Rotary compressor

Abstract

The present application provides a kind of rotary compressor, it includes: cylinder, inner periphery is formed annular to form compression space, and with the suction port formed along the side direction and communicated with compression space, to suck in and provide refrigerant;Roller is rotatably arranged in compression space and is formed with multiple vane slots, multiple vane slots are formed with preset interval along the outer periphery of roller, provide back pressure on the inside one side of vane slot;Multiple blades are slidably inserted into vane slot, the front end surface of blade contacts the inner periphery of cylinder by back pressure, whereby compression space is divided into multiple compression chambers, the cylinder also has suction passage, the suction passage is formed along the direction intersecting with the suction port, whereby the compression space and the suction port can be communicated, the refrigerant can pass through the suction port and the suction passage and flow into the compression space.

Description

Technical Field

[0001] This invention relates to a rotary compressor that reduces the surface pressure in the inlet area. Background Technology

[0002] Based on the method of compressing the refrigerant, compressors can be classified into reciprocating compressors, rotary compressors, and scroll compressors. Reciprocating compressors use a compression space formed between the piston and cylinder, and compress the fluid through the linear reciprocating motion of the piston; rotary compressors use rollers that rotate eccentrically inside the cylinder to compress the fluid; scroll compressors use a pair of spiral-shaped scrolls that mesh and rotate to compress the fluid.

[0003] Rotary compressors can be distinguished based on the way the rollers rotate relative to the cylinder. For example, rotary compressors can be divided into eccentric rotary compressors, where the rollers rotate eccentrically relative to the cylinder, and concentric rotary compressors, where the rollers rotate concentrically relative to the cylinder.

[0004] In addition, rotary compressors can also be distinguished according to the way the compression chambers are divided. For example, they can be divided into: vane rotary compressors, which divide the compression space by the contact between vanes and rollers or cylinders; and elliptical rotary compressors, which divide the compression space by the contact between a portion of an elliptical roller and the cylinder.

[0005] The rotary compressor described above is equipped with a drive motor, and a rotating shaft is connected to the rotor of the drive motor. The rotational force of the drive motor is transmitted to the rollers through the rotating shaft, thereby compressing the refrigerant.

[0006] Patent document 1 (Japanese Patent Application Publication No. 2014-125962) discloses a gas compressor comprising a rotor, a cylinder surrounding the outer side of the rotor and having an inner circumferential surface, a plurality of plate-shaped blades slidably inserted into blade slots formed in the rotor, and two side blocks blocking both ends of the rotor and the cylinder. The front ends of the blades abut against the inner circumferential surface of the cylinder to form a plurality of compression chambers. The contour shape of the inner circumferential surface of the cylinder is set such that each compression chamber thus formed performs only one cycle of gas intake, compression, and discharge during one rotation of the rotor.

[0007] The vane compressor described in Patent Document 1 has a low-pressure structure, wherein refrigerant gas (i) is drawn into the compression chamber through the suction port and (ii) through the suction port on the main bearing section.

[0008] In particular, in Patent Document 1, the intake port is formed on the main bearing portion, and refrigerant gas is drawn into both the upper and lower parts of the cylinder. Furthermore, Patent Document 1 discloses a structure in which a flow path is formed in the lower part of the cylinder, connecting the intake port of the main bearing portion to the secondary bearing portion via the cylinder.

[0009] In most vane compressors, the suction inlet is shaped like this.

[0010] On the other hand, our concentric compressor has a structure in which the suction port is formed on the side of the cylinder and the refrigerant gas flows directly into the compression chamber through the suction port on the side of the cylinder.

[0011] Our company's concentric compressor has a high-pressure structure that differs from existing technology and other companies' vane compressors, but instead has the same suction structure as a rotary compressor.

[0012] The structure of our concentric compressor has an intake port formed on the side of the cylinder, which is disadvantageous in terms of the surface pressure of the blades and may also lead to reliability issues.

[0013] In particular, in the case of existing intake ports, since they are formed on the side of the cylinder, the contact force of the blades is large, and a large surface pressure is generated, which can lead to reliability problems such as wear at the intake port.

[0014] Therefore, in the structure of concentric compressors, there is a need to develop a rotary compressor that has a structure that can improve the efficiency and reliability of the compressor by partially changing the suction structure of the cylinder to reduce the surface pressure acting on the blades. Summary of the Invention

[0015] One object of the present invention is to provide a rotary compressor having a structure that improves reliability and reduces suction loss by reducing the surface pressure in the suction inlet area.

[0016] In particular, the present invention provides a rotary compressor having a structure that can improve reliability by changing the cylinder intake structure for intake of refrigerant gas in a rotary compressor for automobiles or air conditioning systems to reduce the surface pressure acting on the blades.

[0017] Another object of the present invention is to provide a rotary compressor in a cylinder suction structure that has a structure that reduces the surface pressure acting on the blades by drawing in the refrigerant gas in a vertical direction, thereby improving reliability.

[0018] Another object of the present invention is to provide a structure that improves reliability and reduces suction loss by reducing the surface pressure in the suction inlet area of ​​a vane-type vehicle or air conditioning compressor.

[0019] Another object of the present invention is to provide a structure that reduces the wear phenomenon of the intake port caused by the decrease in surface pressure near the intake port by changing the cylinder intake structure for intake of refrigerant gas in a rotary compressor for automobiles or air conditioners.

[0020] Another object of the present invention is to provide a structure that allows refrigerant passing through the intake passage to flow more smoothly into the compression space, and in the process reduces refrigerant intake loss.

[0021] Another object of the present invention is to provide a structure that improves mechanical losses under efficiency conditions by changing the cylinder intake structure for drawing in refrigerant gas in a rotary compressor for automobiles or air conditioning.

[0022] To address the aforementioned issues, the rotary compressor of the present invention includes: a cylinder having an annular inner circumferential surface to form a compression space; a roller rotatably disposed in the compression space of the cylinder and having a plurality of blade grooves formed therein, providing back pressure on one side inside the plurality of blade grooves, the plurality of blade grooves being formed at predetermined intervals along the outer circumferential surface of the roller; and a plurality of blades slidably inserted into the blade grooves and rotating together with the roller, the leading edge faces of the plurality of blades contacting the inner circumferential surface of the cylinder using the back pressure, thereby dividing the compression space into a plurality of compression chambers, the cylinder having a refrigerant intake path, the intake path including: an intake port communicating with the compression space and formed laterally to intake and provide refrigerant; and an intake passage formed along a direction intersecting the intake port and enabling communication between the compression space and the intake port, the refrigerant being able to flow into the compression space through the intake port and the intake passage.

[0023] With this structure, the refrigerant flows through the suction port and into the compression space via the suction passage, thereby reducing the surface pressure in the suction port area, which can improve reliability and reduce suction loss.

[0024] In addition, the rotary compressor of the present invention further includes a main bearing portion and a secondary bearing portion, which are respectively disposed at both ends of the cylinder and configured to be spaced apart from each other to form the surfaces of both ends of the compression space. At least one of the main bearing portion and the secondary bearing portion is formed with a suction guide portion, which is recessed to communicate with the suction passage and the compression space, and to accommodate refrigerant passing through the suction passage and to provide the refrigerant to the compression space.

[0025] Therefore, it is possible to accommodate refrigerant passing through the intake passage and to supply the refrigerant to the compression space, thereby reducing wear caused by the decrease in surface pressure at the intake portion of the cylinder.

[0026] According to one example related to the present invention, the main bearing portion is disposed at the upper end of the cylinder to form the top surface of the compression space, and the suction guide portion may include a main suction guide portion recessed in the main bearing portion, such that the suction passage and the compression space are connected, and the main suction guide portion accommodates refrigerant passing through the suction passage and is able to flow the refrigerant upward, thereby providing the refrigerant to the compression space.

[0027] Additionally, the secondary bearing portion is disposed at the lower end of the cylinder to form the bottom surface of the compression space. The suction guide portion may also include a secondary suction guide portion, which is recessed in the secondary bearing portion, so that the suction passage and the compression space are connected, and the refrigerant passing through the suction passage is accommodated and the refrigerant can flow downward, thereby providing the refrigerant to the compression space.

[0028] Therefore, the existing structure of the suction inlet, which is simply formed along the transverse direction, is transformed into a structure with a suction passage, a main suction guide, and a secondary suction guide in the longitudinal or inclined direction. This partially changes the direction of the refrigerant suction flow path to the direction of the main bearing and the secondary bearing, thereby reducing blade contact force and surface pressure, improving reliability, and improving suction loss.

[0029] According to another example related to the present invention, at least one of the main inhalation guide and the auxiliary inhalation guide has a side portion facing the approach point and an other side portion formed on the opposite side of the side portion, and can be formed as an asymmetrical structure in which the side portion is longer than the other side portion.

[0030] Preferably, the intake passage can be formed to penetrate the top and bottom surfaces of the cylinder in a direction parallel to the vertical.

[0031] In addition, the inhalation passage may have an elliptical cross-section.

[0032] On the other hand, inflow guides can be formed on the top and bottom surfaces of the cylinder to connect the compression space and the suction passage. The inflow guides have a predetermined width and depth so that the refrigerant flowing in the suction passage can flow into the compression space.

[0033] The inhalation guide has a predetermined depth, and the depth of the inflow guide can be less than or equal to the depth of the inhalation guide.

[0034] The inflow guide can be formed by cutting a portion of the inner circumferential surface, top surface, and bottom surface of the cylinder adjacent to the suction passage.

[0035] The intake passage may include: a first intake passage formed along a direction intersecting the vertical direction and communicating with the intake port and penetrating the top surface of the cylinder; and a second intake passage formed along a direction intersecting the first intake passage and communicating with the first intake passage and penetrating the bottom surface of the cylinder.

[0036] To address yet another issue related to this invention, the rotary compressor of this invention comprises: a housing; a drive motor disposed inside the housing and generating rotational power; a cylinder having an inner circumferential surface formed in an annular shape to form a compression space; a roller rotatably disposed in the compression space of the cylinder, having a plurality of blade grooves formed at predetermined intervals along the outer circumferential surface of the roller, providing back pressure on one side inside the plurality of blade grooves; and a plurality of blades slidably inserted into the blade grooves and rotating together with the roller, the leading edge faces of the plurality of blades contacting the inner circumferential surface of the cylinder through the back pressure. The compression space is divided into a plurality of compression chambers by contact; and a main bearing portion and a secondary bearing portion are respectively disposed at both ends of the cylinder barrel and spaced apart from each other to form the surfaces of both ends of the compression space. The cylinder barrel has a refrigerant intake flow path, the intake flow path including: an intake port that communicates with the compression space and is formed laterally to draw in and provide refrigerant; and an intake passage formed in a direction intersecting the intake port and enabling communication between the compression space and the intake port, through which the refrigerant can flow into the compression space.

[0037] This structure transforms the existing simple transversely formed suction inlet into a longitudinal or inclined suction passage and suction guide, thereby partially changing the direction of the refrigerant suction flow path to the direction of the main bearing and secondary bearing. This reduces blade contact force and surface pressure, improving reliability and mitigating suction losses.

[0038] The drive motor may include: a stator fixedly disposed on the inner circumferential surface of the housing; a rotor rotatably inserted into the interior of the stator; and a rotating shaft coupled to the interior of the rotor and rotating together with the rotor, and connected to the roller to transmit a rotational force capable of rotating the roller.

[0039] According to one example related to the present invention, at least one of the main bearing portion and the secondary bearing portion may be formed with a suction guide portion, the suction guide portion being recessed to communicate between the suction passage and the compression space, and to accommodate refrigerant passing through the suction passage and to provide the refrigerant to the compression space.

[0040] The main bearing portion is disposed at the upper end of the cylinder to form the top surface of the compression space. The suction guide portion may include a main suction guide portion, which is recessed in the main bearing portion, so that the suction passage and the compression space are connected, and the refrigerant passing through the suction passage is accommodated and the refrigerant is able to flow upward, thereby providing the refrigerant to the compression space.

[0041] Additionally, the secondary bearing portion is disposed at the lower end of the cylinder to form the bottom surface of the compression space. The suction guide portion may also include a secondary suction guide portion, which is recessed in the secondary bearing portion, so that the suction passage and the compression space are connected, and the refrigerant passing through the suction passage is accommodated and the refrigerant is allowed to flow downward, thereby providing the refrigerant to the compression space.

[0042] In the rotary compressor of the present invention, the mechanical losses of the compressor itself can be improved under the condition of efficiency by constructing the above-mentioned suction passage, main suction guide and auxiliary suction guide.

[0043] The intake passage can be configured to extend parallel to the vertical direction through the top and bottom surfaces of the cylinder.

[0044] In addition, the inhalation passage may have an elliptical cross-section.

[0045] Inflow guides may be formed on the top and bottom surfaces of the cylinder to connect the compression space and the suction passage. The inflow guides have a predetermined width and depth so that refrigerant flowing in the suction passage can flow into the compression space.

[0046] As an example, the inflow guide may be formed such that a portion of the inner circumference of the cylinder adjacent to the suction passage, as well as a portion of the top and bottom surfaces of the cylinder, are cut off.

[0047] As described above, inflow guides are formed on the top and bottom surfaces of the cylinder barrel, thereby allowing the refrigerant passing through the suction passage to flow more smoothly into the compression space, thus reducing refrigerant suction losses. Furthermore, the refrigerant can also flow more smoothly into the compression space through the inflow guides before being contained in the suction passage. In particular, the inflow guides can increase the suction area that will be drawn into the compression space from the suction passage, thereby maintaining a lower surface pressure.

[0048] According to another embodiment related to the present invention, the inhalation passage may include: a first inhalation passage formed along a direction intersecting the vertical direction and communicating with the inhalation port and penetrating the top surface of the cylinder; and a second inhalation passage formed along a direction intersecting the first inhalation passage and communicating with the first inhalation passage and penetrating the bottom surface of the cylinder. Attached Figure Description

[0049] Figure 1 This is a longitudinal sectional view showing the rotary compressor of the present invention.

[0050] Figure 2 This is a perspective view showing the compression section of the rotary compressor of the present invention.

[0051] Figure 3 This is a cross-sectional view showing the compression section of the rotary compressor of the present invention.

[0052] Figure 4 This is an exploded perspective view showing the compression section of the rotary compressor of the present invention.

[0053] Figure 5 This is a longitudinal sectional view showing the compression section of the rotary compressor of the present invention.

[0054] Figure 6 This is a perspective view showing an example of the cylinder of the rotary compressor of the present invention.

[0055] Figure 7 This is a top view showing the bottom surface of the main bearing portion of the rotary compressor of the present invention.

[0056] Figure 8 This is a top view showing the top surface of the main bearing portion of the rotary compressor of the present invention.

[0057] Figure 9 This is a graph comparing the efficiency of existing technologies and the present invention.

[0058] Figure 10 This is a perspective view showing another example of the cylinder of the rotary compressor of the present invention.

[0059] Figure 11 It is shown Figure 10 A longitudinal sectional view of the cylinder.

[0060] Figure 12 This is a graph illustrating the efficiency of the surface pressure of the present invention.

[0061] Figure 13 This is a perspective view showing yet another example of the cylinder of the rotary compressor of the present invention.

[0062] Figure 14 It is shown Figure 13 A longitudinal sectional view of the cylinder. Detailed Implementation

[0063] In this specification, even in different embodiments, the same or similar components are given the same or similar reference numerals, and repeated descriptions are omitted.

[0064] Furthermore, even if the embodiments are different from each other, as long as there is no contradiction in structure or function, the structure applied to one embodiment can also be applied to another embodiment.

[0065] Unless the context explicitly specifies otherwise, the singular form includes the plural form.

[0066] When describing the embodiments disclosed in this specification, detailed descriptions of relevant well-known technologies will be omitted if it is determined that such detailed descriptions may obscure the essence of the embodiments disclosed in this specification.

[0067] Furthermore, the accompanying drawings are only for the purpose of facilitating the understanding of the embodiments disclosed in this specification, and should not be construed as limiting the technical ideas disclosed in this specification. Rather, they should cover all modifications, equivalents, and even substitutions included in the spirit and technical scope of the present invention.

[0068] Figure 1 This is a longitudinal sectional view showing the rotary compressor 100 of the present invention. Figure 2 This is a perspective view showing the compression section 130 of the rotary compressor 100 of the present invention. Additionally, Figure 3 This is a cross-sectional view showing the compression section 130 of the rotary compressor 100 of the present invention. Figure 4 This is an exploded perspective view showing the compression section 130 of the rotary compressor 100 of the present invention.

[0069] Below, refer to Figures 1 to 4 The rotary compressor 100 of the present invention will be described below.

[0070] The rotary compressor 100 of the present invention can be a vane rotary compressor 100. In addition, the rotary compressor 100 of the present invention can reduce the surface pressure in the suction port 1331 area of ​​a vane-type vehicle or air conditioning compressor, thereby improving reliability and reducing mechanical losses.

[0071] Reference Figure 3 and Figure 4 The rotary compressor 100 of the present invention includes a cylinder 133, a roller 134, and a plurality of blades 1351, 1352, and 1353.

[0072] The inner circumferential surface of the cylinder 133 is formed in an annular shape, thereby forming a compression space V. Additionally, the cylinder 133 has a refrigerant intake path. The intake path includes an intake port 1331 and an intake passage 1333. The intake port 1331 is configured to communicate with the compression space V, thereby drawing in refrigerant and supplying it to the compression space V.

[0073] The refrigerant drawn in through the suction port 1331 can be refrigerant gas, which is separated into refrigerant liquid and refrigerant gas in the accumulator. The separated refrigerant gas flows into the compression space V through the suction port 1331 of the cylinder 133, while the refrigerant liquid will flow back into the evaporator.

[0074] Additionally, the intake passage 1333 is formed along a direction intersecting with the intake port 1331, and is formed between the compression space V and the intake port 1331 in a manner that allows communication between the two. The refrigerant flows through the intake port 1331 and the intake passage 1333 and into the compression space V.

[0075] The detailed structure of the inhalation pathway 1333 will be described later.

[0076] 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 is formed into an asymmetrical elliptical shape by combining a plurality of ellipses, such as four ellipses with different length ratios, into two origins. The shape of the inner circumferential surface of the cylinder 133 will be described in detail later.

[0077] The roller 134 is rotatably disposed in the compression space V of the cylinder 133. Furthermore, a plurality of vane slots 1342a, 1342b, and 1342c are formed on the roller 134 at predetermined intervals along its outer circumferential surface. Additionally, the compression space V is formed between the inner circumferential surface of the cylinder 133 and the outer circumferential surface of the roller 134.

[0078] That is, the compression space V is the space formed between the inner circumferential surface of the cylinder 133 and the outer circumferential surface of the roller 134. In addition, the compression space V is divided into spaces corresponding to the number of blades 1351, 1352, and 1353 by a plurality of blades 1351, 1352, and 1353.

[0079] As an example, refer to Figure 3 The illustration shows an example of a compression space V divided by three blades 1351, 1352, and 1353 into: a first compression space V1 located on the side of the discharge outlets 1313a, 1313b, and 1313c; a second compression space V2 located on the side of the inlet 1331; and a third compression space V3 located between the side of the inlet 1331 and the side of the discharge outlets 1313a, 1313b, and 1313c.

[0080] Blades 1351, 1352, and 1353 are slidably inserted into blade grooves 1342a, 1342b, and 1342c, and rotate together with roller 134. Furthermore, by providing back pressure from the rear ends of blades 1351, 1352, and 1353, the front end faces 1351a, 1351b, and 1351c of blades 1351, 1352, and 1353 contact the inner circumferential surface of cylinder 133.

[0081] In this invention, a plurality of blades 1351, 1352, and 1353 are provided, thereby forming a multi-back pressure structure, and the front end faces 1351a, 1351b, and 1351c of the plurality of blades 1351, 1352, and 1353 are in contact with the inner circumference of the cylinder 133, thereby dividing the compression space V into a plurality of compression spaces V1, V2, and V3.

[0082] In this invention, Figure 3 The illustration shows an example where blades 1351, 1352, and 1353 are configured in three ways. Therefore, the compression space V is divided into three compression spaces V1, V2, and V3.

[0083] In the rotary compressor 100 of the present invention, high-pressure refrigerant is contained between one of the plurality of blades 1351, 1352, 1353 and the inner circumferential surface of the cylinder 133, and the high-pressure refrigerant can maintain a predetermined back pressure until it bypasses to the suction port 1331, such that the leading edge faces 1351a, 1351b, 1351c of the blades 1351, 1352, 1353 are in contact with the inner circumferential surface of the cylinder 133.

[0084] The predetermined back pressure can be understood as the discharge back pressure that enables high-pressure refrigerant to be discharged into the internal space of the casing 110 through the discharge ports 1313a, 1313b, and 1313c of the compression space V.

[0085] In addition, the time when the high-pressure refrigerant is bypassed to the suction port 1331 can be understood as the time when the suction begins, that is, the "suction start time point".

[0086] The rotary compressor 100 of the present invention will now be described in detail.

[0087] Reference Figure 1 The rotary compressor 100 of the present invention may further include: a housing 110; a drive motor 120 disposed inside the housing 110 and used to generate rotational power; and a main bearing portion 131 and a secondary bearing portion 132, which are respectively disposed at both ends of the cylinder 133 and configured to be spaced apart from each other to form two sides (the upper and lower end surfaces) of the compression space V. The drive motor 120 may be disposed in the upper inner space 110a of the housing 110, and the compression portion 130 may be disposed in the lower inner space 110b of the housing 110. The drive motor 120 and the compression portion 130 may be connected to each other via a rotating shaft 123.

[0088] The housing 110 is the part that forms the appearance of the compressor, and it can be divided into longitudinal or transverse types depending on the arrangement of the compressor. A longitudinal type is a structure in which the drive motor 120 and the compression unit 130 are arranged axially on the upper and lower sides, while a transverse type is a structure in which the drive motor 120 and the compression unit 130 are arranged on the left and right sides. In this embodiment, the housing 110 is described primarily in a longitudinal configuration, but its application to a transverse configuration is not excluded.

[0089] The housing 110 may include: an intermediate outer shell 111 formed in a cylindrical shape; a lower outer shell 112 covering the lower end of the intermediate outer shell 111; and an upper outer shell 113 covering the upper end of the intermediate outer shell 111.

[0090] The drive motor 120 and the compressor unit 130 can be inserted into and fixedly connected to the intermediate housing 111, while the suction pipe 115 can directly pass through and connect to the compressor unit 130. The lower housing 112 can be sealed to the lower end of the intermediate housing 111, and an oil storage space 110b for storing the oil to be 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, and an oil separating 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.

[0091] The drive motor 120 is part of the electric motor unit, which provides power for driving the compression unit 130. The drive motor 120 includes a stator 121, a rotor 122, and a rotating shaft 123.

[0092] The stator 121 can be fixedly disposed inside the housing 110 and 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.

[0093] The rotor 122 is rotatably inserted into the stator 121, and the rotating shaft 123 is pressed into the center of the rotor 122. Thus, the rotating shaft 123 and the rotor 122 rotate concentrically together.

[0094] A hollow oil flow path 125 is formed at the center of the rotating shaft 123, and oil passage holes 126a and 126b are formed in the middle of the oil flow path 125, extending toward the outer peripheral surface of the rotating shaft 123. The oil passage holes 126a and 126b include: a first oil passage hole 126a belonging to the main bushing portion 1312 (described later); and a second oil passage hole 126b belonging to the secondary bushing portion 1322. One or more of the first oil passage hole 126a and the second oil passage hole 126b may be formed. This embodiment shows the case where multiple or more are formed.

[0095] An oil pickup 127 may be provided at the middle or lower end of the oil flow path 125. As an example, the oil pickup 127 may include one of a gear pump, a viscous pump, and a centrifugal pump. This embodiment illustrates an example using a centrifugal pump. Thus, if the rotating shaft 123 rotates, the oil filling the oil storage space 110b of the housing 110 can be drawn up by the oil pickup 127. The oil can be drawn up along the oil flow path 125 and then supplied to the secondary bearing surface 1322b of the secondary bushing portion 1322 via the second oil through hole 126b, and to the main bearing surface 1312b of the main bushing portion 1312 via the first oil through hole 126a.

[0096] Alternatively, the rotating shaft 123 can be integrally formed with the roller 134, or it can be assembled later after the roller 134 is pressed in. In this embodiment, the example of the roller 134 being integrally formed with the rotating shaft 123 will be described in detail later.

[0097] In the rotating shaft 123, with the roller 134 as a reference, a first bearing support surface (not shown) is formed between the upper half of the rotating shaft 123, i.e., the main shaft portion 123a pressed into the rotor 122, and the main support portion 123b extending from the main shaft portion 123a toward the roller 134; with the roller 134 as a reference, a second supported surface (not shown) can be formed in the lower half of the rotating shaft 123, i.e., the rotating shaft 123 located at the lower end of the auxiliary bearing portion 132. The first bearing support surface and the first shaft support surface (not shown), described later, together form the first axial support portion 151, and the second bearing support surface and the second shaft support surface (not shown), described later, together form the second axial support portion 152. The explanation of the first bearing support surface and the second bearing support surface will be repeated later along with the first axial support portion 151 and the second axial support portion 152.

[0098] The main bearing portion 131 and the auxiliary bearing portion 132 can be respectively provided at both ends of the cylinder 133. The main bearing portion 131 and the auxiliary bearing portion 132 are configured to be spaced apart from each other, thereby forming the two surfaces (the surfaces at both ends) of the aforementioned compression space V respectively.

[0099] As an example, refer to Figure 1 , Figure 2 as well as Figure 4 The illustration shows an example where the main bearing portion 131 is disposed at the upper end of the cylinder 133 to form the top surface of the compression space V, and the auxiliary bearing portion 132 is disposed at the lower end of the cylinder 133 to form the bottom surface of the compression space V.

[0100] Figure 5 This is a longitudinal sectional view showing the compression section of the rotary compressor 100 of the present invention. Figure 6 This is a perspective view showing an example of the cylinder 133 of the rotary compressor 100 of the present invention.

[0101] The compression space V and the inlet 1331 can be connected by an inlet passage 1333, which is formed along a direction that intersects with the inlet 1331.

[0102] Reference Figure 5 and Figure 6 An example is shown where the intake passage 1333 is formed to penetrate the top and bottom surfaces of the cylinder 133 in a direction parallel to the vertical direction and has an elliptical cross-section.

[0103] Additionally, as will be discussed later. Figure 13 and Figure 14 As described herein, the inhalation pathway 1333 may also include a first inhalation pathway 1333a and a second inhalation pathway 1333b formed along a direction intersecting the vertical direction, rather than being formed parallel to the vertical direction, as will be described later.

[0104] like Figure 5 and Figure 6 As shown, the intake passage 1333 is formed along the vertical direction, thus forming an intake flow path for refrigerant to flow from the top and bottom of the cylinder 133 into the compression space V, rather than a structure in which refrigerant is directly drawn into the compression space V from the side.

[0105] Figure 7 This is a top view showing the bottom surface of the main bearing portion 131 of the rotary compressor 100 of the present invention. Figure 8 This is a top view showing the top surface of the main bearing portion 131 of the rotary compressor 100 of the present invention.

[0106] Reference Figure 7 and Figure 8 The suction guides 1317 and 1327 formed in at least one of the main bearing portion 131 and the secondary bearing portion 132 will be described.

[0107] At least one of the main bearing section 131 and the secondary bearing section 132 may be provided with a suction guide section 1317, 1327.

[0108] The intake guides 1317 and 1327 are recessed in the main bearing portion 131 and the secondary bearing portion 132, respectively, so that the intake passage 1333 and the compression space V are connected, and the refrigerant passing through the intake passage 1333 is contained and the refrigerant is guided to be supplied to the compression space V.

[0109] Reference Figure 1 , Figure 2 and Figure 4 Examples are shown, such as a main bearing portion 131 being disposed at the upper end of the cylinder 133 to form the top surface of the compression space V, and a secondary bearing portion 132 being disposed at the lower end of the cylinder 133 to form the bottom surface of the compression space V.

[0110] Inhalation guides 1317 and 1327 may include a main inhalation guide 1317.

[0111] The main suction guide 1317 can be recessed in the main bearing portion 131, so that the suction passage 1333 and the compression space V are connected.

[0112] In addition, the main suction guide 1317 can accommodate refrigerant passing through the suction passage 1333, and can direct the refrigerant upwards and provide the refrigerant to the compression space V.

[0113] Reference Figure 3 , Figure 4 and Figure 7An example of a diamond-shaped main intake guide 1317 is shown, but the shape of the main intake guide 1317 is not necessarily limited to this structure. Other structures can be used as long as the structure can accommodate and guide the flow of refrigerant through the intake passage 1333 and provide it to the compression space V.

[0114] However, the main inhalation guide 1317 must be connected to the inhalation passage 1333 and the compression space V respectively, and is preferably assembled into a sealed structure that is not connected to the outside.

[0115] In addition, the main inhalation guide 1317 should be a structure capable of accommodating all or part of the upper end of the inhalation passage 1333.

[0116] Reference Figure 3 and Figure 4 The main intake guide 1317 may have: a side portion 1317a extending toward the approach point P1; and another side portion 1317b formed on the opposite side of the side portion 1317a.

[0117] Additionally, refer to Figure 3 This illustrates an example where one side portion 1317a of the main intake guide 1317 is formed to be longer than the other side portion 1317b. Therefore, the main intake guide 1317 forms an asymmetrical structure.

[0118] One side portion 1317a of the main inhalation guide portion 1317 is formed to be longer than the other side portion 1317b, and can extend in a manner facing the approach point P1, thereby further improving inhalation efficiency.

[0119] The inhalation guides 1317 and 1327 may also include a secondary inhalation guide 1327.

[0120] The secondary intake guide 1327 can be recessed in the secondary bearing portion 132, thereby connecting the intake passage 1333 and the compression space V.

[0121] Additionally, the secondary intake guide 1327 can accommodate refrigerant passing through the intake passage 1333, and can direct the refrigerant downwards and provide the refrigerant to the compression space V.

[0122] Reference Figure 8 An example of a diamond-shaped secondary intake guide 1327 is shown, but the shape of the secondary intake guide 1327 is not necessarily limited to this structure. Other structures can be used as long as the structure can accommodate and guide the flow of refrigerant through the intake passage 1333 and provide it to the compression space V.

[0123] However, similar to the aforementioned main inhalation guide 1317, the auxiliary inhalation guide 1327 should be connected to the inhalation passage 1333 and the compression space V respectively, and preferably assembled into a sealed structure that is not connected to the outside.

[0124] In addition, the secondary inhalation guide 1327 should be a structure capable of accommodating all or part of the lower end of the inhalation passage 1333.

[0125] Reference Figure 3 and Figure 4 The auxiliary inhalation guide 1327 may have: a side portion 1327a extending toward the approach point P1; and another side portion 1327b formed on the opposite side of the side portion 1327a.

[0126] Additionally, refer to Figure 3 An example is shown where one side portion 1327a of the auxiliary intake guide 1327 is formed to be longer than the other side portion 1327b. Therefore, the auxiliary intake guide 1327 forms an asymmetrical structure.

[0127] One side portion 1327a of the auxiliary inhalation guide 1327 is formed to be longer than the other side portion 1327b, and can extend in a manner facing the approach point P1, thereby further improving inhalation efficiency.

[0128] One side portion 1317a, 1327a and the other side portion 1317b, 1327b of the aforementioned inhalation guide portions 1317, 1327 may be provided in at least one of the main inhalation guide portion 1317 and the auxiliary inhalation guide portion 1327.

[0129] That is, one side portion 1317a, 1327a and the other side portion 1317b, 1327b can be provided on both the main inhalation guide portion 1317 and the auxiliary inhalation guide portion 1327, or one side portion 1317a, 1327a and the other side portion 1317b, 1327b can also be provided on either the main inhalation guide portion 1317 or the auxiliary inhalation guide portion 1327.

[0130] Reference Figure 7 and Figure 8 An example is shown where the main inhalation guide 1317 and the auxiliary inhalation guide 1327 are formed in corresponding shapes.

[0131] As described above, by forming a main suction guide 1317 and an auxiliary suction guide 1327 in the main bearing section 131 and the auxiliary bearing section 132 respectively, a refrigerant suction flow path is formed that allows refrigerant to flow from the side of the cylinder 133 through the direction in which the main bearing section 131 and the auxiliary bearing section 132 are arranged into the compression space V of the cylinder 133.

[0132] In particular, the refrigerant suction flow path is formed as follows: the flow path from the suction part of the cylinder 133 and the suction passage 1333 is connected to the main suction guide 1317 of the main bearing part 131 and the auxiliary suction guide 1327 of the auxiliary bearing part 132, respectively.

[0133] Figure 9 This is a graph comparing the efficiency of existing technologies and the present invention, such as... Figure 9 As shown, in the case of the prior art rotary compressor 100, there is a point where the limit surface pressure of the suction port 1331 is exceeded between 0 degrees and 60 degrees due to the refrigerant gas flowing in through the side suction port 1331. However, in the rotary compressor 100 of the present invention, the limit surface pressure of the suction port 1331 is not exceeded between 0 degrees and 60 degrees due to the decrease in surface pressure on the suction port 1331.

[0134] On the other hand, the intake passage 1333 can be formed to penetrate the top and bottom surfaces of the cylinder 133 in a direction parallel to the vertical direction.

[0135] Reference Figure 5 and Figure 6 This illustrates an example where the intake passage 1333 extends through the top and bottom surfaces of the cylinder 133. Figure 6 The image also shows an example of an inhalation passage 1333 having an elliptical cross-section.

[0136] Figure 10 This is a perspective view showing another example of the cylinder 133 of the rotary compressor 100 of the present invention. Figure 11 It is shown Figure 10 Longitudinal sectional view of cylinder 133.

[0137] Inflow guides 1335 can be formed on the top and bottom surfaces of the cylinder 133. The inflow guides 1335 allow the refrigerant flowing in the suction passage 1333 to flow into the compression space V, as shown in Figure 1335. Figure 10 and Figure 11 The inflow guide 1335 may have a predetermined width and depth, and may be configured to connect the compression space V and the suction passage 1333.

[0138] In addition, the inflow guide 1335 is formed by cutting a portion of the inner peripheral surface, top surface and bottom surface of the cylinder 133 adjacent to the suction passage 1333.

[0139] The inflow guide 1335 can be formed by chamfering with a predetermined width and depth.

[0140] The inflow guide 1335 allows refrigerant passing through the suction passage 1333 to flow more smoothly into the compression space V, thereby reducing refrigerant intake losses. Furthermore, the inflow guide 1335 also allows refrigerant to flow more smoothly into the compression space V before being received by the suction guides 1317 and 1327. In particular, the inflow guide 1335 increases the suction area from the suction passage 1333 into the compression space V, thereby maintaining a lower surface pressure.

[0141] like Figure 11 As shown, the depth of the inflow guide 1335 is preferably formed to be a suitable depth that is less than or equal to the depth of the suction guides 1317 and 1327. By forming the depth of the inflow guide 1335 to a suitable depth, problems such as reduced contact area with the blades 1351, 1352, and 1353 and increased surface pressure can be prevented.

[0142] Figure 12 This is a graph illustrating the efficiency of surface pressure in this invention, see reference. Figure 12 In the case of the prior art rotary compressor 100, there is a point where the limit surface pressure of the suction port 1331 is exceeded between 0 degrees and 60 degrees due to the refrigerant gas flowing in through the side suction port 1331. However, in the rotary compressor 100 of the present invention, the limit surface pressure of the suction port 1331 is not exceeded between 0 degrees and 60 degrees due to the decrease in surface pressure on the suction port 1331.

[0143] Figure 13 This is a perspective view showing yet another example of the cylinder 133 of the rotary compressor 100 of the present invention. Figure 14 It is shown Figure 13 Longitudinal sectional view of cylinder 133.

[0144] Reference Figure 13 and Figure 14 Another example of the cylinder 133 of the rotary compressor 100 of the present invention, which includes the first intake passage 1333a and the second intake passage 1333b, will be described.

[0145] Inhalation pathways 1333a and 1333b may include a first inhalation pathway 1333a and a second inhalation pathway 1333b.

[0146] The first intake passage 1333a is formed along a direction intersecting the vertical direction and communicates with the intake port 1331, and can penetrate the top surface of the cylinder 133. In addition, the first intake passage 1333a can communicate with the main intake guide 1317.

[0147] The second intake passage 1333b is formed along a direction intersecting the first intake passage 1333a and communicates with the intake port 1331, and can penetrate the bottom surface of the cylinder 133. In addition, the second intake passage 1333b can communicate with the auxiliary intake guide 1327.

[0148] In the rotary compressor 100 of the present invention, the refrigerant drawn in through the suction port 1331 passes through the first suction passage 1333a and the second suction passage 1333b, and the refrigerant passing through the first suction passage 1333a and the second suction passage 1333b is guided by the main suction guide 1317 and the auxiliary suction guide 1327, thereby flowing into the compression space V, thereby reducing the loss of the suction flow path and forming an advantageous structure that can improve the suction efficiency of the rotary compressor 100.

[0149] Reference Figure 13 and Figure 14 An example is shown where the inhalation pathway 1333 includes a first inhalation pathway 1333a and a second inhalation pathway 1333b. Additionally, Figure 14 An example is shown where the first inhalation passage 1333a, the second inhalation passage 1333b, and the inhalation port 1331 connected to both are formed together in a horizontal Y-shaped cross section.

[0150] Additionally, refer to Figure 14 The illustration shows an example where the first inhalation passage 1333a and the second inhalation passage 1333b are formed on the left side of the inhalation port 1331 along the upper left and lower left directions, respectively, and can be formed along diagonal directions of approximately 45 degrees.

[0151] Furthermore, the first suction passage 1333a is connected to the main suction guide 1317, and the second suction passage 1333b is connected to the auxiliary suction guide 1327. Thus, the refrigerant drawn in through the suction port 1331 passes through the first suction passage 1333a and the second suction passage 1333b. The refrigerant passing through the first suction passage 1333a and the second suction passage 1333b is guided by the main suction guide 1317 and the auxiliary suction guide 1327 and flows into the compression space V respectively. This reduces the loss in the suction flow path and forms an advantageous structure that can improve the suction efficiency of the rotary compressor 100.

[0152] Next, refer to Figure 3 The structure related to the blades 1351, 1352, and 1353 that pressurize the inner circumference of cylinder 133 through the back pressure of back pressure chambers 1343a, 1343b, and 1343c is described.

[0153] At least one of the main bearing portion 131 and the secondary bearing portion 132 may be provided with at least one back pressure groove 1315a, 1315b, 1325a, 1325b formed by recesses, so as to communicate with the compression space V.

[0154] Back pressure chambers 1343a, 1343b, and 1343c can be formed at the inner ends of the blade grooves 1342a, 1342b, and 1342c. When the back pressure chambers 1343a, 1343b, and 1343c are connected to the back pressure grooves 1315a, 1315b, 1325a, and 1325b, they receive back pressure from the back pressure grooves 1315a, 1315b, 1325a, and 1325b, thereby applying pressure to the blades 1351, 1352, and 1353 toward the inner circumference of the cylinder 133.

[0155] Back pressure chambers 1343a, 1343b, and 1343c are located at the inner ends of blade slots 1342a, 1342b, and 1342c. The back pressure chambers can be understood as the spaces formed between the rear ends of blades 1351, 1352, and 1353 and the inner ends of blade slots 1342a, 1342b, and 1342c. The back pressure chambers 1343a, 1343b, and 1343c can communicate with the first main back pressure groove 1315a, the second main back pressure groove 1315b, the first auxiliary back pressure groove 1325a, and the second auxiliary back pressure groove 1325b, as described later. This allows them to receive back pressure from the first main back pressure groove 1315a, the second main back pressure groove 1315b, the first auxiliary back pressure groove 1325a, and the second auxiliary back pressure groove 1325b. As a result, the front end faces 1351a, 1351b, and 1351c of the blades 1351, 1352, and 1353 can be configured to contact the inner circumferential surface of the cylinder 133 or to be separated from the inner circumference of the cylinder 133 by a predetermined distance, depending on the intensity of the back pressure.

[0156] At least a portion of the back pressure chambers 1343a, 1343b, and 1343c are formed as arcuate surfaces, and the diameter of the arcuate surfaces of the back pressure chambers 1343a, 1343b, and 1343c can be smaller than the distance between the first main back pressure groove 1315a and the second main back pressure groove 1315b. Therefore, when connected to and receiving the emitted back pressure from the first main back pressure groove 1315a which is under high pressure due to the emitted back pressure, it is simultaneously connected to and receives the intermediate pressure from the second main back pressure groove 1315b, thereby preventing excessive increase in back pressure at the rear ends of the blades 1351, 1352, and 1353.

[0157] Figure 3The following example is shown: back pressure chambers 1343a, 1343b, and 1343c are connected to blade slots 1342a, 1342b, and 1342c with arcuate surfaces, and the diameter of the arcuate surfaces of the back pressure chambers 1343a, 1343b, and 1343c is smaller than the distance between the first main back pressure groove 1315a and the second main back pressure groove 1315b.

[0158] As an example, if high pressure is received from the first main back pressure groove 1315a and the first secondary back pressure groove 1325a, the blades 1351, 1352, and 1353 are extended to the maximum extent, thereby the front end faces 1351a, 1351b, and 1351c of the blades 1351, 1352, and 1353 contact the inner circumferential surface of the cylinder 133. If intermediate pressure is received from the second main back pressure groove 1315b and the second secondary back pressure groove 1325b, the blades 1351, 1352, and 1353 are extended relatively less, thereby the front end faces 1351a, 1351b, and 1351c of the blades 1351, 1352, and 1353 are configured to be spaced apart from the inner circumferential surface of the cylinder 133 by a predetermined distance.

[0159] As an example, the back pressure pockets 1315a, 1315b, 1325a, 1325b are connected to the back pressure chambers 1343a, 1343b, 1343c. The predetermined back pressure within the back pressure pockets 1315a, 1315b, 1325a, 1325b is then transmitted through the back pressure chambers 1343a, 1343b, 1343c to apply pressure to the rear ends of the blades 1351, 1352, 1353, and ultimately to the blade 1351. The front end faces 1351a, 1351b, and 1351c of blades 1352 and 1353 are adjacent to the suction port 1331 of cylinder 133, so that the high-pressure refrigerant of the front end faces 1351a, 1351b, and 1351c of blades 1351, 1352, and 1353 is bypassed to the suction port 1331. At this time, the front end faces 1351a, 1351b, and 1351c of blades 1351, 1352, and 1353 apply pressure to the inner circumferential surface of cylinder 133 and come into contact with it.

[0160] In this invention, an example in which back pressure grooves 1315a, 1315b, 1325a, and 1325b are provided in both the main bearing portion 131 and the secondary bearing portion 132 will be described.

[0161] Furthermore, one or more back pressure grooves 1315a, 1315b, 1325a, and 1325b may be formed in the main bearing portion 131 and the secondary bearing portion 132, respectively. In this invention, an example in which two back pressure grooves 1315a, 1315b, 1325a, and 1325b are provided in the main bearing portion 131 and the secondary bearing portion 132, respectively, will be described.

[0162] However, it is not necessary to limit it to this structure. The back pressure grooves 1315a, 1315b, 1325a, and 1325b of the present invention can be provided only in the main bearing part 131. Alternatively, one or three back pressure grooves 1315a, 1315b, 1325a, and 1325b can be provided in the main bearing part 131 and the secondary bearing part 132 respectively.

[0163] The main bearing portion 131 may include a main plate 1311 that is coupled to the cylinder 133 in such a way as to cover the upper side of the cylinder 133.

[0164] Additionally, the secondary bearing portion 132 may include a secondary plate 1321 that is coupled to the cylinder 133 in a manner that covers the lower side of the cylinder 133.

[0165] The back pressure grooves 1315a, 1315b, 1325a, and 1325b may include a first main back pressure groove 1315a and a second main back pressure groove 1315b, which are formed at a predetermined interval on the bottom surface of the main bearing portion 1311. Additionally, the back pressure grooves 1315a, 1315b, 1325a, and 1325b may also include a first secondary back pressure groove 1325a and a second secondary back pressure groove 1325b, which are formed at a predetermined interval on the top surface of the secondary bearing portion 132.

[0166] The detailed structure of the first main back pressure groove 1315a, the second main back pressure groove 1315b, the first auxiliary back pressure groove 1325a, and the second auxiliary back pressure groove 1325b will be explained later.

[0167] On the other hand, the compression section 130 can be understood as being composed of a cylinder 133, a roller 134, a plurality of blades 1351, 1352, 1353, a main bearing section 131, and a secondary bearing section 132. The main bearing section 131 and the secondary bearing section 132 are respectively disposed on the upper and lower sides of the cylinder 133, and together with the cylinder 133, form a compression space V. The roller 134 is rotatably disposed in the compression space V. The blades 1351, 1352, and 1353 are slidably inserted into the roller 134. The plurality of blades 1351, 1352, and 1353 divide the compression space V into a plurality of compression chambers by respectively abutting against the inner circumference of the cylinder 133.

[0168] Reference Figures 1 to 3 The main bearing portion 131 can be fixedly disposed in the intermediate outer shell 111 of the housing 110. For example, the main bearing portion 131 can be inserted into and welded to the intermediate outer shell 111.

[0169] The main bearing portion 131 can be tightly attached to the upper end of the cylinder 133. Thus, the main bearing portion 131 forms the upper side of the compression space V, and supports the top surface of the roller 134 in the axial direction, while supporting the upper half of the rotating shaft 123 in the radial direction.

[0170] The main bearing section 131 may include a main plate section 1311 and a main bushing section 1312.

[0171] The main board 1311 can be combined with the cylinder 133 in such a way that it covers the upper side of the cylinder 133.

[0172] The main bushing portion 1312 extends axially from the center of the main board portion 1311 toward the drive motor 120 and supports the upper half of the rotating shaft 123.

[0173] The main board portion 1311 can be formed in a disc shape, and its outer peripheral surface can be tightly attached to the inner peripheral surface of the intermediate outer shell 111. At least one or more discharge ports 1313a, 1313b, and 1313c can be 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 can be provided on the top surface of the main board portion 1311. A discharge silencer 137 with a discharge space (not indicated in the drawings) can be provided on the upper side of the main board portion 1311, the discharge space being able to accommodate the discharge ports 1313a, 1313b, and 1313c and the discharge valves 1361, 1362, and 1363. The discharge ports 1313a, 1313b, and 1313c will be described again later.

[0174] Reference Figure 4 and Figure 7 On the two axial sides of the main board 1311, a first main back pressure groove 1315a and a second main back pressure groove 1315b can be formed on the bottom surface facing the top surface of the roller 134.

[0175] The first main back pressure groove 1315a and the second main back pressure groove 1315b can be formed in an arc shape and are separated by a predetermined interval along the circumference. The inner circumferential surfaces of the first main back pressure groove 1315a and the second main back pressure groove 1315b are formed in a circular shape, while the outer circumferential surfaces of the two can be formed in an elliptical shape, taking into account the blade grooves 1342a, 1342b, and 1342c described later.

[0176] Additionally, refer to Figure 5 and Figure 7Although the illustration shows an example where the inner circumferential surfaces of the first main back pressure groove 1315a and the second main back pressure groove 1315b are both circular, while their outer circumferential surfaces are elliptical, this structure is not mandatory. Furthermore, as an example, the first main back pressure groove 1315a contains high-pressure refrigerant, thereby providing high-pressure back pressure to the rear ends of blades 1351, 1352, and 1353, while the second main back pressure groove 1315b contains intermediate-pressure refrigerant, thereby providing intermediate-pressure back pressure to the rear ends of blades 1351, 1352, and 1353.

[0177] The first main back pressure groove 1315a and the second main back pressure groove 1315b can be formed within the outer diameter range of the roller 134. Thus, the first main back pressure groove 1315a and the second main back pressure groove 1315b can be separated from the compression space V.

[0178] As an example, the back pressure on the first main back pressure groove 1315a can be higher than the back pressure on the second main back pressure groove 1315b. That is, since the first main back pressure groove 1315a is located near the discharge outlets 1313a, 1313b, and 1313c, it can provide discharge back pressure. In addition, the second main back pressure groove 1315b can form an intermediate pressure between the suction pressure and the discharge pressure.

[0179] Oil (refrigerant oil) can pass through the fine passage between the first main bearing protrusion 1316a and the top surface 134a of the roller 134 (described later) and flow into the first main back pressure groove 1315a.

[0180] The second main back pressure groove 1315b can be formed within the compression chamber that forms the intermediate pressure in the compression space V. Thus, the second main back pressure groove 1315b maintains the intermediate pressure.

[0181] The second main back pressure groove 1315b can create an intermediate pressure that is lower than that of the first main back pressure groove 1315a. Oil flowing into the main bearing portion hole 1312a of the main bearing portion 131 via the first oil passage 126a can flow to the second main back pressure groove 1315b. The second main back pressure groove 1315b can be formed within the compression chamber V2 that creates the suction pressure in the compression space V. Thus, the second main back pressure groove 1315b maintains the suction pressure.

[0182] Furthermore, a first main bearing protrusion 1316a and a second main bearing protrusion 1316b extending from the main bearing surface 1312b of the main bushing portion 1312 can be formed in the first main back pressure groove 1315a and the second main back pressure groove 1315b, respectively. Thus, the first main back pressure groove 1315a and the second main back pressure groove 1315b are sealed relative to the outside, while stably supporting the rotating shaft 123.

[0183] The first main bearing protrusion 1316a and the second main bearing protrusion 1316b have the same height, and an oil communication groove (not shown) or an oil communication hole (not shown) may be formed on the end face of the inner circumferential side of the second main bearing protrusion 1316b. Alternatively, the height of the inner circumferential side of the second main bearing protrusion 1316b may be lower than the height of the inner circumferential side of the first main bearing protrusion 1316a. As a result, high-pressure oil (refrigerant oil) flowing into the inner side of the main bearing surface 1312b can flow into the first main back pressure groove 1315a. The first main back pressure groove 1315a will generate a higher pressure (discharge pressure) than the second main back pressure groove 1315b.

[0184] On the other hand, the main bushing portion 1312 can be formed into a hollow bushing shape, and a first oil groove 1312c can be formed on the inner circumferential surface of the main bearing portion hole 1312a used to form the inner circumferential surface of the main bushing portion 1312. The first oil groove 1312c can be formed in a diagonal or spiral shape between the upper and lower ends of the main bushing portion 1312, and its lower end can communicate with the first oil through hole 126a.

[0185] Figure 4 An example is shown where the main bushing portion 1312 is formed upward in a hollow bushing shape on the main plate 1311, and a first oil groove 1312c formed along an oblique direction is formed on the inner circumferential surface of the main bearing portion hole 1312a used to form the inner circumferential surface of the main bushing portion 1312.

[0186] Although not illustrated, oblique or spiral oil grooves may be formed on the outer peripheral surface of the rotating shaft 123, i.e., the outer peripheral surface of the main support portion 123b.

[0187] Reference Figure 1 and Figure 2 The secondary bearing portion 132 can be tightly coupled to the lower end of the cylinder 133. Thus, the secondary bearing portion 132 forms the lower side of the compression space V, and supports the bottom surface of the roller 134 in the axial direction, while supporting the lower half of the rotating shaft 123 in the radial direction.

[0188] Reference Figure 2 and Figure 4 The secondary bearing portion 132 may include a secondary plate portion 1321 and a secondary bushing portion 1322.

[0189] The sub-plate 1321 can be combined with the cylinder 133 in such a way that it covers the lower side of the cylinder 133.

[0190] 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.

[0191] 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.

[0192] On the two axial sides of the sub-plate portion 1321, a first back pressure groove 1325a and a second back pressure groove 1325b can be formed on the top surface of the sub-plate portion 1321 facing the bottom surface of the roller 134.

[0193] With roller 134 as the reference, the first secondary back pressure groove 1325a and the second secondary back pressure groove 1325b can be symmetrical with the aforementioned first main back pressure groove 1315a and the second main back pressure groove 1315b, respectively.

[0194] In addition, the shapes of the first secondary back pressure groove 1325a and the second secondary back pressure groove 1325b can correspond to the shapes of the first main back pressure groove 1315a and the second main back pressure groove 1315b, respectively.

[0195] For example, the first secondary back pressure groove 1325a and the first main back pressure groove 1315a can be symmetrical to each other through the roller 134, and the second secondary back pressure groove 1325b and the second main back pressure groove 1315b can be symmetrical to each other through the roller 134.

[0196] On the other hand, a first bearing protrusion 1326a can be formed on the inner circumferential side of the first back pressure groove 1325a, and a second bearing protrusion 1326b can be formed on the inner circumferential side of the second back pressure groove 1325b.

[0197] However, depending on the circumstances, the first secondary back pressure groove 1325a and the second secondary back pressure groove 1325b can also be formed asymmetrically with respect to the roller 134 and the first primary back pressure groove 1315a and the second primary back pressure groove 1315b, respectively. For example, the first secondary back pressure groove 1325a and the second secondary back pressure groove 1325b can be formed at a different depth than the first primary back pressure groove 1315a and the second primary back pressure groove 1315b.

[0198] Additionally, an oil supply hole (not shown) may be formed between the first secondary back pressure groove 1325a and the second secondary back pressure groove 1325b, 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.

[0199] For example, the first section forming the inlet of the oil supply hole (not shown) is immersed in the oil storage space 110b, while the second section forming the outlet of the oil supply hole can be formed on the top surface of the sub-plate portion 1321 facing the bottom surface of the roller 134 (described later) along the rotation path of the back pressure chambers 1343a, 1343b, and 1343c. Thus, when the roller 134 rotates, the back pressure chambers 1343a, 1343b, and 1343c periodically communicate with the oil supply hole (not shown), thereby periodically supplying high-pressure oil stored in the oil storage space 110b to the back pressure chambers 1343a, 1343b, and 1343c through the oil supply hole (not shown). This allows each blade 1351, 1352, and 1353 to be stably supported on the inner circumferential surface 1332 of the cylinder 133.

[0200] On the other hand, the secondary bushing portion 1322 is formed as a hollow bushing shape, and a second oil groove 1322c can be formed on the inner circumferential surface of the secondary bearing portion hole 1322a used to form the inner circumferential surface of the secondary bushing portion 1322. The second oil groove 1322c can be formed in a straight line shape or an oblique line shape between the upper and lower ends of the secondary bushing portion 1322, and its upper end can communicate with the second oil passage hole 126b of the rotating shaft 123.

[0201] Although not illustrated, oblique or spiral oil grooves may be formed on the outer peripheral surface of the rotating shaft 123, i.e., the outer peripheral surface of the secondary support 123c.

[0202] Additionally, although not shown, the back pressure grooves 1315a, 1315b, 1325a, and 1325b may also be formed only on one side of the main bearing portion 131 or the secondary bearing portion 132.

[0203] On the other hand, as described above, discharge ports 1313a, 1313b, and 1313c can be formed in the main bearing portion 131.

[0204] However, the discharge ports 1313a, 1313b, and 1313c may also be formed in the secondary bearing portion 132, or respectively in the main bearing portion 131 and the secondary bearing portion 132, or they may be formed through the inner and outer circumferential surfaces of the cylinder 133. In this embodiment, the example in which the discharge ports 1313a, 1313b, and 1313c are formed in the main bearing portion 131 will be described.

[0205] Discharge ports 1313a, 1313b, and 1313c may be formed in only one form. However, in this embodiment, the discharge ports 1313a, 1313b, and 1313c may be formed along the compression travel direction (or the rotation direction of roller 134). Figure 3 In the middle, a plurality of them are formed by separating a preset interval (marked by arrows in the clockwise direction on roller 134).

[0206] Reference Figure 3 and Figure 7 The illustration shows an example where each pair forms a total of six discharge ports 1313a, 1313b, and 1313c that pass through the main bearing section 131.

[0207] Typically, in a rotary compressor 100 having blades 1351, 1352, and 1353, the roller 134 is configured eccentrically relative to the compression space V. Therefore, there is a near-contact point P1 between the outer circumferential surface 1341 of the roller 134 and the inner circumferential surface 1332 of the cylinder 133, and the discharge ports 1313a, 1313b, and 1313c are formed near this near point P1. Consequently, in the compression space V, the distance between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134 narrows significantly as it approaches the near point P1, making it difficult to ensure the area of ​​the discharge ports 1313a, 1313b, and 1313c.

[0208] In this embodiment, the discharge ports 1313a, 1313b, and 1313c can be divided into a plurality of discharge ports 1313a, 1313b, and 1313c, and formed along the rotation direction (or compression travel direction) of the roller 134. Alternatively, the plurality of discharge ports 1313a, 1313b, and 1313c can each be formed as one, or they can each be formed as a pair as in this embodiment.

[0209] For example, refer to Figure 3 The illustration shows an example of the discharge ports 1313a, 1313b, and 1313c of this embodiment arranged in the order of first discharge port 1313a, second discharge port 1313b, and third discharge port 1313c, starting from the discharge ports 1313a, 1313b, and 1313c that are disposed relatively far from the approach portion 1332a. Figure 3 In the example shown, a compression chamber can be connected to a plurality of discharge ports 1313a, 1313b, 1313c.

[0210] On the other hand, although not shown, the first interval between the first discharge port 1313a and the second discharge port 1313b, the second interval between the second discharge port 1313b and the third discharge port 1313c, and the third interval between the third discharge port 1313c and the first discharge port 1313a may also be formed to be identical to each other. The first interval, the second interval, and the third interval may 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, respectively.

[0211] Alternatively, a compression chamber can be configured to be connected to a plurality of discharge ports 1313a, 1313b, and 1313c, or a discharge port 1313a, 1313b, and 1313c can be configured not to be connected to a plurality of compression chambers. Alternatively, 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.

[0212] However, unlike this embodiment, when the blade slots 1342a, 1342b, and 1342c are not equally spaced, they can also be configured such that the circumferential lengths of each compression chamber V1, V2, and V3 are different, and one compression chamber is connected to a plurality of discharge ports 1313a, 1313b, and 1313c or one discharge port 1313a, 1313b, and 1313c is connected to a plurality of compression chambers.

[0213] Additionally, refer to Figure 3 In this embodiment, the discharge ports 1313a, 1313b, and 1313c may also extend to form discharge grooves (not shown). The discharge grooves may extend in an arc shape along the compression travel direction (the rotation direction of the roller 134). Thus, refrigerant that has not been discharged from the preceding compression chamber can be guided via the discharge grooves to the discharge ports 1313a, 1313b, and 1313c, which communicate with the following compression chamber, and discharged together with the refrigerant compressed in the following compression chamber. Therefore, overcompression can be suppressed by minimizing the refrigerant remaining in the compression space V, thereby improving the compressor efficiency.

[0214] The discharge slots described above can be formed to extend from the final discharge ports 1313a, 1313b, 1313c (e.g., the third discharge port 1313c). Typically, in a rotary compressor 100 having blades 1351, 1352, 1353, the compression space V is divided into an intake chamber and a discharge chamber on both sides by an approach portion (approach point 1332a). Therefore, considering the sealing between the intake chamber and the discharge chamber, the discharge ports 1313a, 1313b, 1313c cannot overlap with the approach point P1 located in the approach portion 1332a. Therefore, a residual space is formed along the circumferential direction between the approach point P1 and the discharge ports 1313a, 1313b, 1313c, between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134. The refrigerant cannot be discharged through the final discharge ports 1313a, 1313b, 1313c and remains in this residual space. This residual refrigerant eventually causes the pressure in the compression chamber to rise, which may lead to a decrease in compression efficiency due to over-compression.

[0215] However, as in this embodiment, when the discharge trough extends from the final discharge outlets 1313a, 1313b, 1313c toward the residual space, the refrigerant remaining in the residual space flows back toward the final discharge outlets 1313a, 1313b, 1313c via the discharge trough and is additionally discharged. Therefore, the decrease in compression efficiency caused by overcompression of the compression chamber can be effectively suppressed.

[0216] Although not shown in the diagram, in addition to the discharge slot, a residual discharge hole can also be formed in the residual space. The residual discharge hole can be formed such that its inner diameter is smaller than the inner diameter of the discharge ports 1313a, 1313b, and 1313c. The residual discharge hole can be formed differently from the discharge ports 1313a, 1313b, and 1313c, so that it will not be opened or closed by the discharge valve, but will always be open.

[0217] Furthermore, the plurality of discharge ports 1313a, 1313b, and 1313c can be opened and closed by the aforementioned discharge valves 1361, 1362, and 1363. Each discharge valve 1361, 1362, and 1363 can be a cantilevered, pilot-type valve with one end fixed and the other end free. Since such discharge valves 1361, 1362, and 1363 are widely used in ordinary rotary compressors 100, detailed descriptions of them are omitted.

[0218] Reference Figures 1 to 3 In this embodiment, the cylinder 133 can also be closely attached to the bottom surface of the main bearing portion 131 and fastened to the main bearing portion 131 together with the secondary bearing portion 132 by bolts. As described above, since the main bearing portion 131 is fixedly connected to the housing 110, the cylinder 133 can be fixedly connected to the housing 110 through the main bearing portion 131.

[0219] The cylinder 133 can be formed as an annular shape with a hollow portion in its center to form a compression space V. The hollow portion is sealed by the main bearing portion 131 and the secondary bearing portion 132, thereby forming the aforementioned compression space V, to which the roller 134 can be rotatably coupled.

[0220] Reference Figure 1 and Figure 2 The intake port 1331 can be formed by penetrating both the inner and outer circumferential surfaces of the cylinder 133. However, compared with... Figure 2 In contrast, the intake port 1331 may also be formed by penetrating the inner and outer peripheral surfaces of the main bearing portion 131 or the secondary bearing portion 132.

[0221] Centered on the approach point P1 described later, the intake port 1331 can be formed on one side in the circumferential direction. Centered on the approach point P1, the aforementioned discharge ports 1313a, 1313b, and 1313c can be formed on the main bearing portion 131 on the other side in the circumferential direction opposite to the intake port 1331.

[0222] 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 is formed into an asymmetrical elliptical shape by combining a plurality of ellipses, for example, four ellipses with different aspect ratios, into a single shape with two origins.

[0223] Specifically, the inner circumferential surface 1332 of the cylinder 133 in this embodiment can be formed such that the rotation center of the roller 134 (axis center or outer diameter center of the cylinder 133) is taken as the first origin Or, and a second origin O′ is biased towards the distal portion 1332b relative to the first origin Or.

[0224] The XY plane centered at the first origin Or will form the third and fourth quarter planes, while the XY plane centered at the second origin O′ will form the first and second quarter planes. The third quarter plane can be formed by the third ellipse, the fourth quarter plane by the fourth ellipse, the first quarter plane by the first ellipse, and the second quarter plane by the second ellipse.

[0225] Additionally, refer to Figure 3 In this embodiment, the inner circumferential surface 1332 of the cylinder 133 may include an approach portion 1332a, a remote portion 1332b, and a curved portion 1332c. The approach portion 1332a is the portion closest to the outer circumferential surface of the roller 134 (or the rotation center Or of the roller 134), the remote portion 1332b is the portion located at the position furthest from the outer circumferential surface 1341 of the roller 134, and the curved portion 1332c is the portion that connects the approach portion 1332a and the remote portion 1332b.

[0226] Reference Figure 3 and Figure 4 Roller 134 is rotatably disposed in the compression space V of cylinder 133, and a plurality of blades 1351, 1352, and 1353 can be inserted into roller 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 dividing the compression space V into three compression chambers using three blades 1351, 1352, and 1353 will be described.

[0227] In this embodiment, the outer peripheral surface 1341 of the roller 134 is formed in a circular shape. The rotating shaft 123 can be integrally formed at the rotation center Or of the roller 134, or it can be formed as a single unit and then assembled together. Thus, the rotation center Or of the roller 134 can be coaxial with the axis center (not marked) of the rotating shaft 123, and the roller 134 and the rotating shaft 123 can rotate concentrically together.

[0228] 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 configured to be eccentric 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 comes into contact with the inner circumferential surface 1332 of the cylinder 133, or more precisely, almost into contact with the approach portion 1332a, thereby forming an approach point P1.

[0229] As described above, the approach point P1 can be formed in the approach portion 1332a. Therefore, the imaginary line passing through the approach point P1 can be the minor axis of the elliptic curve constituting the inner circumferential surface 1332 of the cylinder 133.

[0230] In addition, a plurality of blade grooves 1342a, 1342b, and 1342c spaced apart from each other can be formed on the outer peripheral surface 1341 of the roller 134 along the circumferential direction, and a plurality of blades 1351, 1352, and 1353 described later can be slidably inserted into and engaged in each blade groove 1342a, 1342b, and 1342c respectively.

[0231] Reference Figure 4 The diagram illustrates the direction of compression travel (rotation direction of roller 134). Figure 3 The first blade groove 1342a, the second blade groove 1342b, and the third blade groove 1342c are arranged on the roller 134 (marked by a clockwise arrow). The first blade groove 1342a, the second blade groove 1342b, and the third blade groove 1342c can be spaced equally along the circumferential direction, or they can be formed with non-equal intervals, having the same width and depth. An example of an equally spaced arrangement is illustrated in this invention.

[0232] For example, the plurality of blade grooves 1342a, 1342b, and 1342c can be formed at a predetermined angle relative to the radial direction, thereby ensuring the lengths of blades 1351, 1352, and 1353. Therefore, even when the inner circumferential surface 1332 of the cylinder 133 is formed into an asymmetrical elliptical shape, 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, the blades 1351, 1352, and 1353 can be prevented from detaching from the blade grooves 1342a, 1342b, and 1342c, thereby increasing the design freedom for the inner circumferential surface 1332 of the cylinder 133.

[0233] 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 1351a, 1351b, and 1351c of each blade 1351, 1352, and 1353 that are in contact with the inner circumferential surface 1332 of the cylinder 133 are inclined toward the rotation direction of the roller 134. This can pull the compression start angle toward the rotation direction of the roller 134, so that compression can start quickly.

[0234] On the other hand, back pressure chambers 1343a, 1343b, and 1343c can be formed on the inner ends of blade slots 1342a, 1342b, and 1342c, respectively, and the back pressure chambers 1343a, 1343b, and 1343c are connected to blade slots 1342a, 1342b, and 1342c.

[0235] Back pressure chambers 1343a, 1343b, and 1343c are spaces that contain refrigerant (or oil) with discharge pressure or intermediate pressure on the rear side of each blade 1351, 1352, and 1353, i.e., on the rear end parts 1351c, 1352c, and 1353c of blades 1351, 1352, and 1353. The pressure of the refrigerant (or oil) filling these back pressure chambers 1343a, 1343b, and 1343c allows each blade 1351, 1352, and 1353 to apply pressure to the inner circumferential surface of the cylinder 133. Hereinafter, based on the direction of movement of blades 1351, 1352, and 1353, the direction toward the cylinder 133 is defined as forward, and the opposite direction is defined as rearward, for ease of explanation.

[0236] The back pressure chambers 1343a, 1343b, and 1343c can be configured such that their upper and lower ends are sealed by the main bearing portion 131 and the secondary bearing portion 132, respectively. The back pressure chambers 1343a, 1343b, and 1343c can be independently connected to the respective back pressure grooves 1315a, 1315b, 1325a, and 1325b, or they can be connected to each other through the back pressure grooves 1315a, 1315b, 1325a, and 1325b.

[0237] Furthermore, as described above, at least a portion of the back pressure chambers 1343a, 1343b, and 1343c are formed as arcuate surfaces, and the diameter of the arcuate surfaces of the back pressure chambers 1343a, 1343b, and 1343c can be smaller than the distance between the first main back pressure groove 1315a and the second main back pressure groove 1315b. Therefore, when receiving the emitted back pressure by communicating with the first main back pressure groove 1315a, which forms a high pressure due to the emitted back pressure, it also communicates with the second main back pressure groove 1315b at the same time. Thus, the intermediate pressure of the second main back pressure groove 1315b is also received, thereby preventing excessive increase in back pressure at the rear ends of the blades 1351, 1352, and 1353.

[0238] exist Figure 3 The figure illustrates an example in which back pressure chambers 1343a, 1343b, and 1343c are connected to blade slots 1342a, 1342b, and 1342c with arcuate surfaces, and the diameter of the arcuate surfaces of the back pressure chambers 1343a, 1343b, and 1343c is smaller than the distance between the first main back pressure groove 1315a and the second main back pressure groove 1315b.

[0239] Reference Figure 3 and Figure 4 In this embodiment, a plurality of blades 1351, 1352, and 1353 can be slidably inserted into each blade groove 1342a, 1342b, and 1342c. Thus, the plurality of blades 1351, 1352, and 1353 can be formed to have a shape substantially the same as that of each blade groove 1342a, 1342b, and 1342c.

[0240] For example, taking the rotation direction of roller 134 as a reference, the plurality of blades 1351, 1352, and 1353 can be defined as the first blade 1351, the second blade 1352, and the third blade 1353, respectively. The first blade 1351 can be inserted into the first blade groove 1342a, the second blade 1352 can be inserted into the second blade groove 1342b, and the third blade 1353 can be inserted into the third blade groove 1342c. Figure 3 and Figure 4 The diagram illustrates this structure.

[0241] Multiple blades 1351, 1352, and 1353 can all be formed in the same shape.

[0242] Specifically, the plurality of blades 1351, 1352, and 1353 can be formed into approximately cuboid shapes, the front end faces 1351a, 1351b, and 1351c that contact the inner circumferential surface 1332 of the cylinder 133 can be formed into curved surfaces, and the rear end faces 1351b, 1352b, and 1353b that face each of the back pressure chambers 1343a, 1343b, and 1343c can be formed into straight surfaces.

[0243] On the other hand, Figure 3 The illustration shows an example where the leading edge face 1351a of the first blade 1351 begins to contact the cylinder 133 on the suction port 1331 side. Since a high pressure is provided from the rear end of the first blade 1351, no vibration occurs, and the first blade 1351 contacts the inner circumferential surface of the cylinder 133. When the leading edge face 1351a of the first blade 1351 passes the suction port 1331, the high-pressure refrigerant between the leading edge faces 1351a, 1351b, 1351c of the first blade 1351 and the inner circumference of the cylinder 133 bypasses the suction port 1331.

[0244] At this time, since the high pressure back pressure is not applied to the back pressure grooves 1315a, 1315b, 1325a, and 1325b that are connected to the first main back pressure groove 1315a and the first auxiliary back pressure groove 1325a, the front end face 1351a of the first blade 1351 will not be pushed backward to contact the inner circumferential surface of the cylinder 133.

[0245] In response, in the rotary compressor 100 of the present invention, at least one back pressure groove 1315a, 1315b, 1325a, 1325b is provided in at least one of the main bearing portion 131 and the secondary bearing portion 132, and is recessed to communicate with the compression space V; back pressure chambers 1343a, 1343b, 1343c are formed at the inner ends of the blade grooves 1342a, 1342b, 1342c to accommodate the rear ends of the blades 1351, 1352, 1353, so as to communicate with the back pressure grooves 1315a, 1315b, 1325a, 1325b. The back pressure is received from the back pressure grooves 1315a, 1315b, 1325a, 1325b and applied to the blades 1351, 1352, 1353, which exert pressure toward the inner circumferential surface of the cylinder 133. The back pressure grooves 1315a, 1315b, 1325a, 1325b are connected to the back pressure chambers 1343a, 1343b, 1343c until the high-pressure refrigerant bypasses from the suction port 1331, so that the front end faces 1351a, 1351b, 1351c of the blades 1351, 1352, 1353 come into contact with the inner circumferential surface of the cylinder 133.

[0246] Therefore, the high-pressure refrigerant that may accumulate between the front ends of blades 1351, 1352, and 1353 and the inner circumferential surface of cylinder 133 can be bypassed through the suction port 1331 on the side of cylinder 133, and the discharge back pressure can be maintained until the high-pressure refrigerant bypasses through the suction port 1331 on the side of cylinder 133, so that blades 1351, 1352, and 1353 are not pushed backward.

[0247] The operation of the rotary compressor 100 of the present invention will be described.

[0248] In the rotary compressor 100, when power is applied to the drive motor 120, the rotor 122 of the drive motor 120 and the rotating shaft 123 connected to the rotor 122 rotate, and the roller 134 connected to or integrally formed with the rotating shaft 123 rotates together with the rotating shaft 123.

[0249] Thus, through the centrifugal force generated by the rotation of the roller 134 and the back pressure of the back pressure chambers 1343a, 1343b, 1343c used to support the rear end faces 1351, 1352, 1353, 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.

[0250] Therefore, the compression space V of the cylinder 133 is divided into compression chambers V1, V2, and V3 corresponding to the number of blades 1351, 1352, and 1353 by a plurality of blades 1351, 1352, and 1353. When each compression chamber V1, V2, and V3 moves with the rotation of the roller 134, its volume changes due to the shape of the inner circumferential surface 1332 of the cylinder 133 and the eccentricity of the roller 134. The refrigerant to be drawn into each compression chamber V1, V2, and V3 repeatedly undergoes a series of processes, being compressed while moving along the roller 134 and the blades 1351, 1352, and 1353, and being discharged into the internal space of the housing 110.

[0251] In particular, the refrigerant flowing into the suction port 1331 of the cylinder 133 will pass through the suction passage 1333 and flow into the compression space V via the suction guides 1317 and 1327. As described above, in this invention, the refrigerant moves a predetermined distance from the side of the cylinder 133 toward the main bearing portion 131 and the secondary bearing portion 132 via the refrigerant suction flow path and flows into the compression space V in the vertical direction. Therefore, it is possible to reduce blade contact force and surface pressure and improve reliability, and also to improve suction loss.

[0252] Of course, depending on the shape of the cylinder 133, the refrigerant flowing into the intake port 1331 of the cylinder 133 can also pass through the first intake passage 1333a and the second intake passage 1333b, and pass through the intake guides 1317 and 1327 formed in at least one of the main bearing portion 131 and the secondary bearing portion 132, and flow into the compression space V. Alternatively, as described above, if the upper end face and the lower end face of the cylinder 133 have inflow guides 1335, the refrigerant flowing into the intake port 1331 of the cylinder 133 can also pass through the intake passage 1333 and flow into the compression space V via the inflow guides 1335.

[0253] With this structure, in the rotary compressor 100 of the present invention, the existing structure of the suction port 1331 formed simply along the transverse direction is transformed into a structure of suction passage 1333 and suction guides 1317 and 1327 in the longitudinal or inclined direction. This partially changes the direction of the refrigerant suction flow path to the direction of the main bearing section 131 and the secondary bearing section 132, thereby improving reliability by reducing blade contact force and reducing surface pressure, and improving suction loss.

[0254] Furthermore, in the rotary compressor 100 of the present invention, inflow guides 1335 are formed on the top and bottom surfaces of the cylinder 133, thereby allowing the refrigerant to pass more smoothly through the suction passage 1333 and flow into the compression space V, thus reducing refrigerant suction losses. Additionally, the refrigerant can also flow more smoothly into the compression space through the inflow guides 1335 before being contained in the suction guides 1317 and 1327. In particular, the inflow guides 1335 increase the suction area from the suction passage 1333 into the compression space V, thereby maintaining a lower surface pressure.

[0255] Furthermore, in the rotary compressor 100 of the present invention, the refrigerant drawn in through the suction port 1331 will pass through the first suction passage 1333a and the second suction passage 1333b, and the refrigerant passing through the first suction passage 1333a and the second suction passage 1333b respectively will be guided by the main suction guide 1317 and the auxiliary suction guide 1327 and flow into the compression space V respectively, thereby reducing the loss of the suction flow path and forming an advantageous structure that can improve the suction efficiency of the rotary compressor 100.

[0256] In the rotary compressor of the present invention, the refrigerant passes through the suction port and flows into the compression space via the suction passage, thereby reducing the surface pressure in the suction port area and improving reliability, and also improving suction loss.

[0257] Furthermore, in the rotary compressor of the present invention, suction guides are formed in the main bearing section and the auxiliary bearing section, thereby enabling the refrigerant that has passed through the suction passage to be contained and the refrigerant to be supplied to the compression space, thereby reducing the wear phenomenon caused by the decrease in surface pressure at the suction port of the cylinder.

[0258] Furthermore, in the rotary compressor of the present invention, by constructing the above-described suction passage and suction guide, the mechanical losses of the compressor itself can be improved under the condition of the same efficiency.

[0259] Furthermore, in the rotary compressor of the present invention, the existing structure of the suction port, which is simply formed along the transverse direction, is formed into a suction passage and suction guide in the longitudinal or inclined direction. This partially changes the direction of the refrigerant suction flow path to the direction of the main bearing and the secondary bearing, thereby improving reliability by reducing blade contact force and reducing surface pressure, and improving suction loss.

[0260] Furthermore, in the rotary compressor of the present invention, inflow guides are formed on the top and bottom surfaces of the cylinder, thereby allowing the refrigerant to pass more smoothly through the suction passage and flow into the compression space, thus reducing refrigerant suction losses. Additionally, the refrigerant can flow more smoothly into the compression space through the inflow guides before being contained in the suction guides. In particular, the inflow guides increase the suction area from the suction passage into the compression space, thereby maintaining a lower surface pressure.

[0261] Furthermore, in the rotary compressor of the present invention, the refrigerant drawn in through the suction port passes through the first suction passage and the second suction passage, and the refrigerant passing through the first suction passage and the second suction passage is guided by the main suction guide and the auxiliary suction guide and flows into the compression space respectively, thereby reducing the loss of the suction flow path and forming an advantageous structure that can improve the suction efficiency of the rotary compressor.

[0262] The rotary compressor 100 described above is not limited to the configuration and method of the above embodiments, and various modifications can be made by selectively combining all or part of the various embodiments.

[0263] It will be self-evident to those skilled in the art that the present invention can be implemented in other specific forms without departing from the spirit and essential technical features of the invention. Therefore, it should be understood that the detailed description above is not limiting in any respect, but rather exemplary. The scope of the invention should be determined by a reasonable interpretation of the claims, and all modifications within the equivalent scope of the invention fall within the scope of the invention.

Claims

1. A rotary compressor, wherein, include: The cylinder barrel has an inner circumferential surface that is formed into an annular shape to create a compression space; A roller is rotatably disposed in the compression space of the cylinder, and a plurality of blade grooves are formed along the outer peripheral surface of the roller at predetermined intervals, providing back pressure on one side inside the plurality of blade grooves; as well as A plurality of blades are slidably inserted into a plurality of blade slots and rotate together with the roller. The leading edge faces of the plurality of blades contact the inner circumferential surface of the cylinder using the back pressure, thereby dividing the compression space into a plurality of compression chambers. The cylinder has a refrigerant suction flow path. The suction flow path includes: a suction inlet, communicating with the compression space and formed laterally, for drawing in and providing refrigerant; and a suction passage, formed in a direction intersecting the suction inlet, and enabling communication between the compression space and the suction inlet. The refrigerant can flow into the compression space through the suction port and the suction passage; The rotary compressor further includes a main bearing section and a secondary bearing section, which are respectively disposed at both ends of the cylinder and are spaced apart from each other to form two surfaces of the compression space. At least one of the main bearing portion and the secondary bearing portion is provided with a suction guide portion, the suction guide portion being recessed to communicate with the suction passage and the compression space, the suction guide portion accommodating refrigerant passing through the suction passage and being able to supply the refrigerant to the compression space; The main bearing portion is disposed at the upper end of the cylinder to form the top surface of the compression space. The suction guide includes a main suction guide recessed in the main bearing portion, which connects the suction passage and the compression space. The main suction guide accommodates refrigerant passing through the suction passage and is capable of directing the refrigerant upward and providing it to the compression space. The secondary bearing portion is located at the lower end of the cylinder to form the bottom surface of the compression space. The suction guide also includes a secondary suction guide, which is recessed in the secondary bearing portion to connect the suction passage and the compression space. The secondary suction guide accommodates refrigerant passing through the suction passage and is able to direct the refrigerant downwards and provide it to the compression space. There is a point of near contact between the outer circumferential surface of the roller and the inner circumferential surface of the cylinder. At least one of the main inhalation guide and the auxiliary inhalation guide is formed as an asymmetrical structure having a side portion facing the approach point and another side portion formed on the opposite side of the side portion, wherein the side portion is longer than the other side portion. The intake passage is formed to extend through the top and bottom surfaces of the cylinder in a direction parallel to the vertical. Inflow guides are formed on the top and bottom surfaces of the cylinder to enable communication between the compression space and the suction passage. The inflow guide has a preset width and depth, allowing the refrigerant flowing in the suction passage to flow into the compression space. The inhalation guide has a predetermined depth. The depth of the inflow guide is less than or equal to the depth of the suction guide. The inflow guide has a shape formed by cutting through a portion of the inner circumferential surface, top surface, and bottom surface of the cylinder adjacent to the suction passage.

2. The rotary compressor according to claim 1, wherein, The inhalation pathway has an elliptical cross-section.

3. A rotary compressor, wherein, include: case; A drive motor is located inside the housing and generates rotational power; The cylinder barrel has an inner circumferential surface that is formed into an annular shape to create a compression space; A roller is rotatably disposed in the compression space of the cylinder, and a plurality of blade grooves are formed along the outer peripheral surface of the roller at predetermined intervals, providing back pressure on one side inside the plurality of blade grooves; A plurality of blades are slidably inserted into a plurality of blade slots and rotate together with the roller. The front end faces of the plurality of blades contact the inner circumferential surface of the cylinder by the back pressure, thereby dividing the compression space into a plurality of compression chambers. as well as The main bearing section and the auxiliary bearing section are respectively disposed at both ends of the cylinder barrel, and are spaced apart from each other to form two surfaces of the compression space. The cylinder has a refrigerant intake flow path. The suction flow path includes: a suction inlet, communicating with the compression space and formed laterally, for drawing in and providing refrigerant; and a suction passage, formed in a direction intersecting the suction inlet, and enabling communication between the compression space and the suction inlet. The refrigerant can flow into the compression space through the suction port and the suction passage; At least one of the main bearing portion and the secondary bearing portion is provided with a suction guide portion, the suction guide portion being recessed to communicate with the suction passage and the compression space, the suction guide portion accommodating refrigerant passing through the suction passage and being able to supply the refrigerant to the compression space; The main bearing portion is disposed at the upper end of the cylinder to form the top surface of the compression space. The suction guide includes a main suction guide recessed in the main bearing portion, which connects the suction passage and the compression space. The main suction guide accommodates refrigerant passing through the suction passage and is capable of directing the refrigerant upward and providing it to the compression space. The secondary bearing portion is located at the lower end of the cylinder to form the bottom surface of the compression space. The suction guide also includes a secondary suction guide, which is recessed in the secondary bearing portion to connect the suction passage and the compression space. The secondary suction guide accommodates refrigerant passing through the suction passage and is able to direct the refrigerant downwards and provide it to the compression space. There is a point of near contact between the outer circumferential surface of the roller and the inner circumferential surface of the cylinder. At least one of the main inhalation guide and the auxiliary inhalation guide is formed as an asymmetrical structure having a side portion facing the approach point and another side portion formed on the opposite side of the side portion, wherein the side portion is longer than the other side portion. The intake passage is formed to extend through the top and bottom surfaces of the cylinder in a direction parallel to the vertical. Inflow guides are formed on the top and bottom surfaces of the cylinder to enable communication between the compression space and the suction passage. The inflow guide has a preset width and depth, allowing the refrigerant flowing in the suction passage to flow into the compression space. The inhalation guide has a predetermined depth. The depth of the inflow guide is less than or equal to the depth of the suction guide. The inflow guide has a shape formed by cutting through a portion of the inner circumferential surface, top surface, and bottom surface of the cylinder adjacent to the suction passage.

4. The rotary compressor according to claim 3, wherein, The drive motor includes: The stator is fixedly disposed on the inner circumferential surface of the housing; The rotor is rotatably inserted into the interior of the stator; and A rotating shaft is incorporated inside the rotor and rotates with the rotor, and is connected to the roller and transmits rotational force that enables the roller to rotate.

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