Rotary compressor

Abstract

This invention discloses a rotary compressor. The rotary compressor includes a housing with an oil storage space, a cylinder, a main bearing and a secondary bearing, a rotating shaft, rollers with blade grooves and a back pressure chamber, and at least one blade. An oil supply port connecting the back pressure chamber and the oil storage space can be formed through the main bearing or the secondary bearing, or through the rollers. Therefore, by directly supplying high-pressure oil to the rear end face of the blade, the back pressure on that blade can be increased, and compressor start-up delay can be suppressed. This improves compressor efficiency while suppressing blade vibration, thereby reducing collision noise and wear between the blades and the cylinder.

Description

Technical Field

[0001] This invention relates to a rotary compressor with blades and 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. Conversely, in a rotary vane 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, the number of compression chambers, equivalent to the number of blades, is 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, the number of compression chambers, equivalent to the number of blades, is formed continuously with each rotation of the rollers, and each chamber sequentially performs the suction, compression, and discharge strokes. Therefore, the compression ratio of a rotary vane compressor is higher than that of a rotary compressor. Consequently, rotary vane compressors are more suitable for using high-pressure refrigerants with lower ozone depletion potential (ODP) and global warming potential (GWP), such as R32, R410a, and CO2.

[0005] Such a rotary vane compressor is disclosed in Patent Document 1 (Japanese Patent Publication: JP2013-213438A). In the rotary vane compressor disclosed in Patent Document 1, the internal space of the motor chamber is filled with refrigerant at low pressure, or a structure in which multiple vanes are slidably inserted into rotating rollers reveals the characteristics of a rotary vane compressor.

[0006] In Patent Document 1, back pressure chambers are formed at the rear end of the blades, and these back pressure chambers are configured to communicate with a back pressure pocket. The back pressure pocket is divided into a first pocket that forms an intermediate pressure and a second pocket that forms or approaches an intermediate pressure at the discharge pressure. With a reference direction from the intake side to the discharge side, a first groove communicates with the back pressure pocket located upstream, and a second groove communicates with the back pressure pocket located downstream.

[0007] However, in the existing rotary vane compressors described above, a vibration phenomenon may occur during operation, where the vanes vibrate after being separated from the cylinder due to the pressure difference between the front and rear faces. This phenomenon is particularly severe during the initial startup of the compressor, which may lead to poor initial startup, thereby reducing the compressor's efficiency and potentially delaying the cooling and heating performance of the refrigeration and heating equipment using the compressor.

[0008] Furthermore, in existing rotary vane compressors, vane vibration occurs concentrated around the near-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 leads to leakage between compression chambers, which may reduce compression efficiency.

[0009] In addition, in existing rotary vane compressors, the pressure of the oil supplied to the rear end face of the vane is uneven, resulting in pressure pulsation. As a result, the back pressure formed on the rear end face of the vane cannot be constant, which may aggravate the vane vibration phenomenon.

[0010] Furthermore, the aforementioned problems may be further exacerbated when using high-pressure refrigerants such as R32, R410a, and CO2. That is, when using high-pressure refrigerants, even if the volume of the compression chamber is reduced by increasing the number of blades, only the same level of cooling capacity can be achieved as with relatively low-pressure refrigerants such as R134a. However, increasing the number of blades correspondingly increases the friction area between the blades and the cylinder. Therefore, if the bearing surface of the rotating shaft is reduced, the operation of the rotating shaft becomes considerably 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 problem the invention aims to solve

[0012] The purpose of this invention is to provide a rotary compressor that can improve compressor efficiency by suppressing delayed compressor start-up.

[0013] Furthermore, the present invention aims to provide a rotary compressor capable of suppressing vibration caused by the blades being separated from the cylinder during operation.

[0014] Furthermore, the object of the present invention is to provide a rotary compressor capable of maintaining back pressure on the blades by rapidly and uniformly supplying high-pressure oil to the rear end face of the blades.

[0015] Another object of the present invention is to provide a rotary compressor capable of reducing suction loss or compression loss by suppressing wear on the inner circumference of the cylinder or the leading edge face of the blades.

[0016] Furthermore, the object of the present invention is to provide a rotary compressor capable of suppressing vibration between the blades and the cylinder by directly supplying oil stored in the housing to the rear end face of the blades passing the near point.

[0017] Furthermore, the present invention aims to provide a rotary compressor capable of suppressing excessive rise in back pressure supporting a blade by directly supplying high-pressure oil to the rear end face of the blade passing through the near point.

[0018] Another object of the present invention is to provide a rotary compressor that can suppress blade vibration even when using high-pressure refrigerants such as R32, R410a, and CO2.

[0019] means for solving problems

[0020] A rotary compressor for achieving the purpose of this invention includes a housing, a cylinder, a main bearing and a secondary bearing, a rotating shaft, rollers, and at least one blade. The housing has an internal oil storage space. The cylinder is fixed inside the housing to form a compression space. The main bearing and the secondary bearing are respectively disposed on opposite axial sides of the cylinder, and each has an axially penetrating main bearing hole and a secondary bearing hole. The rotating shaft is supported by passing through the main bearing hole of the main bearing and the secondary bearing hole of the secondary bearing. The rollers are disposed on the rotating shaft and eccentrically positioned in the compression space, and form at least one blade groove along their outer circumferential surface, with a back pressure chamber communicating at the inner end of each blade groove. The leading edge face of each blade contacts the inner circumferential surface of the cylinder, allowing the blades to slidably insert into the blade grooves to divide the compression space into a plurality of compression chambers. An oil supply hole communicating between the back pressure chamber and the oil storage space may be provided through the main bearing or the secondary bearing. Therefore, by directly supplying high-pressure oil to the rear end face of the blade, the back pressure on the blade can be increased. This can improve compressor efficiency by suppressing compressor delay start-up while suppressing blade vibration, thereby reducing collision noise and wear between the blade and the cylinder.

[0021] As an example, the secondary bearing configured to face the oil reservoir may include: a secondary plate portion, coupled to one axial side of the cylinder; and a secondary bushing portion, extending axially from the secondary plate portion and passing through the secondary bearing bore. The oil supply hole may be formed through the secondary bushing portion. Thus, initial start-up delays can be suppressed by rapidly supplying oil stored in the oil reservoir to the rear end face of the blade.

[0022] As another example, the oil supply hole can extend between the axial end face of the secondary bushing and the side of the secondary plate facing the roller. Thus, the lower end of the oil supply hole is deeply positioned within the oil reservoir, ensuring a constant back pressure even during abnormal operation by stably supplying oil to the rear end face of the blade.

[0023] As another example, the oil supply hole can penetrate between the inner circumferential surface of the secondary bearing hole of the secondary bushing and the side of the secondary plate facing the roller. This allows for the rapid supply of oil to the rear end face of the blade via centrifugal force, thereby suppressing initial start-up delays.

[0024] As another example, an oil groove can be formed on the inner circumferential surface of the secondary bearing bore. The oil supply hole can be formed to communicate with the middle of the oil groove. This allows for a more rapid supply of oil flowing into the secondary bearing surface to the rear end face of the blade.

[0025] As an example, the secondary bearing configured to face the oil reservoir may include a secondary plate portion joined to one axial side of the cylinder barrel; and a secondary bushing portion extending axially from the secondary plate portion, with the rotating shaft passing through the secondary bushing portion and being supported. The oil supply port may be formed through the secondary plate portion. Thus, by reducing the length of the oil supply port, oil can be rapidly supplied to the rear end face of the blade.

[0026] As another example, the oil supply hole can extend through the space between the two axially opposite sides of the sub-plate at an angle relative to the axial direction. This allows for the oil supply guide groove to be machined in a straight line while reducing the length of the oil supply hole.

[0027] As another example, the oil supply hole can be composed of a first hole extending radially from the outer peripheral surface of the sub-plate and a second hole penetrating the inner side of the first hole towards the axial side of the sub-plate facing the roller. This allows for a more rapid supply of oil to the rear end face of the blade by further reducing the actual length of the oil supply hole.

[0028] As an example, the secondary bearing configured to face the oil reservoir may include: a secondary plate portion, coupled to one axial side of the cylinder; and a secondary bushing portion, extending axially from the secondary plate portion and passing through the secondary bearing bore. The oil supply port may be formed through the secondary bushing portion. An oil pump is also provided in the secondary bushing portion, and the oil supply port may communicate with the outlet of the oil pump. This allows for a more rapid and constant supply of oil to the rear end face of the blade.

[0029] As an example, an oil flow path can be formed inside the rotating shaft in a hollow shape to draw oil from the oil reservoir space in the housing. A plurality of back pressure chambers, communicating with the oil flow path and having different pressures, can be formed in the main bearing or the auxiliary bearing. The plurality of back pressure chambers are formed at predetermined intervals along the circumferential direction on the axial side facing the roller. An oil supply port can be formed between the plurality of back pressure chambers and overlaps at least partially with the back pressure chambers axially. Thus, by periodically communicating with the oil supply port through the back pressure chambers, appropriate back pressure can be maintained on the rear end face of the blade at the required location.

[0030] As another example, the inner diameter of the oil supply hole can be less than or equal to the inner diameter of the back pressure chamber. This allows for the supply of an appropriate amount of oil to the back pressure chamber while simultaneously suppressing oil buildup in the corresponding area of ​​the sub-bearing using the oil supply hole.

[0031] As another example, the inner diameter of the oil supply hole can be formed such that the upper end facing the roller is greater than or equal to the lower end within the oil storage space. This allows oil from the oil storage space to be rapidly supplied to the rear end face of the blade through the oil supply hole by generating a differential pressure within it.

[0032] As another example, a connecting groove can be formed between the upper end facing the roller and the back pressure chamber facing the upper end in the circumferential direction in the oil supply hole. This allows oil to be supplied more rapidly to the rear end face of the blade through the oil supply hole by creating a larger differential pressure between the oil supply hole and the back pressure chamber.

[0033] Furthermore, the rotary compressor for achieving the purpose of this invention includes a housing, a cylinder, a main bearing and a secondary bearing, a rotating shaft, rollers, and at least one blade. The housing has an oil storage space inside. The cylinder is fixed inside the housing. The main bearing and the secondary bearing, together with the cylinder, form a compression space. The rotating shaft is radially supported by the main bearing and the secondary bearing. The rollers are disposed on the rotating shaft and eccentrically positioned in the compression space, and form at least one blade groove along their outer circumferential surface, with a back pressure chamber communicating at the inner end of the blade groove. The front end face of the blade contacts the inner circumferential surface of the cylinder, allowing the blade to slidably insert into the blade groove, thereby dividing the compression space into a plurality of compression chambers. An oil flow path can be formed in a hollow shape inside the rotating shaft. An oil supply hole penetrating the back pressure chamber can be formed on the inner circumferential surface of the oil flow path. Thus, the back pressure on the blade can be increased by directly supplying high-pressure oil to the rear end face of the blade.

[0034] As an example, an oil supply guide groove communicating with the back pressure chamber can also be formed on the axial side of the roller. The oil supply hole can penetrate between the inner circumferential surface of the oil flow path and the inner circumferential surface of the oil supply guide groove. Thus, the oil supply hole can be easily machined while stabilizing the blade movement by reducing pressure pulsation in the back pressure chamber communicating with the oil supply hole.

[0035] As another example, the rotating shaft may have an oil passage hole formed in the middle of the oil flow path, extending towards the main bearing or the secondary bearing and into the outer circumferential surface of the rotating shaft. The inner diameter of the oil supply hole may be less than or equal to the inner diameter of the oil passage hole. This allows for the suppression of overall frictional losses between the cylinder and the blades by preventing excessive back pressure from acting on the rear end face of the blades.

[0036] Invention Effects

[0037] In the rotary compressor of this embodiment, an oil supply hole can be passed through the main bearing or auxiliary bearing, connecting the back pressure chamber and the oil storage space. This allows for the direct supply of high-pressure oil to the rear end face of the blades to increase the back pressure on those blades, and also enables the compressor efficiency to be improved by suppressing compressor start-up delay while suppressing blade vibration, thereby reducing collision noise and wear between the blades and the cylinder.

[0038] Furthermore, in the rotary compressor of this embodiment, the oil supply port can be formed in the auxiliary bushing portion extending toward the oil storage space through the auxiliary bearing. This allows for the suppression of initial start-up delays by rapidly supplying oil stored in the oil storage space to the rear end face of the blades.

[0039] Furthermore, in the rotary compressor of this embodiment, the oil supply hole can penetrate between the axial end face of the auxiliary bushing and the roller-facing side of the auxiliary plate. Therefore, by positioning the lower end of the oil supply hole deeper within the oil reservoir, oil can be stably supplied to the rear end face of the blades even during abnormal operation.

[0040] Furthermore, in the rotary compressor of this embodiment, the oil supply hole can penetrate between the inner circumferential surface of the auxiliary bearing hole in the auxiliary bushing portion and the roller-facing side of the auxiliary plate portion. This allows for the rapid supply of oil flowing into the auxiliary bearing surface to the rear end face of the blades using centrifugal force.

[0041] Furthermore, in the rotary compressor of this embodiment, the oil supply hole can be formed through the sub-plate portion. This allows for rapid oil supply to the rear end face of the blades by reducing the length of the oil supply hole.

[0042] Furthermore, in the rotary compressor of this embodiment, the oil supply port can be formed through the auxiliary bushing portion, and the lower end of the oil supply port can be connected to the outlet of the oil pump. This allows for a more rapid and constant supply of oil to the rear end face of the blades.

[0043] Furthermore, in the rotary compressor of this embodiment, the oil supply port can be formed between a plurality of back pressure chambers, and overlaps at least partially with the back pressure chambers along the axial direction. This allows the rear end face of the blades to maintain appropriate back pressure at desired locations by periodically communicating the back pressure chambers with the oil supply port.

[0044] Furthermore, in the rotary compressor of this embodiment, the inner diameter of the oil supply port can be formed such that the upper end facing the roller is greater than or equal to the lower end within the oil storage space. This allows oil from the oil storage space to be rapidly supplied to the rear end face of the blades through the oil supply port by creating a differential pressure within it.

[0045] Furthermore, in the rotary compressor of this embodiment, a connecting groove can be formed between the upper end of the oil supply port facing the roller and the back pressure chamber facing the upper end in the circumferential direction. This allows for a greater differential pressure to be generated between the oil supply port and the back pressure chamber, enabling oil to be supplied more rapidly to the rear end face of the blades through the oil supply port.

[0046] Furthermore, in the rotary compressor of this embodiment, an oil supply hole penetrating the back pressure chamber can be formed on the inner circumferential surface of the oil flow path. This allows for the increase of the back pressure on the blade by directly supplying high-pressure oil to the rear end face of the blade.

[0047] Furthermore, in the rotary compressor of this embodiment, an oil supply guide groove communicating with the back pressure chamber can be formed at one end of the back pressure chamber, and an oil supply hole can penetrate between the inner circumferential surface of the oil flow path and the inner circumferential surface of the oil supply guide groove. This allows for easy machining of the oil supply hole while stabilizing blade movement by reducing pressure pulsations in the back pressure chamber communicating with the oil supply hole.

[0048] Furthermore, in the rotary compressor of this embodiment, the inner diameter of the oil supply port can be smaller than or equal to the inner diameter of the oil passage. This allows for the suppression of overall frictional losses between the cylinder and the blades by preventing excessive back pressure from acting on the rear end face of the blades. Attached Figure Description

[0049] Figure 1 This is a cross-sectional view showing an embodiment of the rotary blade compressor of the present invention.

[0050] Figure 2 It is decomposition Figure 1 The compression section is shown in a three-dimensional view.

[0051] Figure 3 It is assembly Figure 2 The compression section is shown in a top view.

[0052] Figure 4 It is decomposition Figure 1A three-dimensional view of a portion of the compressed section, viewed from above.

[0053] Figure 5 It is assembly Figure 4 A three-dimensional view of a portion of the compressed section, viewed from below.

[0054] Figure 6 It is assembly Figure 1 The compressed portion is shown in a cross-sectional view.

[0055] Figure 7 It is used for explanation Figure 1 A schematic diagram showing the effect of the oil supply hole in the middle.

[0056] Figure 8 As a comparison Figure 1 The curves shown are based on the effect of the oil supply hole and existing technology. Figure 8 (a) in the figure is a graph illustrating the prior art. Figure 8 (b) in the figure is a graph illustrating this embodiment.

[0057] Figure 9 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0058] Figure 10 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0059] Figure 11 yes Figure 10 A cross-sectional view of line "Ⅳ-Ⅳ".

[0060] Figure 12 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0061] Figure 13 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0062] Figure 14 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0063] Figure 15 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0064] Figure 16 In order to explain Figure 1 Another embodiment of the oil supply hole is shown in a cross-sectional view of a portion of the compression section.

[0065] Figure 17 It is assembly Figure 16 A portion of the compressed section is shown in a cross-sectional view.

[0066] Figure 18 It is shown Figure 17 A partial plan view of the cross section along line "V-V". Detailed Implementation

[0067] Hereinafter, a rotary vane compressor of the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings. For reference, the oil supply port of the present invention can be equally applied to a rotary vane compressor in which vanes are slidably inserted into rollers. For example, it can be applied not only to examples where the vane slots are formed obliquely, as in this embodiment, but also to examples where the vane slots are formed radially. Hereinafter, an example where the vane slots are formed obliquely on the rollers and the inner circumferential surface of the cylinder is an asymmetrical elliptical shape will be described as a representative example.

[0068] Figure 1 This is a cross-sectional view illustrating an embodiment of the rotary vane compressor of 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.

[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 will be described with a focus on the vertical type.

[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.

[0072] The drive motor 120 and the compressor unit 130 can be inserted into and fixedly connected to the intermediate housing 111. The suction pipe 115 passes through the intermediate housing 111 and is directly connected to the compressor unit 130. The lower housing 112 can be sealed to the lower end of the intermediate housing 111. An oil storage space 110b for storing oil supplied to the compressor unit 130 can be formed on the lower side of the compressor unit 130. The upper housing 113 can be 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.

[0073] The drive motor 120 is a component of the electric motor unit, which provides power for driving the compressor 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 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 110a.

[0075] The rotor 122 is inserted into the stator 121 in a rotatable manner, and the rotating shaft 123 is pressed into the center of the rotor 122. Thus, the rotating shaft 123 will rotate concentrically with the rotor 122.

[0076] 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 second bearing portion 1322. The first oil through hole 126a and the second oil through hole 126b can each be formed as one, or they can each be formed as multiples. This embodiment shows an example where multiple are formed.

[0077] An oil pump 127 may be provided at the middle or lower end of the oil flow path 125. The oil pump 127 may be a gear pump, a viscous pump, a centrifugal pump, etc. In this embodiment, an example using a centrifugal pump is shown. Thus, when the rotating shaft 123 rotates, the oil filling the oil storage space 110b of the housing 110 can be pumped by the oil pump 127. As the oil is pumped up along the oil flow path 125, it can be supplied to the secondary bearing surface 1322b of the secondary bushing portion 1322 through the second oil through hole 126b, and to the main bearing surface 1312b of the main bushing portion 1312 through the first oil through hole 126a.

[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, 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 to divide the compression space V into a plurality of compression chambers.

[0079] Reference Figures 1 to 3 The main bearing 131 can be fixedly disposed in the intermediate outer shell 111 of the housing 110. For example, the main bearing 131 can be inserted into and welded to the intermediate outer shell 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, supporting the top surface of the roller 134 axially and the upper half of the rotating shaft 123 radially.

[0081] 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. 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.

[0082] The main board portion 1311 is formed in a disc shape, and its outer peripheral surface can be tightly attached to the inner peripheral surface of the intermediate outer casing 111 for fixation. At least one or more discharge ports 1313a, 1313b, and 1313c are formed on 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 are provided on the top surface of the main board portion 1311. A discharge silencer 137 may be provided on the upper side of the main board portion 1311. The discharge silencer 137 may have a discharge space (not marked) to accommodate the discharge ports 1313a, 1313b, and 1313c and the discharge valves 1361, 1362, and 1363. The discharge ports will be described again later.

[0083] On the two axial sides of the main board 1311, a first main back pressure cavity 1315a and a second main back pressure cavity 1315b can be formed on the bottom surface of the top surface of the main board 1311 facing the roller 134.

[0084] The first main back pressure cavity 1315a and the second main back pressure cavity 1315b can be formed in an arc shape and separated by a predetermined interval along the circumference. The inner circumferential surfaces of the first main back pressure cavity 1315a and the second main back pressure cavity 1315b can be formed in a circular shape, while the outer circumferential surfaces can be formed in an elliptical shape, taking into account the blade groove described later.

[0085] The first main back pressure chamber 1315a and the second main back pressure chamber 1315b can be formed within the outer diameter range of the roller 134. Thus, the first main back pressure chamber 1315a and the second main back pressure chamber 1315b can be separated from the compression space V. However, the first main back pressure chamber 1315a and the second main back pressure chamber 1315b can be slightly connected through a gap between their two sides, unless a separate sealing member is provided between the bottom surface of the main plate portion 1311 and the top surface of the roller 134 facing the main plate portion 1311.

[0086] The first main back pressure chamber 1315a forms a pressure lower than that of the second main back pressure chamber 1315b, for example, an intermediate pressure between the suction pressure and the discharge pressure. In the first main back pressure chamber 1315a, oil (refrigerant oil) can flow into the first main back pressure chamber 1315a through a small passage between the first main bearing protrusion 1316a and the top surface 134a of the roller 134 (described later). The first main back pressure chamber 1315a can be formed within the compression chamber that constitutes the intermediate pressure in the compression space V. Thus, the first main back pressure chamber 1315a maintains an intermediate pressure.

[0087] The second main back pressure chamber 1315b forms a pressure higher than that of the first main back pressure chamber 1315a, such as the discharge pressure or an intermediate pressure between the suction pressure and the discharge pressure, close to the discharge pressure. Oil flowing into the main bearing bore 1312a of the main bearing 131 through the first oil passage 126a can flow into the second main back pressure chamber 1315b. The second main back pressure chamber 1315b can be formed within the compression chamber that constitutes the discharge pressure in the compression space V. Thus, the second main back pressure chamber 1315b maintains the discharge pressure.

[0088] Furthermore, on the inner circumferential sides of the first main back pressure chamber 1315a and the second main back pressure chamber 1315b, the first main bearing protrusion 1316a and the second main bearing protrusion 1316b can respectively extend from the main bearing surface 1312b of the main bushing portion 1312. Thus, the first main back pressure chamber 1315a and the second main back pressure chamber 1315b can be sealed from the outside while the rotating shaft 123 can be stably supported.

[0089] The first main bearing protrusion 1316a and the second main bearing protrusion 1316b can be formed at the same height or at different heights.

[0090] For example, when the first main bearing protrusion 1316a and the second main bearing protrusion 1316b are formed at 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. This allows high-pressure oil (refrigerant oil) flowing into the inner side of the main bearing surface 1312b to flow into the second main back pressure chamber 1315b through the oil communication groove (not shown) or the oil communication hole (not shown).

[0091] Conversely, 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 lower than the height of the first main bearing protrusion 1316a. This allows high-pressure oil (refrigerant oil) flowing into the inside of the main bearing bore 1312a to pass over the second main bearing protrusion 1316b and flow into the second main back pressure chamber 1315b.

[0092] On the other hand, 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 can be formed between the upper and lower ends of the main bushing portion 1312 in a straight line or oblique line, and communicate with the first oil through hole 126a.

[0093] Reference Figures 1 to 3 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, and supports the bottom surface of the roller 134 axially while supporting the lower half of the rotating shaft 123 radially.

[0094] 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.

[0095] The sub-plate 1321 can be formed into a disc 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.

[0096] On the two axial sides of the sub-plate portion 1321, the top surface of the sub-plate portion 1321 facing the bottom surface of the roller 134 may form a first sub-back pressure cavity 1325a and a second sub-back pressure cavity 1325b.

[0097] The first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b can be symmetrically formed with the first main back pressure chamber 1315a and the second main back pressure chamber 1315b respectively with the roller 134 as the center.

[0098] For example, the first secondary back pressure cavity 1325a can be formed symmetrically with the first main back pressure cavity 1315a, and the second secondary back pressure cavity 1325b can be formed symmetrically with the second main back pressure cavity 1315b. Thus, a first secondary bearing protrusion 1326a can be formed on the inner circumferential side of the first secondary back pressure cavity 1325a, and a second secondary bearing protrusion 1326b can be formed on the inner circumferential side of the second secondary back pressure cavity 1325b.

[0099] The descriptions of the first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b, the first secondary bearing protrusion 1326a and the second secondary bearing protrusion 1326b are used instead of the descriptions of the first main back pressure chamber 1315a and the second main back pressure chamber 1315b, the first main bearing protrusion 1316a and the second main bearing protrusion 1316b.

[0100] However, depending on the circumstances, the first secondary back pressure cavity 1325a and the second secondary back pressure cavity 1325b can be formed asymmetrically with respect to the first primary back pressure cavity 1315a and the second primary back pressure cavity 1315b, respectively, with the roller 134 as the center. For example, the first secondary back pressure cavity 1325a and the second secondary back pressure cavity 1325b can be formed to be deeper than the first primary back pressure cavity 1315a and the second primary back pressure cavity 1315b.

[0101] Additionally, an oil supply hole 1327, described later, may be formed between the first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b, or more precisely, between the first secondary bearing protrusion 1326a and the second secondary bearing protrusion 1326b or at the portion where the first secondary bearing protrusion 1326a and the second secondary bearing protrusion 1326b are connected to each other.

[0102] For example, the first end of the inlet 1327a constituting the oil supply hole 1327 is formed to be immersed in the oil storage space 110b, and the second end of the outlet 1327b constituting the oil supply hole 1327 is formed to be located on the rotation path of the back pressure chambers 1343a, 1343b, and 1343c, which are described later, on the top surface of the sub-plate portion 1321 facing the bottom surface of the roller 134. Thus, when the roller 134 rotates, the back pressure chambers 1343a, 1343b, and 1343c can periodically communicate with the oil supply hole 1327, and a portion of the oil stored in the oil storage space 110b can be periodically supplied to the back pressure chambers 1343a, 1343b, and 1343c through the oil supply hole 1327. As a result, each blade 1351, 1352, and 1353 can be stably supported toward the inner circumferential surface 1332 of the cylinder 133. The oil supply port 1327 will be explained again later.

[0103] On the other hand, the secondary bushing portion 1322 can be formed as a hollow bushing shape, and an oil groove 1322c 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 1322c can be formed as a straight line or an oblique line between the upper and lower ends of the secondary bushing portion 1322 and communicate with the second oil passage hole 126b of the rotating shaft 123.

[0104] Although not shown in the accompanying drawings, the back pressure cavities 1315a, 1315b, 1325a, and 1325b may also be formed on either side of the main bearing 131 or the secondary bearing 132.

[0105] On the other hand, as described 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 through the cylinder 133 between the inner and outer circumferential surfaces. This embodiment will be described with an example in which the discharge port 1313 is formed in the main bearing 131.

[0106] The discharge port 1313 may be formed as a single port. However, in this embodiment, the discharge port 1313 may be formed as a plurality of discharge ports 1313a, 1313b, and 1313c at a predetermined interval along the compression direction (or the rotation direction of the roller).

[0107] Typically, in a rotary vane compressor, with the roller 134 eccentrically positioned relative to the compression space V, a near-contact point P1 is created between the outer circumferential surface 1341 of the roller 134 and the inner circumferential surface 1332 of the cylinder 133, and the discharge port 1313 is formed near this near point P1. Therefore, the closer the compression space V is to the near point P1, the greater 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 a suitable discharge port area.

[0108] Therefore, similar to this embodiment, the discharge port 1313 can be divided into a plurality of discharge ports 1313a, 1313b, and 1313c and formed along the rotation direction (or compression direction) of the roller 134. Furthermore, although the plurality of discharge ports 1313a, 1313b, and 1313c can each be formed as one, they can also be formed in pairs, as in this embodiment.

[0109] For example, in this embodiment, the discharge outlets 1313 can be arranged from the discharge outlets closest to the proximal portion 1332a in the order of first discharge outlet 1313a, second discharge outlet 1313b, and third discharge outlet 1313c. The interval between the first discharge outlet 1313a and the second discharge outlet 1313b and / or the interval between the second discharge outlet 1313b and the third discharge outlet 1313c can be formed approximately in the same manner as the interval between preceding and subsequent blades, that is, the circumferential length of each compression chamber is similar.

[0110] For example, the interval between the first discharge port 1313a and the second discharge port 1313b, and the interval between the second discharge port 1313b and the third discharge port 1313c, can be formed identically to each other. The first interval and the second interval can be formed to be approximately the same as the circumferential length of the first compression chamber V1, the circumferential length of the second compression chamber V2, and the circumferential length of the third compression chamber V3. Thus, a compression chamber will not be connected to a plurality of discharge ports 1313, or a discharge port 1313 will not be connected to a plurality of compression chambers, but the first compression chamber V1 can be connected to the first discharge port 1313a, the second compression chamber V2 can be connected to the second discharge port 1313b, and the third compression chamber V3 can be connected to the third discharge port 1313c.

[0111] However, similar to this embodiment, when the blade grooves 1342a, 1342b, and 1342c described later are formed at non-equal intervals, the circumferential lengths of each compression chamber V1, V2, and V3 are formed to be different from each other, and one compression chamber may be connected to a plurality of discharge ports or one discharge port may be connected to a plurality of compression chambers.

[0112] Furthermore, 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 direction (the rotation direction of the rollers). This allows any refrigerant not discharged from the preceding compression chamber to be guided through the discharge groove 1314 to the discharge port 1313, which communicates with the following compression chamber, and discharged together with the compressed refrigerant in that chamber. This minimizes the amount of residual refrigerant in the compression space V, thereby suppressing overcompression and improving compressor efficiency.

[0113] As described above, the discharge groove 1314 can ultimately be formed to extend from the discharge port (e.g., a 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 either side by a proximal portion (proximal point) 1332a. Therefore, considering the seal between the intake and discharge chambers, the discharge port 1313 cannot overlap with the proximal point P1 located at the proximal portion 1332a. Consequently, a residual space S is formed circumferentially between the proximal point P1 and the discharge port 1313, separating the inner circumferential surface 1332 of the cylinder 133 from the outer circumferential surface 1341 of the roller 134. Refrigerant ultimately cannot be discharged through the discharge port 1313 and remains in this residual space S. The residual refrigerant eventually causes the pressure in the compression chamber to rise, leading to a decrease in compression efficiency due to overcompression.

[0114] However, as in this embodiment, when the discharge trough 1314 eventually extends from the discharge port 1313 to the residual space S, the refrigerant remaining in the residual space S will eventually flow back to the discharge port 1313 through the discharge trough 1314 and be additionally discharged, thereby effectively suppressing the reduction in compression efficiency caused by overcompression in the compression chamber.

[0115] Although not shown in the accompanying drawings, a residual discharge hole may also be formed in the residual space S, in addition to the discharge groove 1314. The inner diameter of the residual discharge hole is smaller than the inner diameter of the discharge outlet, and the residual discharge hole may be formed differently from the discharge outlet so that it is always open without the use of a discharge valve to open and close.

[0116] Furthermore, the plurality of discharge ports 1313a, 1313b, 1313c can be opened and closed using each of the aforementioned discharge valves 1361, 1362, 1363. Each discharge valve 1361, 1362, 1363 can be configured as a cantilever type reed valve, with one end being a fixed end and the other end being a free end. Such discharge valves 1361, 1362, 1363 are well known in conventional rotary compressors, and therefore their specific descriptions are omitted.

[0117] Reference Figures 1 to 3 In this embodiment, the cylinder 133 can also be tightly attached to the bottom surface of the main bearing 131 and fastened to the main bearing 131 together with the auxiliary bearing 132 using bolts. Thus, the cylinder 133 can be fixedly connected to the housing 110 using the main bearing 131.

[0118] The cylinder 133 can be formed as an annular shape with an empty space to form a compression space V in the center. The empty space can be sealed by the main bearing 131 and the secondary bearing 132 to form the compression space V described above, in which the roller 134 described later can be rotatably coupled.

[0119] In cylinder 133, the intake port 1331 can be formed by penetrating from the outer peripheral surface to the inner peripheral surface. However, the intake port can also be formed by penetrating the main bearing 131 or the secondary bearing 132.

[0120] The intake port 1331 can be formed on one side of the circumferential direction with the proximal point P1 as described later. The discharge port 1313 described above can be formed on the main bearing 131 on the other side of the circumferential direction opposite to the intake port 1331 centered on the proximal point P1.

[0121] 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 into a plurality of ellipses. For example, four ellipses with different aspect ratios can be combined to form an asymmetrical elliptical shape with two origins.

[0122] Specifically, the inner circumferential surface 1332 of the cylinder 133 in this embodiment can be formed to have a first point O, which serves as the rotation center (axis center or outer diameter center of the cylinder) of the roller 134 described later, and a second point O′ that is inclined toward the near point P1 relative to the first point O.

[0123] The XY plane centered on the first point O forms the third quarter plane Q3 and the fourth quarter plane Q4, and the XY plane centered on the second point O′ forms the first quarter plane Q1 and the second quarter plane Q2. The third quarter plane Q3 is formed by the third ellipse, the fourth quarter plane Q4 is formed by the fourth ellipse, the first quarter plane Q1 is formed by the first ellipse, and the second quarter plane Q2 is formed by the second ellipse.

[0124] In addition, 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 farthest 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.

[0125] The proximal portion 1332a can be defined as the proximal point P1. The first quarter surface Q1 and the fourth quarter surface Q4 can be distinguished with the proximal portion 1332a as the center. On both sides centered on the proximal portion 1332a, an intake port 1331 can be formed on the first quarter surface Q1, and an exhaust port 1313 can be formed on the fourth quarter surface Q4. Therefore, when the blades 1351, 1352, and 1353 pass the proximal point P1, the compression surfaces on the rotational direction side of the rollers 1351, 1352, and 1353 will be subjected to a low-pressure intake pressure, while the compression surfaces on the opposite side will be subjected to a high-pressure exhaust pressure. Therefore, during the process of the roller 134 passing the near point P1, it will be subjected to the maximum variable pressure between the front end faces 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 end faces 1351b, 1352b, 1353b of each blade 1351, 1352, 1353 that are facing the back pressure chambers 1343a, 1343b, 1343c, which may result in a large vibration phenomenon of the blades 1351, 1352, 1353.

[0126] Therefore, in this embodiment, the back pressure chambers 1343a, 1343b, and 1343c may also be provided with oil supply ports 1327 capable of supplying high-pressure (discharge pressure or a pressure similar to discharge pressure) oil stored in the oil storage space 110b. The oil supply ports 1327 will be described again later.

[0127] Reference Figures 1 to 3 Rollers 134 are rotatably disposed in the compression space V of the cylinder 133. A plurality of blades 1351, 1352, and 1353, described later, can be inserted into the rollers 134 at predetermined intervals along the circumferential direction. Thus, the compression space V can be divided into compression chambers corresponding to the number of blades 1351, 1352, and 1353. In this embodiment, the example of three blades 1351, 1352, and 1353, dividing the compression space V into three compression chambers, will be described in detail.

[0128] In this embodiment, the outer peripheral surface 1341 of the roller 134 can be formed as a circle, and the rotating shaft 123 can extend from the rotation center Or of the roller 134 as a single unit or be subsequently assembled and combined with the rotation center Or of the roller 134. Thus, the rotation center Or of the roller 134 can be located on the same axis as the axis center (not marked) of the rotating shaft 123, and the roller 134 and the rotating shaft 123 can rotate concentrically together.

[0129] However, as described above, since the inner circumferential surface 1332 of the cylinder 133 is formed into an asymmetrical elliptical shape inclined in a specific direction, the rotation center Or of the roller 134 can be eccentrically positioned relative to the outer diameter center (Oc) of the cylinder 133. As a result, one side of the outer circumferential surface 1341 of the roller 134 is in near contact with the inner circumferential surface 1332 of the cylinder 133, specifically, the proximal portion 1332a, forming a proximal point P1.

[0130] As described above, the near point P1 can be formed at the near portion 1332a. Thus, the assumed line passing through the near point P1 can correspond to the minor axis of the elliptic curve constituting the inner circumferential surface 1332 of the cylinder 133.

[0131] In addition, a suitable number of multiple blade grooves 1342a, 1342b, and 1342c are formed on the outer peripheral surface 1341 of the roller 134 along the circumferential direction. The multiple blades 1351, 1352, and 1353 described later can be slidably inserted into and engaged with each blade groove 1342a, 1342b, and 1342c, respectively.

[0132] A plurality of blade grooves 1342a, 1342b, and 1342c can be defined as the first blade groove 1342a, the second blade groove 1342b, and the third blade groove 1342c along the direction of compression (the direction of rotation of the roller). The first blade groove 1342a, the second blade groove 1342b, and the third blade groove 1342c can be formed identically to each other along the circumferential direction at equal or unequal intervals.

[0133] For example, multiple blade grooves 1342a, 1342b, and 1342c can be formed at a predetermined angle relative to the radial direction, thus sufficiently 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, even if the distance from the outer circumferential surface 1341 of the roller 134 to the inner circumferential surface 1332 of the cylinder 133 increases, it is possible to prevent blades 1351, 1352, and 1353 from detaching from the blade grooves 1342a, 1342b, and 1342c, thereby increasing the design freedom of the inner circumferential surface 1332 of the cylinder 133.

[0134] Preferably, the inclination direction of the blade grooves 1342a, 1342b, and 1342c is opposite to the rotation direction of the roller 134. That is, the front end faces 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 is beneficial to pull the compression start angle toward the rotation direction of the roller 134 so that compression can start more quickly.

[0135] On the other hand, the inner ends of the blade slots 1342a, 1342b, and 1342c can be configured to communicate with the back pressure chambers 1343a, 1343b, and 1343c, respectively. The back pressure chambers 1343a, 1343b, and 1343c serve as spaces for accommodating oil (or refrigerant) at discharge or intermediate pressure towards the rear side of each blade 1351, 1352, and 1353, i.e., the rear ends 1351c, 1352c, and 1353c of the blades. The pressure of the oil (or refrigerant) filling the back pressure chambers 1343a, 1343b, and 1343c can pressurize each blade 1351, 1352, and 1353 towards the inner circumferential surface of the cylinder 133. For ease of explanation, the direction towards the cylinder can be defined as forward, and the opposite side as rearward, based on the blade's direction of movement.

[0136] The back pressure chambers 1343a, 1343b, and 1343c can be configured to be sealed by the main bearing 131 and the auxiliary bearing 132, respectively. The back pressure chambers 1343a, 1343b, and 1343c can also be configured to be individually connected to each of the back pressure chambers 1315a, 1315b, 1325a, and 1325b, or they can be configured to be interconnected using the back pressure chambers 1315a, 1315b, 1325a, and 1325b.

[0137] Reference Figures 1 to 3 In this embodiment, a plurality of blades 1351, 1352, and 1353 can be slidably inserted into each blade slot 1342a, 1342b, and 1342c. Thus, the plurality of blades 1351, 1352, and 1353 can be formed to have a shape substantially the same as each blade slot 1342a, 1342b, and 1342c.

[0138] For example, a plurality of blades 1351, 1352, and 1353 can be defined as first blade 1351, second blade 1352, and third blade 1353 along the rotation direction of roller 134. First blade 1351 can be inserted into first blade groove 1342a, second blade 1352 can be inserted into second blade groove 1342b, and third blade 1353 can be inserted into third blade groove 1342c.

[0139] Multiple blades 1351, 1352, and 1353 can be formed in approximately the same shape.

[0140] Specifically, the plurality of blades 1351, 1352, and 1353 can be formed into approximately rectangular hexahedrons, the front end faces 1351a, 1352a, and 1353a that contact the inner circumferential surface 1332 of the cylinder 133 can be formed into curves, and the rear end faces 1351b, 1352b, and 1353b that face each back pressure chamber 1343a, 1343b, and 1343c can be formed into straight surfaces.

[0141] In a rotary vane compressor having a composite cylinder as described above, when power is applied to the drive motor 120, the rotor 122 of the drive motor 120 and the rotating shaft 123 coupled with the rotor 122 rotate, and the roller 134 coupled with or integrally formed with the rotating shaft 123 rotates together with the rotating shaft 123.

[0142] Thus, the plurality of blades 1351, 1352, 1353 are drawn out from their respective blade slots 1342a, 1342b, 1342c and come into contact with the inner circumferential surface 1332 of the cylinder 133 by the centrifugal force generated by the rotation of the roller 134 and the back pressure of the back pressure chambers 1343a, 1343b, 1343c supporting the rear end faces 1351b, 1351b, 1351c of the blades 1351, 1352, 1353 using the back pressure of the back pressure chambers 1343a, 1343b, 1343c of the blades 1351, 1352, 1353.

[0143] Thus, the following series of processes are repeated: 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 with the rotation of the roller 134 and changes its volume by the shape of the inner circumferential surface 1332 of the cylinder 133 and the eccentricity of the roller 134. The refrigerant drawn into its respective compression chamber V1, V2, V3 is compressed and discharged into the internal space of the housing 110 as the roller 134 and blades 1351, 1352, 1353 move.

[0144] On the other hand, as described above, in the rotary compressor of this embodiment, the leading edge face of each blade receives both compression pressure and suction pressure simultaneously in the interval from the proximal point between the cylinder and the rollers to the suction inlet. Consequently, each blade may experience blade vibration due to pressure unevenness within this interval. Such blade vibration can lead to leakage between the compression chambers, resulting in suction and compression losses, and generating collision noise and vibration between the cylinder and the blades. This can further exacerbate suction and compression losses caused by wear on the cylinder or blades.

[0145] Therefore, in this embodiment, the blades can be prevented from being pushed backward by increasing the back pressure of the back pressure chamber, thereby suppressing blade vibration. For example, an oil supply port can be provided in the back pressure chamber to directly supply high-pressure oil stored in the oil reservoir. The oil supply port can be formed through the main bearing or the auxiliary bearing. Hereinafter, the example of an oil supply port formed through the auxiliary bearing will be described, but it is not limited to the auxiliary bearing.

[0146] Figure 4 It is decomposition Figure 1A three-dimensional view of a portion of the compression section, viewed from above. Figure 5 It is assembly Figure 4 A perspective view of a portion of the compression section, viewed from below. Figure 6 It is assembly Figure 1 The compression section is shown in the cross-sectional view. Figure 7 It is used for explanation Figure 1 A schematic diagram showing the effect of the oil supply hole in the middle.

[0147] Refer again Figure 3 As described above, the secondary bearing 132 in this embodiment includes a secondary plate portion 1321 and a secondary bushing portion 1322. The secondary plate portion 1321 is formed in the shape of an annular disk, and the secondary bushing portion 1322 is formed in the shape of a cylinder extending from the center of the secondary plate portion 1321 toward the oil storage space 110b.

[0148] The first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b, which have different pressures as described above, are formed on one side of the secondary plate portion 1321, that is, the top surface facing the roller 134, separated by a predetermined interval in the circumferential direction.

[0149] The first secondary back pressure chamber 1325a communicates with the first main back pressure chamber 1315a of the main bearing 131 through each of the back pressure chambers 1343a, 1343b, and 1343c. The second secondary back pressure chamber 1325b communicates with the second main back pressure chamber 1315b of the main bearing 1311 through each of the back pressure chambers 1343a, 1343b, and 1343c. In other words, the first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b are formed on an assumed circle C connecting each of the back pressure chambers 1343a, 1343b, and 1343c. Thus, the first secondary back pressure chamber 1315a, 1325a and the second secondary back pressure chamber 1315b, 1325b can alternately communicate with each of the back pressure chambers 1343a, 1343b, and 1343c when the roller 134 rotates. Therefore, the outlet 1327b of the oil supply port 1327 described later is located between the first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b, or more precisely, on the assumed circle C connecting each back pressure chamber 1343a, 1343b, and 1343c.

[0150] Reference Figures 4 to 7 In this embodiment, the lower end face of the secondary bushing portion 1322 can extend toward the bottom surface of the oil storage space 110b, that is, the bottom surface of the lower outer casing 112. A secondary bearing hole 1322a can be formed in the central portion of the secondary bushing portion 1322, and an oil groove can be formed on the inner circumferential surface of the secondary bearing hole 1322a. Figure 5 (As shown) 1322c.

[0151] An oil supply hole 1327 can be formed on the lower end face of the sub-blade portion 1322, extending through the top surface of the sub-plate portion 1321. For example, the oil supply hole 1327 can be formed between the lower end face of the sub-blade portion 1322 and the top surface of the sub-plate portion 1321.

[0152] As described above, the inlet 1327a, which forms the first end of the oil supply hole 1327, can be formed by penetrating the lower end face of the secondary bushing portion 1322. Thus, the lower end of the oil supply hole 1327 is deeply disposed in the oil storage space 110b, and even in abnormal operation, oil can be stably supplied to the rear end faces 1351b, 1352b, and 1353b of the blades 1351, 1352, and 1353.

[0153] However, the lower end of the inlet 1327a constituting the oil supply hole 1327 can also be formed by penetrating the outer peripheral surface of the secondary bushing portion 1322. In other words, the inlet 1327a of the oil supply hole 1327 can be formed at any position immersed in the oil in the oil storage space 110b.

[0154] As described above, the outlet 1327b of the oil supply port 1327 can be formed between the first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b. Specifically, the outlet 1327b of the oil supply port 1327 can be formed at the position of the front end faces 1351a, 1352a, 1353a of the corresponding blades 1351, 1352, 1353 through the variation range α from the proximal point P1 to the suction port 1331, and at the rear side of the blade grooves 1342a, 1342b, 1342c into which the blades 1351, 1352, 1353 are inserted, that is, at the position communicating with the corresponding back pressure chambers 1343a, 1343b, 1343c. From the perspective of crankshaft rotation angle, when the proximal point P1 is 0°, the variation range α can be formed in the range of approximately 300° to 350°.

[0155] The inner diameter D1 of the oil supply port 1327 can be formed to be approximately the same size as or smaller than the inner diameter D2 of the back pressure chambers 1343a, 1343b, and 1343c. For example, the inner diameter D1 of the oil supply port 1327 can be formed to be the same inner diameter from the inlet 1327a to the outlet 1327b of the oil supply port 1327, and the outlet 1327b of the oil supply port 1327 can be formed to be smaller than or equal to the inner diameter D2 of the back pressure chambers 1343a, 1343b, and 1343c. Thus, the outer diameter of the secondary bushing portion 1322 can be maintained while the oil supply port 1327 is formed in the secondary bushing portion 1322.

[0156] As described above, when an oil supply hole 1327 directly communicating with the oil storage space 110b is formed between the first secondary back pressure chamber 1325a and the second secondary back pressure chamber 1325b, when the blades 1351, 1352, and 1353 pass through the variation range α between the proximal point P1 and the suction port 1331, high-pressure oil can be supplied to the rear end faces 1351b, 1352b, and 1353b of the blades 1351, 1352, and 1353 to suppress the blade vibration phenomenon caused by insufficient back pressure.

[0157] In other words, based on the rotation direction of roller 134, a pre-set interval β is created between the rear end of the second secondary back pressure chamber 1325b, which forms an intermediate pressure similar to or close to the discharge pressure, and the front end of the first secondary back pressure chamber 1325a, which faces it and forms an intermediate pressure less than the discharge pressure. This interval β generates the aforementioned variation interval α or exacerbates the vibration phenomenon of blades 1351, 1352, and 1353.

[0158] Within the partition β, the leading edge faces 1351a, 1352a, and 1353a of blades 1351, 1352, and 1353 are subjected to suction pressure on the side facing the rotation direction and discharge pressure on the opposite side facing the rotation direction, resulting in unstable pressure. At this time, the trailing edge faces 1351b, 1352b, and 1353b of blades 1351, 1352, and 1353 are in a state of passing through the partition β and are subjected to back pressure less than the discharge pressure, thus failing to sufficiently suppress the rearward pressure on the leading edge faces 1351a, 1352a, and 1353a of blades 1351, 1352, and 1353. As a result, the blades 1351, 1352, and 1353 will be repeatedly pushed towards the back pressure chambers 1343a, 1343b, and 1343c and then pushed towards the inner circumferential surface 1332 of the cylinder 133, which may cause the blades 1351, 1352, and 1353 to vibrate.

[0159] However, as in this embodiment, with the formation of an oil supply port 1327 communicating with the oil storage space 110b in the partition β, high-pressure oil can be supplied from the partition β to the back pressure chambers 1343a, 1343b, and 1343c. Thus, when the blades 1351, 1352, and 1353 pass between the proximal point P1 and the suction port 1331, high-pressure oil is supplied to the rear end faces 1351b, 1352b, and 1353b of the blades 1351, 1352, and 1353, increasing the back pressure and thereby suppressing the vibration of the blades 1351, 1352, and 1353.

[0160] Furthermore, since both ends of the oil supply port 1327 in this embodiment are directly connected between the oil storage space 110b and the back pressure chambers 1343a, 1343b, and 1343c, oil from the oil storage space 110b can be rapidly supplied to the back pressure chambers 1343a, 1343b, and 1343c when the compressor restarts. This effectively suppresses the vibration of the blades 1351, 1352, and 1353 that occurs when the compressor restarts.

[0161] Figure 8 As a comparison Figure 1 The curves shown are based on the effect of the oil supply hole and existing technology. Figure 8 (a) in the figure is a graph illustrating the prior art. Figure 8 (b) in the figure is a graph illustrating this embodiment.

[0162] Reference Figure 8 As can be seen, with the same oil supply hole as in this embodiment, the initial start-up time and compression formation time are shortened compared to existing rotary compressors without oil supply holes.

[0163] Reference Figure 8 As can be seen from (a), under the existing technology, the formation of intake pressure and exhaust pressure is delayed by more than five minutes. This indicates that the vibration of the blades near the point causes continuous pressure leakage between the two compression chambers (intake and exhaust chambers), thus delaying the formation of intake and exhaust pressure.

[0164] Conversely, refer to Figure 8 As can be seen from (b), in this embodiment, compared to the prior art, the formation of intake pressure and exhaust pressure begins to occur in approximately one minute. This indicates that the vibration of the blades near the point of contact is improved, reducing pressure leakage between the two compression chambers (intake and exhaust chambers), thereby allowing the formation of intake pressure and exhaust pressure to begin and complete rapidly.

[0165] Additionally, refer to Figure 8 As can be seen from (a), in the prior art, the input increases sharply approximately five minutes after startup. This can be interpreted as initial startup occurring approximately five minutes after startup. Ultimately, the prior art suffers from poor initial startup.

[0166] Conversely, refer to Figure 8 As can be seen from (b), in the case of this embodiment, input is added within 30 seconds after the start of operation, thereby rapidly forming an initial startup compared to the prior art.

[0167] Thus, in the rotary compressor of this embodiment, the vibration phenomenon that occurs when the blades are separated from the cylinder and then re-engage due to the pressure difference between the front and rear ends during operation can be suppressed. In particular, by effectively suppressing the more severe blade vibration that may occur during the initial start-up of the compressor, poor initial start-up can be prevented and compressor efficiency can be improved. Furthermore, when applied to a heater / cooler, it can quickly achieve cooling and heating effects.

[0168] Furthermore, in the rotary compressor of this embodiment, wear on the inner circumferential surface of the cylinder or the leading edge surface of the blades near the near point is suppressed by suppressing the vibration phenomenon of the blades around the near point. As a result, not only may vibration noise in specific parts increase, but leakage between compression chambers may also occur, leading to a decrease in compression efficiency.

[0169] Furthermore, in the rotary compressor of this embodiment, pressure pulsation at the rear end face of the blades can be suppressed by making the pressure of the oil supplied to the rear end face of the blades uniform. Therefore, blade vibration can be suppressed more effectively by making the back pressure formed on the rear end face of the blades constant.

[0170] Furthermore, in the rotary compressor of this embodiment, when using high-pressure refrigerants such as R32, R410a, and CO2, the above-mentioned effects can be further expected.

[0171] On the other hand, another embodiment of the oil supply port is as follows.

[0172] That is, in the above embodiments, the inner diameter of the oil supply hole is formed in the same way along the length direction, but depending on the situation, the inner diameter of the oil supply hole may be formed differently along the length direction.

[0173] Figure 9 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0174] Reference Figure 9 In this embodiment, the inner diameter D1 of the oil supply hole 1327 can be formed differently along the length direction. For example, in the oil supply hole 1327, the inner diameter (D12) of the upper half constituting the outlet 1327b can be larger than the inner diameter D11 of the lower half constituting the inlet 1327a.

[0175] Specifically, in the oil supply port 1327, the lower end (inlet end) of the inlet 1327a can be formed into a first inner diameter D11, and the upper end (outlet end) of the outlet 1327b can be formed into a second inner diameter D12. The second inner diameter D12 can be larger than the first inner diameter D11.

[0176] Although not shown in the accompanying drawings, the inner circumferential surface of the oil supply hole 1327 may also be formed as an ellipse or rectangle instead of a circle. In this case, the cross-sectional area of ​​the upper half constituting the outlet 1327b may be larger than the cross-sectional area of ​​the lower half constituting the inlet 1327a.

[0177] As described above, the inner diameters (or cross-sectional areas) D11 and D12 of the oil supply port 1327 are formed differently along the length direction. When the inner diameter (or cross-sectional area) D11 of the lower half constituting the inlet 1327a is larger than the inner diameter (or cross-sectional area) D12 of the upper half constituting the outlet 1327b, the volume of the upper half adjacent to the back pressure chambers 1343a, 1343b, and 1343c is formed relatively large. As a result, by generating a differential pressure inside the oil supply port 1327, the oil in the oil storage space 110b can move more rapidly towards the back pressure chambers 1343a, 1343b, and 1343c along the oil supply port 1327.

[0178] On the other hand, another embodiment of the oil supply port is as follows.

[0179] That is, in the above embodiment, the oil supply port is formed to be separated from the back pressure chambers on both sides, but depending on the situation, the oil supply port can be formed to be connected to either of the back pressure chambers on both sides.

[0180] Figure 10 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port. Figure 11 yes Figure 10 A cross-sectional view of line "Ⅳ-Ⅳ".

[0181] Reference Figure 10 and Figure 11 In this embodiment, the oil supply hole 1327 can be formed in a similar manner to that in the embodiment described above. For example, the oil supply hole 1327 can be formed through the secondary bushing portion 1322, but the upper end constituting the outlet 1327b can be formed between the rear end of the second secondary back pressure chamber 1325b and the front end of the first secondary back pressure chamber 1325a.

[0182] In this case, the inner diameter D1 of the oil supply hole 1327 can also be formed in the same way, and the inner diameter of the upper half constituting the outlet 1327b can also be larger than the inner diameter of the lower half constituting the inlet 1327a. This embodiment is described using the case where the inner diameter D1 of the oil supply hole 1327 is the same as an example.

[0183] However, in this embodiment, taking the rotation direction of the roller 134 as a reference, a connecting groove 1328 can also be formed between the rear end side of the second auxiliary back pressure chamber 1325b and the upper end side of the oil supply hole 1327 facing it in the circumferential direction. Thus, the oil supply hole 1327 can communicate with the second auxiliary back pressure chamber 1325b through the connecting groove 1328.

[0184] The width D3 of the connecting groove 1328 can also be formed in the same way as the inner diameter D1 of the oil supply hole 1327. In this case, the communication area between the second secondary back pressure chamber 1325b and the oil supply hole 1327 becomes wider, thereby enabling oil to flow actively between the second secondary back pressure chamber and the oil supply hole 1327. For example, oil drawn up through the oil supply hole 1327 can move rapidly to the second secondary back pressure chamber 1325b.

[0185] On the contrary, such as Figure 10 As shown, the width D3 of the connecting groove 1328 can be smaller than the inner diameter D1 of the oil supply hole 1327. In this case, the connecting groove 1328 forms a venturi tube between the oil supply hole 1327 and the second auxiliary back pressure chamber 1325b, allowing the oil in the oil storage space 110b to flow more quickly into the oil supply hole 1327. This oil then moves rapidly towards the second auxiliary back pressure chamber 1325b, thereby eliminating the oil shortage in the second auxiliary back pressure chambers 1343a, 1343b, and 1343c during compressor restart.

[0186] On the other hand, another embodiment of the oil supply port is as follows.

[0187] That is, in the above embodiment, the oil supply hole is formed through the sub-bulb portion, but depending on the situation, the oil supply hole may be formed through the sub-plate portion.

[0188] Figure 12 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port. Figure 13 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0189] Reference Figure 12 The shape or through-hole position of the oil supply hole 1327 in this embodiment can be similar to that in the above embodiments. For example, the inner diameter D1 of the oil supply hole 1327 can be formed as a single inner diameter or as multiple inner diameters along the length direction.

[0190] The outlet 1327b of the oil supply port 1327 is formed between the rear end of the second auxiliary back pressure chamber 1325b and the front section of the first auxiliary back pressure chamber 1325a facing it, as shown below. Figure 10 As shown in the embodiment, a connecting groove 1328 may also be formed between the outlet 1327b of the oil supply port 1327 and the rear end of the second auxiliary back pressure chamber 1325b. Since the effect of this is the same as that of the embodiment described above, the description therein will be replaced by the description of the embodiment described above.

[0191] However, in this embodiment, the oil supply hole 1327 can be formed by penetrating from the bottom surface to the top surface of the sub-plate portion 1321. In this case, considering the outer diameter of the sub-bushing portion 1322, the inlet 1327a of the oil supply hole 1327 can be formed on the radially outer side of the outlet 1327b of the oil supply hole 1327. Thus, the oil supply hole 1327 can be inclined to make the outlet 1327b closer to the rotation shaft 123.

[0192] As described above, when the oil supply hole 1327 is formed by penetrating the sub-plate portion 1321, the length of the oil supply hole 1327 is shorter than that in the embodiment described above, thus shortening the oil supply path accordingly. As a result, oil can be rapidly supplied to the back pressure chambers 1343a, 1343b, and 1343c through the oil supply hole 1327.

[0193] On the other hand, the oil supply hole 1327 is formed in the sub-plate portion 1321, but it can also be formed radially. (See reference...) Figure 13 The oil supply hole 1327 can be formed by penetrating from the outer peripheral surface of the sub-plate portion 1321 toward the top surface of the sub-plate portion 1321. For example, the oil supply hole 1327 can be composed of a first hole portion 1327c formed from the outer peripheral surface of the sub-plate portion 1321 at a predetermined depth and a second hole portion 1327d penetrating from the inner end of the first hole portion 1327c toward the top surface of the sub-plate portion 1321.

[0194] The first hole 1327c and the second hole 1327d can also be formed with the same inner diameter. Considering that the first hole 1327c is formed to be relatively long, the inner diameter of the first hole 1327c can be larger than the inner diameter of the second hole 1327d. In this case, a pressure-reducing pin (not shown) can also be inserted into the first hole 1327c.

[0195] The area of ​​the second hole 1327d can be larger than the area of ​​the first hole 1327c (excluding the area of ​​the groove excluding the pressure reducing pin). This improves the differential pressure generation effect described above.

[0196] As described above, when a portion of the oil supply hole 1327 is formed radially from the sub-plate portion 1321, although the total length of the oil supply hole 1327 increases, a constant amount of oil is always filled in the first hole portion 1327c, which constitutes the oil supply hole 1327, as it is formed radially. Therefore, the actual length of the oil supply hole 1327 corresponds to the length of the second hole portion 1327d, which is shorter than the axial length of the oil supply hole 1327 in the above embodiment. Thus, in this embodiment, the actual length of the oil supply hole 1327 is shorter. Therefore, when the compressor restarts, oil can be rapidly supplied to the back pressure chambers 1343a, 1343b, and 1343c.

[0197] On the other hand, another embodiment of the oil supply port is as follows.

[0198] That is, in the above embodiment, the oil supply hole is formed outside the secondary bearing hole, but depending on the situation, the oil supply hole may also be formed through the inner circumferential surface of the secondary bearing hole.

[0199] Figure 14 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0200] Reference Figure 14 In the oil supply hole 1327 of this embodiment, the lower end of the inlet 1327a can be formed on the inner circumferential surface of the sub-bulb portion 1322, that is, the sub-bearing surface 1322b of the inner circumferential surface of the sub-bearing hole 1322a.

[0201] For example, as shown in the above embodiment, the outlet 1327b of the oil supply port 1327 can be formed on the top surface of the sub-plate portion 1321, and can be formed between the rear end of the second sub-back pressure chamber 1325b and the front end of the first sub-back pressure chamber 1325a. In this case, the oil supply port 1327 can also be formed to be separated from the first sub-back pressure chamber 1325a or the second sub-back pressure chamber 1325b, or as shown in the example. Figure 10 As shown in the embodiment, it is configured to communicate with the second auxiliary back pressure chamber 1325b via a connecting groove 1328. Since this is similar to the embodiment described above, the description therein will be replaced by the description of the embodiment described above.

[0202] However, in this embodiment, the inlet 1327a of the oil supply hole 1327 can be formed to penetrate the inner peripheral surface of the sub-bulb portion 1322 constituting the sub-bearing surface 1322b. Therefore, a portion of the oil supplied to the sub-bearing surface 1322b through the oil flow path 125 and the second oil through hole 126b can be supplied to the back pressure chambers 1343a, 1343b, and 1343c through the oil supply hole 1327.

[0203] Furthermore, in this embodiment, an oil groove 1322c is spirally formed on the secondary bearing surface 1322b, and the inlet 1327a of the oil supply port 1327 can be formed to penetrate through the middle of the oil groove 1322c. In this case, when the rotating shaft 123 rotates, a portion of the oil drawn up through the oil groove 1322c by centrifugal force can flow into the oil supply port 1327, and this oil can be quickly supplied to the back pressure chambers 1343a, 1343b, and 1343c through the oil supply port 1327. Thus, in this embodiment, oil can be supplied to the back pressure chambers 1343a, 1343b, and 1343c more quickly, more stably supporting the blades 1351, 1352, and 1353, while more effectively suppressing the vibration phenomenon generated when the compressor restarts.

[0204] On the other hand, another embodiment of the oil supply port is as follows.

[0205] That is, in the above embodiments, the inlet of the oil supply hole is exposed and connected in the oil storage space, but depending on the situation, the inlet of the oil supply hole can also be set in the pumping unit.

[0206] Figure 15 It is shown Figure 1 A cross-sectional view of another embodiment of the oil supply port.

[0207] Reference Figure 15 In this embodiment, an oil pump 128 may also be provided at the lower end of the rotating shaft 123, and the outlet of the oil pump 128 may be configured to communicate with the inlet 1327a of the oil supply hole 1327.

[0208] In this case, the oil pump 128 can be of various types, such as a centrifugal pump, a viscous pump, or a positive displacement pump. In this embodiment, an example using a trochoid gear pump, which is a type of positive displacement pump, will be described.

[0209] The oil supply port 1327 in this embodiment can be used Figure 4 The oil supply hole 1327 of the embodiment is described above. That is, the lower end of the inlet 1327a constituting the oil supply hole 1327 can be formed by penetrating the lower end face of the sub-bushing portion 1322. The shape and position of the oil supply hole 1327 are the same as those of the embodiment described above, therefore, the description of it is replaced by the description of the embodiment described above.

[0210] However, similar to this embodiment, an oil pump 128 is provided at the lower end of the rotating shaft 123. When the outlet of the oil pump 128 is connected to the inlet 1327a of the oil supply port 1327, the oil stored in the oil storage space 110b can be rapidly supplied to the back pressure chambers 1343a, 1343b, and 1343c. Therefore, even when the compressor restarts, oil can be rapidly and effectively supplied to the back pressure chambers 1343a, 1343b, and 1343c, thereby significantly reducing the vibration of the blades 1351, 1352, and 1353 and the resulting noise and losses.

[0211] On the other hand, another embodiment of the oil supply port is as follows.

[0212] That is, in the above embodiment, the oil supply hole passes through the secondary bearing and is periodically connected to the back pressure chamber. However, depending on the situation, the oil supply hole may also pass through the rotating shaft and the roller and be always connected to the back pressure chamber.

[0213] Figure 16 In order to explain Figure 1 Another embodiment of the oil supply port is shown in a cross-sectional view of a portion of the compression section. Figure 17 It is assembly Figure 16 A portion of the compression section is shown in a cross-sectional view. Figure 18 Yes, yes Figure 17 A cross-sectional view of the “V-V” line.

[0214] Reference Figures 16 to 18 In this embodiment, the oil supply holes 1345a, 1345b, and 1345c are formed by passing through the oil flow path 125 of the rotating shaft 123 and the back pressure chambers 1343a, 1343b, and 1343c of the roller 134.

[0215] For example, in this embodiment, there are multiple oil supply holes 1345a, 1345b, and 1345c, and the multiple oil supply holes 1345a, 1345b, and 1345c can be formed to extend through the inner circumferential surface of the oil flow path 125 that penetrates the interior of the rotating shaft 123 toward each blade groove 1342a, 1342b, and 1342c of the roller 134, or more precisely, toward each back pressure chamber 1343a, 1343b, and 1343c of the roller 134.

[0216] A plurality of oil supply holes 1345a, 1345b, and 1345c may be formed at equal intervals along the circumference at the same height. However, depending on the circumstances, the plurality of oil supply holes 1345a, 1345b, and 1345c may also be formed at equal intervals along the circumference at different heights, or they may be formed at different intervals along the circumference at the same height.

[0217] The plurality of oil supply holes 1345a, 1345b, and 1345c may also be formed radially. However, considering that the outlet 1327b of the oil supply holes 1345a, 1345b, and 1345c penetrates the inner circumferential surface of the oil supply guide grooves 1346a, 1346b, and 1346c described later, the plurality of oil supply holes 1345a, 1345b, and 1345c may preferably be formed at an angle.

[0218] A plurality of oil supply holes 1345a, 1345b, and 1345c can penetrate the inner peripheral surfaces of the back pressure chambers 1343a, 1343b, and 1343c. However, similar to this embodiment, oil supply guide grooves 1346a, 1346b, and 1346c are formed to communicate with each of the back pressure chambers 1343a, 1343b, and 1343c, so that each oil supply hole 1345a, 1345b, and 1345c can be formed through these oil supply guide grooves 1346a, 1346b, and 1346c. Therefore, when machining the oil supply holes 1345a, 1345b, and 1345c, the posture angle can be ensured while reducing the pulsating pressure of the oil flowing into the back pressure chambers 1343a, 1343b, and 1343c.

[0219] For example, oil supply guide grooves 1346a, 1346b, and 1346c, which are larger than the inner diameter of the back pressure chambers 1343a, 1343b, and 1343c, are formed at the lower end of each back pressure chamber 1343a, 1343b, and 1343c, respectively. A plurality of oil supply holes 1345a, 1345b, and 1345c can be formed by penetrating the inner circumferential surface of each enlarged oil supply guide groove 1346a, 1346b, and 1346c in each back pressure chamber 1343a, 1343b, and 1343c. Therefore, before the high-pressure oil flows into the back pressure chambers 1343a, 1343b, and 1343c, it flows into each oil supply guide groove 1346a, 1346b, and 1346c with a cross-sectional area larger than that of the back pressure chambers 1343a, 1343b, and 1343c and is thus buffered. As a result, the vibration of the blades 1351, 1352, and 1353 can be effectively suppressed by mitigating the pulsation of the back pressure on the supporting blades 1351, 1352, and 1353.

[0220] As described above, in this embodiment, the oil supply holes 1345a, 1345b, and 1345c pass through the rotating shaft 123 and the roller 134 and are respectively connected to the oil flow path 125 and the back pressure chambers 1343a, 1343b, and 1343c. More precisely, the back pressure chambers 1343a, 1343b, and 1343c are connected to the oil supply guide grooves 1346a, 1346b, and 1346c. Thus, each back pressure chamber (more precisely, the oil supply guide groove) 1343a, 1343b, and 1343c can be continuously connected to the oil storage space 110b through its respective oil supply hole 1345a, 1345b, and 1345c and the oil flow path 125. As a result, the back pressure of each back pressure chamber 1343a, 1343b, and 1343c is always formed or maintained at a constant pressure or above, for example, a discharge pressure or a pressure close to the discharge pressure. Therefore, even when each blade 1351, 1352, 1353 passes between the proximal point P1 and the inlet 1331, and the front end faces 1351a, 1352a, 1353a are subjected to high pressure changes, the high back pressure of the rear end faces 1351b, 1352b, 1353b keeps the respective blades 1351, 1352, 1353 in contact with the inner circumferential surface 1332 of the cylinder 133, thereby suppressing the vibration phenomenon of the blades 1351, 1352, 1353.

[0221] However, in this embodiment, the inner diameter D1 of the oil supply holes 1345a, 1345b, and 1345c can be less than or equal to the inner diameter D4 of the oil passage holes 126a and 126b. For example, as described above, the rotating shaft 123 has oil passage holes 126a and 126b that extend from the middle of the oil flow path 125 toward the main bearing surface 1312b or the secondary bearing surface 1322b, and the inner diameter D1 of the oil supply holes 1345a, 1345b, and 1345c can be less than or equal to the inner diameter D4 of the oil passage holes 126a and 126b. Therefore, even though the back pressure chambers (oil supply guide grooves) 1343a, 1343b, and 1343c are continuously connected to the oil storage space 110b through the oil supply holes 1345a, 1345b, 1345c and the oil flow path 125, the excessive increase of back pressure on the rear end faces 1351b, 1352b, and 1353b supporting the blades 1351, 1352, and 1353 can be suppressed, and the excessive contact of the area around the near point P1 can be limited, thereby reducing friction loss.

[0222] Although not shown in the accompanying drawings, oil supply guide grooves 1346a, 1346b, and 1346c may also be formed at the upper end of the back pressure chambers 1343a, 1343b, and 1343c facing the main bearing 131. In other words, in the above embodiment, oil supply guide grooves 1346a, 1346b, and 1346c are formed at the lower end of the back pressure chambers 1343a, 1343b, and 1343c facing the auxiliary bearing 132. However, depending on the situation, oil supply guide grooves 1346a, 1346b, and 1346c may also be formed at the upper end of the back pressure chambers 1343a, 1343b, and 1343c, and oil supply holes 1345a, 1345b, and 1345c may also be formed inclined upwards from the middle of the oil flow path 125 toward the oil supply guide grooves 1346a, 1346b, and 1346c. In this case, as the oil supply holes 1345a, 1345b, and 1345c are formed in the direction relative to the oil suction direction, the oil drawn up through the oil flow path 125 can flow more quickly into the oil supply guide grooves 1346a, 1346b, and 1346c through the oil supply holes 1345a, 1345b, and 1345c.

[0223] Furthermore, although in the above embodiments, a first back pressure chamber serving as a low-pressure section and a second back pressure chamber serving as a high-pressure section are formed in the main bearing 131 and the auxiliary bearing 132, respectively, in this embodiment, since the oil supply holes 1345a, 1345b, and 1345c are connected to their respective back pressure chambers 1343a, 1343b, and 1343c, the first back pressure chambers 1315a and 1325a and the second back pressure chambers 1315b and 1325b can be excluded. This ensures the support rigidity of the main bearing surface 1312b and the auxiliary bearing surface 1322b surrounding the rotating shaft 123, and suppresses frictional losses between the upper and lower sides of the blades 1351, 1352, and 1353 and between the main bearing 131 and the auxiliary bearing 132 facing these sides, making it easier to manufacture the main bearing 131 and the auxiliary bearing 132.

[0224] Furthermore, in the rotary vane compressor of this embodiment, it may be more effective when using high-pressure refrigerants such as R32, R410a, or CO2. For example, when using a high-pressure refrigerant, compared to using a medium- or low-pressure refrigerant such as R134a, a larger pressure difference is generated between the compression surfaces and compression back surfaces of the blades 1351, 1352, and 1353 between the near point P1 and the suction port 1331. As a result, when using a high-pressure refrigerant, the vibration of the blades 1351, 1352, and 1353 between the near point P1 and the suction port 1331 may increase. However, similar to this embodiment, the vibration of the blades 1351, 1352, and 1353 can be effectively suppressed by the back pressure of the corresponding area. This suppresses leakage between the compression chambers and reduces noise and wear caused by blade vibration.

[0225] In addition, in the above embodiments, larger back pressure chambers 1343a, 1343b, and 1343c are formed on the inner side (i.e., the roller center side) of the blade grooves 1342a, 1342b, and 1342c. The back pressure chambers 1343a, 1343b, and 1343c can also be formed with the same cross-sectional area as the blade grooves 1342a, 1342b, and 1342c. In this case, although it can also be understood that the back pressure chambers 1343a, 1343b, and 1343c are extensions of the blade slots 1342a, 1342b, and 1342c, without being clearly distinguished from the back pressure chambers 1343a, 1343b, and 1343c, and that the aforementioned oil supply guide grooves 1346a, 1346b, and 1346c are connected to the blade slots 1342a, 1342b, and 1342c, for ease of explanation, the back pressure chambers 1343a, 1343b, and 1343c are described separately from the blade slots 1342a, 1342b, and 1342c. Therefore, it can be understood that the oil supply guide grooves 1346a, 1346b, and 1346c are limited to being connected to the back pressure chambers 1343a, 1343b, and 1343c.

Claims

1. A rotary compressor, wherein, include: The casing has an internal oil storage space; The cylinder is fixed inside the housing and forms a compression space; The main bearing and the auxiliary bearing are respectively disposed on both sides of the cylinder barrel, and each has a main bearing hole and an auxiliary bearing hole that pass through along the axial direction. A rotating shaft is supported by passing through the main bearing hole and the secondary bearing hole. Inside the rotating shaft, an oil flow path is formed in a hollow shape to draw up the oil stored in the oil storage space of the housing. A roller is disposed on the rotating shaft and eccentrically disposed in the compression space, and has at least one blade groove formed along its outer peripheral surface. A back pressure chamber is connected to the inner end of the blade groove. At least one blade is slidably inserted into the blade slot, and the compression space is divided into a plurality of compression chambers by the contact between its front end face and the inner circumferential surface of the cylinder. as well as A plurality of back pressure chambers are formed at predetermined intervals along the circumferential direction on the axial side of the roller in either the main bearing or the secondary bearing, and are connected to the oil flow path and have different pressures from each other. An oil supply hole is provided through the main bearing or the auxiliary bearing. The oil supply hole is formed between a plurality of back pressure chambers and overlaps with the back pressure chamber at least partially along the axial direction to connect the back pressure chamber and the oil storage space.

2. The rotary compressor according to claim 1, wherein, The secondary bearing configured to face the oil storage space includes: The sub-plate portion is attached to one axial side of the cylinder barrel; and The secondary bushing portion extends axially from the secondary plate portion and passes through the secondary bearing hole; The oil supply hole is formed by penetrating the secondary bushing portion.

3. The rotary compressor according to claim 2, wherein, The oil supply hole passes between the axial end face of the secondary bushing and the side of the secondary plate facing the roller.

4. The rotary compressor according to claim 2, wherein, The oil supply hole extends between the inner circumferential surface of the secondary bearing hole and the side of the secondary plate facing the roller.

5. The rotary compressor according to claim 4, wherein, An oil groove is formed on the inner circumferential surface of the secondary bearing hole. The oil supply hole is formed to be connected to the middle of the oil groove.

6. The rotary compressor according to claim 1, wherein, The secondary bearing configured to face the oil storage space includes: The sub-plate is attached to one axial side of the cylinder; and A secondary bushing portion extends axially from the secondary plate portion, and the rotating shaft passes through the secondary bushing portion and is supported thereon. The oil supply hole is formed by penetrating the sub-plate portion.

7. The rotary compressor according to claim 6, wherein, The oil supply hole extends obliquely to the axial direction between the two axial sides of the sub-plate.

8. The rotary compressor according to claim 6, wherein The oil supply hole is composed of a first hole extending radially from the outer peripheral surface of the sub-plate and a second hole penetrating the inner side of the first hole toward the axial side of the sub-plate facing the roller.

9. The rotary compressor according to claim 1, wherein, The secondary bearing configured to face the oil storage space includes: The sub-plate portion is attached to one axial side of the cylinder barrel; and The secondary bushing portion extends axially from the secondary plate portion and passes through the secondary bearing hole; An oil pump is also provided in the secondary bushing section. The oil supply port is connected to the outlet of the oil pump.

10. The rotary compressor according to claim 1, wherein, The inner diameter of the oil supply hole is less than or equal to the inner diameter of the back pressure chamber.

11. The rotary compressor according to claim 1, wherein, The inner diameter of the oil supply hole is formed such that the inner diameter of the upper end facing the roller is greater than or equal to the inner diameter of the lower end belonging to the oil storage space.

12. The rotary compressor according to claim 1, wherein, In the oil supply hole, a connecting groove is formed between the upper end facing the roller and the back pressure cavity facing the upper end in the circumferential direction.

13. A rotary compressor, wherein, include: The casing has an internal oil storage space; The cylinder barrel is fixed inside the housing; The main bearing and the auxiliary bearing are combined with the cylinder to form a compression space together with the cylinder; A rotating shaft is supported radially by the main bearing and the secondary bearing, and an oil flow path is formed in a hollow shape inside the rotating shaft. A roller is disposed on the rotating shaft and eccentrically disposed in the compression space, and forms at least one blade groove along the outer peripheral surface, with a back pressure chamber connected to the inner end of the blade groove. as well as At least one blade is slidably inserted into the blade slot, and the compression space is divided into a plurality of compression chambers by the contact between its front end face and the inner circumferential surface of the cylinder. An oil supply guide groove communicating with the back pressure chamber is formed on the axial side of the roller. An oil supply hole is formed in the rotating shaft, and the oil supply hole connects the inner circumferential surface of the oil flow path and the inner circumferential surface of the oil supply guide groove. The cross-sectional area of ​​the oil supply guide groove is larger than the cross-sectional area of ​​the back pressure chamber.

14. The rotary compressor according to claim 13, wherein, An oil passage hole is formed in the rotating shaft, extending from the middle of the oil flow path toward the main bearing or the secondary bearing and into the outer peripheral surface of the rotating shaft. The inner diameter of the oil supply hole is formed to be less than or equal to the inner diameter of the oil passage hole.

15. A rotary compressor, wherein, The casing has an internal oil storage space; The cylinder is fixed inside the housing and forms a compression space; The main bearing and the auxiliary bearing are respectively disposed on both sides of the cylinder barrel, and each has a main bearing hole and an auxiliary bearing hole that pass through along the axial direction. A rotating shaft is supported by passing through the main bearing hole and the secondary bearing hole. Inside the rotating shaft, an oil flow path is formed in a hollow shape to draw up the oil stored in the oil storage space of the housing. A roller is disposed on the rotating shaft and eccentrically disposed in the compression space to have a contact point with the inner circumferential surface of the cylinder. At least one blade groove is formed along the outer circumferential surface, and a back pressure chamber is connected to the inner end of the blade groove. At least one blade is slidably inserted into the blade slot, and the compression space is divided into a plurality of compression chambers by the contact between its front end face and the inner circumferential surface of the cylinder. A back pressure chamber is formed on the axial side of either the main bearing or the secondary bearing facing the roller, and is connected to the oil flow path; as well as An oil supply hole penetrates either the main bearing or the secondary bearing. The oil supply hole is formed between a plurality of the back pressure chambers and overlaps at least a portion of the back pressure chambers along the axial direction to communicate the outside of the back pressure chambers with the back pressure chambers. The back pressure chamber includes: First back pressure chamber; as well as The second back pressure chamber generates a higher pressure than the first back pressure chamber. The second back pressure chamber is located on one side of the first back pressure chamber and is formed at a predetermined interval along the circumferential direction. One end of the oil supply port is connected to the oil storage space of the housing, and the other end of the oil supply port is located between the first back pressure chamber and the second back pressure chamber. The oil supply port generates a higher pressure than the second back pressure chamber.

Images