figure 2 As shown, valve receiving grooves 1334a and 1334b can be formed into a triangular shape to ensure a flat valve seat surface.

[0102] Furthermore, there may be a plurality of discharge outlets 1333a and 1333b along the compression path (compression direction). For ease of explanation, the discharge outlet located upstream of the compression path will be defined as the first discharge outlet 1333a, and the discharge outlet located downstream will be defined as the second discharge outlet 1333b.

[0103] However, the number of discharge ports does not have to be multiple. For example, if the overcompression of the refrigerant is to be appropriately reduced by forming a longer compression cycle, then the inner circumferential surface of the cylinder 133 may form only one discharge port.

[0104] Additionally, refer to Figure 4 The roller 134 described above can be rotatably arranged in the compression space V of the cylinder 133. The roller 134 can be formed such that the rotation center Or and the axis Os of the rotation shaft 123 are located on the same axis. The roller 134 can be integrally formed with the rotation shaft 123 or assembled with the rotation shaft 123. Thus, the roller 134 can rotate together with the rotation shaft 123 around the axis Os.

[0105] The outer peripheral surface 1341 of the roller 134 can be formed as a circle, and a plurality of bushing grooves 1342 are formed on the outer peripheral surface 1341 of the roller 134 at predetermined intervals along the circumferential direction. The bushing grooves 1342 can be defined as a first bushing groove (not shown), a second bushing groove (not shown), and a third bushing groove (not shown) along the compression direction (the rotation direction of the roller), and the first bushing groove, the second bushing groove, and the third bushing groove are formed to be identical to each other.

[0106] A rocker bushing 1343 constituting a blade groove can be rotatably coupled to each bushing groove 1342. The rocker bushing 1343 can be inserted into and coupled to the bushing groove 1342 in such a way that two bushings formed in a generally semi-circular shape are spaced apart by the thickness of the respective blades 1351, 1352, 1353. Thus, the blades 1351, 1352, 1353 coupled to the rocker bushing 1343 can move along the inner circumferential surface 1331 of the cylinder 133 and rotate with the rocker bushing 1343 as the hinge point.

[0107] As described above, if the blades 1351, 1352, and 1353 can be rotatably supported relative to the roller 134 by each rocker bushing 1343, then even when the roller 134 rotates, the blades 1351, 1352, and 1353 will always face the center Ov of the compression space V, provided that the rotation center Or of the roller 134 is eccentrically located at the center Ov of the compression space V. Therefore, the leading tips 1351b, 1352b, and 1353b of the blades constituting the leading surfaces of the blades 1351, 1352, and 1353 described later can be formed with the same curvature as the inner circumferential surface 1331 of the cylinder 133, thereby ensuring the sealing area between each blade 1351, 1352, and 1353 and the cylinder 133.

[0108] Additionally, back pressure chambers 1344 can be formed on the inner side of the bushing groove 1342, that is, between the bushing groove 1342 and the rotation center Or of the roller 134. The back pressure chambers 1344 are radially connected to each bushing groove 1342 and axially connected to the main guide groove 1311a and / or the auxiliary guide groove 1321a described above. Thus, the pressure of the high-pressure oil (or refrigerant) flowing into the main guide groove 1311a and / or the auxiliary guide groove 1321a can be used to apply pressure to each blade 1351, 1352, 1353 towards the inner circumferential surface 1331 of the cylinder 133.

[0109] Each back pressure chamber 1344 can be sealed by a main bearing 131 and a secondary bearing 132, as described above, and is axially connected to the main guide groove 1311a and / or the secondary guide groove 1321a. The back pressure chamber 1344 can be simultaneously connected to the main guide groove 1311a and / or the secondary guide groove 1321a.

[0110] Reference Figures 2 to 4 In this embodiment, the plurality of blades 1351, 1352, and 1353 may include blade bodies 1351a, 1352a, and 1353a, blade front ends (or front surfaces) 1351b, 1352b, and 1353b, blade rear ends (or rear surfaces) 1351c, 1352c, and 1353c, and guide protrusions 1351d, 1352d, and 1353d. The blade front ends 1351b, 1352b, and 1353b can be understood as the surfaces that contact the inner circumferential surface 1331 of the cylinder 133, and the blade rear ends 1351c, 1352c, and 1353c can be understood as the surfaces facing the back pressure chamber 1344.

[0111] Each blade body 1351a, 1352a, 1353a can be formed into a generally rectangular parallelepiped shape. Thus, each blade body 1351a, 1352a, 1353a can slide smoothly along the length direction between each rocker bushing 1343.

[0112] The leading tips 1351b, 1352b, and 1353b of the blades can be formed into curved shapes in a manner that allows them to make line contact with the inner circumferential surface 1331 of the cylinder 133. The sealing surfaces of the leading edges of each blade 1351b, 1352b, and 1353b are formed with a curvature that is nearly identical to that of the inner circumferential surface 1331 of the cylinder 133. Thus, even if each blade leading tip 1351b, 1352b, and 1353b is slightly spaced from the inner circumferential surface 1331 of the cylinder 133, leakage between the compression chambers can be suppressed by ensuring a sealing area between the blade leading tips 1351b, 1352b, and 1353b and the cylinder.

[0113] The rear ends 1351c, 1352c, and 1353c of the blades can be formed in a planar manner. As a result, the rear pressure-bearing surfaces constituting the rear ends 1351c, 1352c, and 1353c of each blade can uniformly receive the back pressure of each back pressure chamber 1344, thereby allowing each blade 1351, 1352, and 1353 to move rapidly toward the cylinder 133, and the movement of the blades 1351, 1352, and 1353 becomes stable.

[0114] The guide protrusions 1351d, 1352d, and 1353d can be formed to extend axially from the rear side of the blade body 1351a, 1352a, and 1353a constituting the rear end 1351c, 1352c, and 1353c. For example, the guide protrusions 1351d, 1352d, and 1353d can be composed of an upper guide protrusion (hereinafter, the first guide protrusion) 1351d1 (not shown) (not shown) extending axially upward toward the main guide groove 1311a and a lower guide protrusion (hereinafter, the second guide protrusion) 1351d2 (not shown) (not shown) extending axially downward toward the secondary guide groove 1321a.

[0115] The first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can be constructed with the same shape and size and formed on the same axis. However, depending on the circumstances, the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can also be formed with different shapes and sizes, and formed eccentrically to each other along the axial direction. Hereinafter, the example of the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) being constructed with the same shape and size and formed on the same axis will be described.

[0116] The first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can be formed to have the same width as the blade bodies 1351a, 1352a, and 1353a. However, depending on the circumstances, the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can also be formed to have a width greater than or less than the blade bodies 1351a, 1352a, and 1353a. For example, the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can be formed to extend circumferentially from both sides or one side of the blade bodies 1351a, 1352a, and 1353a. In this case, preferably, the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can be formed in an arc shape corresponding to the inner circumferential surfaces 1311a1, 1321a1 of each guide groove 1311a, 1321a. Furthermore, in this case, although the first guide protrusions 1351d1, 1352d1, 1353d1 and the second guide protrusions 1351d2, 1352d2, 1353d2 can be formed in the same circumferential direction, they can also be formed in different circumferential directions.

[0117] The outer peripheral surfaces of the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can each be formed in a planar manner. However, since the inner peripheral surfaces 1311a1, 1321a1 of the guide grooves 1311a, 1321a1 facing the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) are formed as circular curved surfaces, the outer peripheral surfaces of the first guide protrusions 1351d1 (not shown), (not shown) and the second guide protrusions 1351d2 (not shown), (not shown) can be formed as circular curved surfaces in a manner corresponding to the inner peripheral surfaces 1311a1, 1321a1 of each guide groove 1311a, 1321a1, or more precisely, preferably, corresponding to the inner peripheral surface 1365a of the first bearing portion 1365 of the inner wheel 1362 described later.

[0118] Additionally, refer to Figures 1 to 4Blade bearings 136 and 137 can be provided between the outer peripheral surfaces of the first guide protrusions 1351d1, 1352d1, 1353d1 and the inner peripheral surfaces 1311a1 and 1321a1 of the main guide groove 1311a and the auxiliary guide groove 1321a facing them. The blade bearings 136 and 137 can be variously used, such as ball bearings, roller bearings, bushing bearings, and foil bearings. This embodiment focuses on an example of ball bearing blade bearings 136 and 137; the blade bearings 136 and 137 will be described further later.

[0119] The operation of the rotary vane compressor described above is as follows.

[0120] That is, when power is applied to the drive motor 120, the rotor 122 of the drive motor 120 and the rotating shaft 123 connected to the rotor 122 rotate, and the roller 134 connected to the rotating shaft 123 or formed as one piece rotates together with the rotating shaft 123.

[0121] Therefore, the plurality of blades 1351, 1352, 1353, which are slidably inserted into the rocker bushing 1343 of the roller 134 that acts as a blade groove, are drawn out or introduced from the roller 134 by the centrifugal force generated by the rotation of the roller 134 and the back pressure of the back pressure chamber 1343 located on the rear side of the blades 1351, 1352, 1353, so that the blade tip 1351b, 1352b, 1353b of each blade 1351, 1352, 1353 contacts the inner circumferential surface 1331 of the cylinder 133.

[0122] Therefore, the compression space V of the cylinder 133 is divided by a plurality of blades 1351, 1352, 1353 into compression chambers (including suction chambers or discharge chambers) V1, V2, V3 corresponding to the number of blades 1351, 1352, 1353. Each compression chamber V1, V2, V3 moves as the roller 134 rotates, and the volume of each compression chamber V1, V2, V3 changes due to the shape of the inner circumferential surface 1331 of the cylinder 133 and the eccentricity of the roller 134. The refrigerant drawn into each compression chamber V1, V2, V3 repeatedly undergoes the following series of processes: the refrigerant is compressed while moving along the roller 134 and the blades 1351, 1352, 1353, and the refrigerant is discharged into the internal space 110a of the housing 110 through the discharge ports 1333a, 1333b provided on the inner circumferential surface 1331 of the cylinder 133.

[0123] At this time, a plurality of blades 1351, 1352, and 1353 are drawn out from the roller 134, and the front ends 1351b, 1352b, and 1353b of the blades forming the front side of the blades 1351, 1352, and 1353 contact the inner circumferential surface 1331 of the cylinder 133, thereby separating the compression chambers.

[0124] However, if the leading tips 1351b, 1352b, and 1353b of each blade 1351, 1352, and 1353 are slidably moved in a state of constant contact with the inner circumferential surface 1331 of the cylinder 133, the mechanical losses (or frictional losses) caused by friction between the cylinder 133 and the blades 1351, 1352, and 1353 will increase significantly. On the other hand, given this, if the back pressure on each blade 1351, 1352, and 1353 is reduced, the leading tips 1351b, 1352b, and 1353 of each blade 1351, 1352, and 1353 will be separated from the inner circumferential surface 1331 of the cylinder 133, resulting in refrigerant leakage between the compression chambers. In particular, during the compression stroke, as the pressure in the corresponding compression chamber increases, the blades 1351, 1352, and 1353 are pushed away from the cylinder 133 by the gas force in the compression chamber. Therefore, the cylinder 133 and the blades 1351, 1352, and 1353 will be further separated, thereby increasing refrigerant leakage.

[0125] Therefore, the back pressure acting on the rear ends 1351c, 1352c, and 1353c of the blades can be appropriately reduced. Within a range where refrigerant does not leak between the inner circumferential surface 1331 of the cylinder 133 and the leading surfaces of the blades 1351, 1352, and 1353, the cylinder 133 and the blades 1351, 1352, and 1353 move relative to each other in a separated state. Thus, preferably, it is possible to reduce the mechanical friction loss between the cylinder 133 and the blades 1351, 1352, and 1353 while ensuring the back pressure acting on the blades 1351, 1352, and 1353, thereby suppressing refrigerant leakage.

[0126] In this embodiment, as described above, a main guide groove 1311a can be formed in the main plate portion 1311, and a secondary guide groove 1321a can be formed in the secondary plate portion 1321. A first guide protrusion 1351d1 (not shown) and (not shown) are formed at the upper axial end of the blade bodies 1351a, 1352a, and 1353a facing these main guide grooves 1311a and secondary guide grooves 1321a, and a second guide protrusion 1351d2 (not shown) and (not shown) are formed at the lower axial end. Therefore, the first guide protrusion 1351d1 (not shown), (not shown) and the second guide protrusion 1351d2 (not shown), (not shown) are stuck in the main guide groove 1311a and the auxiliary guide groove 1321a, thereby limiting the amount of blade protrusion. This reduces the mechanical friction loss between the cylinder 133 and the blades 1351, 1352, 1353 while ensuring the back pressure acting on the blades 1351, 1352, 1353, thereby suppressing refrigerant leakage.

[0127] As described above, when guide grooves 1311a and 1321a and guide protrusions 1351d, 1352d, and 1353d are formed, frictional losses can occur between the guide grooves 1311a and 1321a and the guide protrusions 1351d, 1352d, and 1353d. To address this, the frictional losses between the guide grooves 1311a and 1321a and the guide protrusions 1351d, 1352d, and 1353d can be reduced by providing the blade bearings 136 and 137 described above between the guide grooves 1311a and 1321a and the guide protrusions 1351d, 1352d, and 1353d, respectively.

[0128] Figure 5 It is shown in magnification Figure 1 A cross-sectional view of the compression section in the middle. Figure 6 It is broken and shown Figure 5 A three-dimensional diagram of the blade bearing in the image. Figure 7 It is shown Figure 6 A cross-sectional view of the blade bearing installed in the main bearing configuration.

[0129] Reference Figures 5 to 7 In this embodiment, blade bearings 136 and 137 may be respectively provided between the main guide groove 1311a and the first guide protrusion 1351d1 (not shown) and (not shown) inserted into the main guide groove 1311a and / or between the secondary guide groove 1321a and the second guide protrusion 1351d2 (not shown) and (not shown) inserted into the secondary guide groove 1321a.

[0130] As described above, although various types of bearings such as ball bearings, roller bearings, bushing bearings, and foil bearings can be used in blade bearings 136 and 137, this embodiment will focus on describing blade bearings 136 and 137 with ball bearings.

[0131] Alternatively, the blade bearings 136 and 137 may also extend between the roller 134 and the main bearing 131 and the secondary bearing 132 facing it. In this embodiment, the description will focus on an example where the blade bearings 136 and 137 are respectively disposed between the guide grooves 1311a and 1321a and the guide protrusions 1351d, 1352d and 1353d, and between the roller 134 and the bearings 131 and 132.

[0132] In addition, the blade bearings 136 and 137 are respectively defined as the main side blade bearing 136, which is located between the main guide groove 1311a and the first guide protrusion 1351d1 (not shown) and (not shown), and the secondary side blade bearing 137, which is located between the secondary guide groove 1321a and the second guide protrusion 1351d2 (not shown) and (not shown). Hereinafter, the main side blade bearing will be used as a representative example for explanation.

[0133] The blade bearing 136 in this embodiment may include an outer wheel 1361, an inner wheel 1362, and a plurality of balls 1363.

[0134] The outer wheel 1361 can be formed as a ring, and the center Oob of the outer wheel 1361 and the center Og of the main guide groove 1311a can be formed to be located on the same axis. In other words, the center Oob of the outer wheel 1361 can be eccentrically set relative to the rotation center Or of the roller 134.

[0135] Furthermore, the outer diameter of the outer wheel 1361 can be formed to be nearly the same as or slightly smaller than the inner diameter of the main guide groove 1311a. For example, when the outer diameter of the outer wheel 1361 is nearly the same as the inner diameter of the main guide groove 1311a, the outer wheel 1361 can be pressed into and fixed to the main guide groove 1311a; when the outer diameter of the outer wheel 1361 is slightly smaller than the inner diameter of the main guide groove 1311a, the outer wheel 1361 can rotate freely within the main guide groove 1311a. In this embodiment, the example of the outer diameter of the outer wheel 1361 being nearly the same as the inner diameter of the main guide groove 1311a and the outer wheel 1361 being pressed into and fixed to the inner circumferential surface of the main guide groove 1311a will be described as the central example.

[0136] The inner wheel 1362 may include a first bearing portion 1365 and a second bearing portion 1366. The first bearing portion 1365 may be formed as an annular shape, and the second bearing portion 1366 may be formed as a circular plate with a hollow center.

[0137] The first bearing portion 1365 can be formed with an outer diameter smaller than that of the outer wheel 1361 and an inner diameter larger than that of the main bearing bore 1312a. The center Ob1 of the first bearing portion 1365 and the center Oob of the outer wheel 1361 can be formed to be located on the same axis; in other words, the center Ob1 of the first bearing portion 1365 can be eccentrically formed relative to the rotation center Or of the roller 134. Thus, the inner wheel 1362, including the first bearing portion 1365, can be rotatably inserted into the interior of the outer wheel 1361.

[0138] The second bearing portion 1366 may extend in a flange shape on the outer peripheral surface of the lower end or the lower periphery of the first bearing portion 1365. The second bearing portion 1366 may be formed as a single unit with the first bearing portion 1365 or formed separately and then assembled.

[0139] For example, when the second bearing portion 1366 and the first bearing portion 1365 are formed as one unit, the manufacturing cost can be reduced by eliminating the assembly process of the integral inner wheel. When the second bearing portion 1366 is assembled to the first bearing portion 1365, the sealing portions 1367 and 1377 described later can be easily formed by making the thickness t2 of the second bearing portion 1366 thicker than the thickness t1 of the first bearing portion 1365.

[0140] However, when the first bearing portion 1365 and the second bearing portion 1366 are formed as a single unit, the thickness t2 of the second bearing portion 1366 can also be made thicker than the thickness t1 of the first bearing portion 1365. Similarly, without forming an additional sealing portion 1367, the thickness t2 of the second bearing portion 1366 can also be made thicker than the thickness t1 of the first bearing portion 1365. This ensures a sufficient sealing area between the outer peripheral surface 1366a of the second bearing portion 1366 and the inner peripheral surface 1331 of the cylinder barrel 133.

[0141] The inner diameter D1 of the second bearing portion 1366 can be formed to the extent that the back pressure chamber 1344 can communicate with the main guide groove 1311a. For example, it can be formed to be smaller than the inner diameter D2 of the main guide groove 1311a and larger than the diameter D3 of the imaginary circle of the inner end of each connected back pressure chamber 1344. As a result, the high-pressure oil flowing into the main guide groove 1311a can flow smoothly into each back pressure chamber 1344 without being blocked by the second bearing portion 1366.

[0142] The outer diameter D12 of the second bearing portion 1366 can be formed to be approximately the same as or slightly smaller than the inner diameter D4 of the inner circumferential surface 1331 of the cylinder 133, i.e., the compression space V. Thus, the second bearing portion 1366 can be rotatably inserted into the internal space of the cylinder 133, i.e., the compression space V, and rotate together with the first bearing portion 1365 around the rotation center Or of the roller 134. Therefore, the first bearing 1365 can also be defined as a rotating ring portion, and the second bearing portion 1366 as a rotating plate portion.

[0143] In this case, the second bearing portion 1366 can be formed such that one of its axial sides is separated from the bottom surface of the main plate portion 1311 or the top surface of the sub-plate portion 1321 facing it by a predetermined interval t3. For example, the lower end of the second bearing portion 1366 can be formed to be slightly longer than the lower end of the first bearing portion 1365, so that the second bearing portion 1366 is axially separated from the main plate portion 1311 or the sub-plate portion 1321. Thus, when the second bearing portion rotates, mechanical friction loss can be reduced by suppressing contact with the main plate portion 1311 or the sub-plate portion 1321.

[0144] Furthermore, the second bearing portions 1366 of the blade bearings 136 respectively disposed on both axial sides of the roller form a substantial compression space V by sealing both axial sides of the compression space V that constitutes the internal space of the cylinder 133. Therefore, a sealing portion 1367 for sealing the compression space V can also be provided between the outer peripheral surface of the second bearing portion 1366 and the inner peripheral surface 1331 of the cylinder 133 facing it.

[0145] The sealing portion 1367 may be formed by at least one sealing groove that is annular in the circumferential direction on the outer peripheral surface of the second bearing portion 1366. Figure 8 and Figure 9 It is shown Figure 5 A cross-sectional view of another embodiment of the sealing portion of the blade bearing.

[0146] For example, such as Figure 5 As shown, the sealing part 1367 can be formed by a sealing groove, such as Figure 8 As shown, it can also be composed of a plurality of sealing grooves arranged at predetermined intervals along the axial direction. Thus, oil or refrigerant is filled into the sealing portion 1367, thereby sealing the compression chambers.

[0147] Or such as Figure 9 As shown, the sealing portion 1367 may also have a sealing groove 1367a formed on the outer peripheral surface of the second bearing portion 1366, and an annular sealing member 1367b inserted into the sealing groove 1367a. In this case, the sealing member 1367b may be made of a lubricating Teflon material or the like.

[0148] Reference Figure 6 and Figure 7 A plurality of balls 1363 can be inserted between the inner circumferential surface of the outer wheel 1361 and the outer circumferential surface of the inner wheel 1362. Thus, the inner wheel 1362, which is in contact with the first guide protrusions 1351d1 (not shown) and (not shown) of the blades 1351, 1352, and 1353, can move relative to the outer wheel 1361.

[0149] Additionally, refer to Figure 5 Alternatively, the secondary blade bearing 137 described above can also be used between the secondary guide groove 1321a of the secondary bearing 132 and the second guide protrusions 1351d2 (not shown) and (not shown) of the blades 1351, 1352, and 1353. As with the primary blade bearing, the secondary blade bearing 137 consists of an outer wheel 1371, an inner wheel 1372, and a plurality of balls 1373; this will be described in place of the primary blade bearing 136.

[0150] Although not shown in the figure, the secondary blade bearing 137 may also be formed in a different shape than the primary blade bearing 136. For example, the primary blade bearing 136 may be formed by a ball bearing, while the secondary blade bearing 137 may be formed by a roller bearing or a bushing bearing, etc.

[0151] As described above, with blade bearings 136 and 137 formed by ball bearings respectively provided between the main guide groove 1311a and the first guide protrusions 1351d1 (not shown) and (not shown), and between the secondary guide groove 1321a and the second guide protrusions 1351d2 (not shown) and (not shown), even if the guide protrusions 1351d, 1352d, and 1353 of each blade 1351, 1352, and 1353 rotate together with the roller 134, the inner wheels 1362 and 1372 of the blade bearings 136 and 137 that are in contact with the guide protrusions 1351d, 1352d, and 1353 of the blade 1351, 1352, and 1353 will also rotate relative to the outer wheel 1361 due to the plurality of balls 1363. Therefore, each blade 1351, 1352, 1353 can significantly reduce radial friction loss between the guide protrusions 1351d, 1352d, 1353d and the guide grooves 1311a, 1321a while having guide protrusions 1351d, 1352d, 1353d.

[0152] Meanwhile, in this embodiment, the inner wheel 1362 not only has first bearing portions 1365 and 1375 between the guide protrusions 1351d, 1352d, 1353d and guide grooves 1311a and 1321a, but also has second bearing portions 1366 and 1376 extending between the main bearing portion 1311 and the upper side of the roller 134, and between the secondary bearing portion 1321 and the lower side of the roller 134. The second bearing portions 1366 and 1376 can rotate together with the roller 134. This significantly reduces axial friction losses between the main bearing 131 and the roller 134, and between the secondary bearing 132 and the roller 134.

[0153] Therefore, by limiting the amount of blade protrusion, frictional losses between the blade tip and the cylinder can be suppressed, while radial frictional losses between the guide protrusion and the guide groove, as well as axial frictional losses between the main bearing and the rollers, and between the secondary bearing and the rollers, can also be significantly reduced. Thus, compressor efficiency can be improved by reducing mechanical frictional losses in the compression section.

[0154] Another embodiment of the blade bearing is as follows.

[0155] That is, in the aforementioned embodiments, the inner wheel can be composed of a first bearing portion and a second bearing portion, or, depending on the situation, the outer wheel of the blade bearing can also be composed of a first bearing portion and a second bearing portion. For ease of explanation, the following description will focus on the main-side blade bearing, and the description of the secondary-side blade bearing will be replaced by the description of the main-side blade bearing.

[0156] Figure 10 This is a cross-sectional view showing another embodiment of the blade bearing.

[0157] Reference Figure 10 The main-side blade bearing 136 in this embodiment may include an outer wheel 1361, an inner wheel 1362, and a plurality of balls 1363. Since these outer wheels 1361, inner wheels 1362, and plurality of balls 1363 are similar to those in the foregoing embodiments, a detailed description of them is provided instead of a description of the foregoing embodiments.

[0158] However, in this embodiment, the outer wheel 1361 can be composed of a first bearing portion 1365 and a second bearing portion 1366, and the inner wheel 1362 can be formed as an annular shape. In this case, the second bearing portion 1366 can be inserted into the compression space V of the cylinder 133 and form the upper side surface of the compression space V.

[0159] In this embodiment, the outer peripheral surface 1365a of the first bearing portion 1365 of the outer wheel 1361 can be pressed into and fixed to the inner peripheral surface 1311a1 of the main guide groove 1311a as described in the previous embodiment, or it can be rotatably inserted into the inner peripheral surface 1311a1 of the main guide groove 1311a.

[0160] For example, when the outer wheel 1361 is pressed into and fixed to the main guide groove 1311a as described in the previous embodiment, the second bearing portion 1366 can also be fixed to the main plate portion 1311. Therefore, leakage of the compression space V can be more effectively suppressed by tightly abutting the outer peripheral surface 1366a of the second bearing portion 1366 and the inner peripheral surface 1331 of the cylinder 133. Furthermore, with the second bearing portion 1366 fixed, compression efficiency can be improved by shaping the inner peripheral surface of the cylinder 133 into various configurations, such as a symmetrical ellipse (combining multiple ellipses other than a circle) or an asymmetrical ellipse.

[0161] On the other hand, when the outer wheel 1361 is rotatably inserted into the inner circumferential surface 1311a1 of the first bearing portion 1365, as in the aforementioned embodiment, the second bearing portion 1366 can rotate together with the roller 134. Therefore, not only can the radial friction loss of the first bearing portion 1365 be suppressed, but also the axial friction loss of the second bearing portion 1366 can be suppressed, thereby improving compressor efficiency.

[0162] Another embodiment of the blade bearing is as follows.

[0163] That is, in the aforementioned embodiments, the inner or outer wheel of the blade bearing may be composed of a first bearing portion and a second bearing portion, or, depending on the circumstances, the inner or outer wheel of the blade bearing may be composed of only the first bearing portion. For ease of explanation, the following description will focus on the main-side blade bearing, and the description of the secondary-side blade bearing will be replaced by the description of the main-side blade bearing.

[0164] Figure 11 This is a cross-sectional view showing yet another embodiment of the blade bearing.

[0165] Reference Figure 11 The blade bearing 136 in this embodiment may include an outer wheel 1361, an inner wheel 1362, and a plurality of balls 1363. Since these outer wheels 1361, inner wheels 1362, and plurality of balls 1363 are similar to those in the foregoing embodiments, a detailed description of them is provided instead of a description of the foregoing embodiments.

[0166] However, in this embodiment, the outer wheel 1361 and the inner wheel 1362 may each be composed solely of the first bearing portion 1365. For example, the inner wheel 1362 may be composed solely of the annular first bearing portion 1365, and thus be disposed only between the inner circumferential surface 1311a1 of the main guide groove 1311a and the first guide protrusions 1351d1 (not shown) and (not shown). The shape and specifications of the first bearing portion 1365 may be formed to be the same as those of the first bearing portion 1365 in the aforementioned embodiments.

[0167] As described above, when the outer wheel 1361 and the inner wheel 1362 are only composed of the first bearing portion 1365, radial friction loss generated between the inner circumferential surface 1311a1 of the main guide groove 1311a and the first guide protrusions 1351d1 (not shown) and (not shown) can be suppressed.

[0168] Furthermore, as in this embodiment, the inner circumferential surface 1331 of the cylinder 133 can be formed in various ways, excluding the second bearing portion 1366. For example, the inner circumferential surface 1331 of the cylinder 133 can be formed as a symmetrical ellipse or an asymmetrical ellipse, consisting of a plurality of ellipses other than a circle. Therefore, compression loss caused by overcompression can be reduced by forming the inner circumferential surface 1331 of the cylinder 133 in a manner that forms a longer compression cycle in the compression space V.

[0169] Furthermore, as in this embodiment, excluding the second bearing portion 1366, the discharge port (not shown) can be formed on the main plate portion 1311 or the sub-plate portion 1321. This suppresses insufficient surface pressure on the blade tips 1351b, 1352b, and 1353b that would occur if the discharge port (not shown) were formed on the inner circumferential surface 1331 of the cylinder barrel 133. Consequently, compression chamber leakage and the resulting reduction in compression efficiency can be prevented beforehand by suppressing partial damage to the blade tips 1351b, 1352b, and 1353b or to the inner circumferential surface 1331 of the cylinder barrel 133 facing them.

[0170] Furthermore, although the foregoing embodiments have all been described with an example of a rocking bushing provided in the roller, it is not necessary to provide a rocking bushing. For example, in a conventional rotary vane compressor, at least one vane groove can be formed on the outer circumferential surface of the roller, and the vane can be slidably inserted into the vane groove, which can also be used in the same way.

Claims

1. A rotary compressor, wherein, include: The cylinder barrel has an inner circumferential surface that is annular. The main bearing and the auxiliary bearing are respectively disposed on both sides of the cylinder and together with the cylinder form a compression space. A guide groove is provided on the side forming the compression space. Rollers are housed in the cylinder and rotate together with the rotating shaft; At least one blade is slidably inserted into the roller, and a guide protrusion slidably inserted into the guide groove in the circumferential direction extends axially. as well as A bearing component is disposed between the guide groove of at least one of the main bearing and the secondary bearing and the guide protrusion of the blade. The bearing component includes: A first bearing portion is disposed between at least one of the main bearing and the secondary bearing and the blade that radially faces the at least one of the bearings; as well as The second bearing portion extends integrally from the first bearing portion and is disposed between at least one of the main bearing and the secondary bearing and the roller axially facing the at least one of the bearings. The second bearing portion is inserted into the cylinder barrel with its outer peripheral surface facing the inner peripheral surface of the cylinder barrel.

2. The rotary compressor according to claim 1, wherein, The second bearing portion is formed to be thicker than the first bearing portion.

3. The rotary compressor according to claim 1, wherein, The first bearing portion is formed in a ring shape, and the second bearing portion is formed in a circular plate shape.

4. The rotary compressor according to claim 1, wherein, The first bearing portion includes: The outer wheel is inserted into a guide groove in at least one of the main bearing and the secondary bearing; An inner wheel, disposed inside the outer wheel, has its inner circumferential surface slidably contacting the guide protrusion of the blade; and A sliding member is disposed between the outer wheel and the inner wheel, allowing the outer wheel and the inner wheel to move relative to each other. The second bearing portion extends radially from one end of the inner wheel of the first bearing portion or one end of the outer wheel of the first bearing portion and is disposed between the axial side of the roller and the axial side of the main bearing and the secondary bearing facing the axial side of the roller.

5. The rotary compressor according to claim 1, wherein, The axial side of the second bearing portion is separated from the axial side of the main bearing or the secondary bearing facing the axial side of the second bearing portion.

6. The rotary compressor according to claim 1, wherein, A sealing portion is provided between the outer peripheral surface of the second bearing portion and the inner peripheral surface of the cylinder.

7. The rotary compressor according to claim 1, wherein, The outer peripheral surface of the second bearing portion is formed to have the same shape as the inner peripheral surface of the cylinder.

8. The rotary compressor according to claim 1, wherein, The inner circumferential surface of the cylinder is formed into a circle or an ellipse. An outlet is formed on at least one of the axial side surface of the main bearing and the axial side surface of the secondary bearing.

9. The rotary compressor according to any one of claims 1 to 8, wherein, The roller has a bushing groove into which a pair of rocker bushings are rotatably inserted, and the blade is slidably inserted between the rocker bushings.

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