CN218266336U

CN218266336U - Rotary compressor

Info

Publication number: CN218266336U
Application number: CN202222568088.XU
Authority: CN
Inventors: 辛镇雄; 姜胜敏
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2022-04-29
Filing date: 2022-09-27
Publication date: 2023-01-10
Anticipated expiration: 2032-09-27
Also published as: KR20230154333A; US20230349382A1; KR102626191B1; EP4269801A1

Abstract

A rotary compressor comprising: a driving motor disposed in the inner space of the housing; a rotating shaft coupled to a rotor of the driving motor, the rotating shaft having a hollow shape through which an oil supply passage passes; a cylinder barrel disposed in the inner space of the housing to form a compression space; a roller which is provided on the rotating shaft and accommodated in the compression space, and which is eccentrically disposed with respect to an inner circumferential surface of the cylinder tube; a vane slidably inserted into a vane groove provided in the roller; and a main bearing and a sub bearing which are respectively arranged at two sides of the cylinder barrel in the axial direction and form a compression space together with the cylinder barrel, wherein at least one of the main bearing and the sub bearing is provided with a discharge port for discharging the refrigerant compressed in the compression space to the inner space of the shell, a plurality of backpressure grooves communicated with the rear side of the blade are formed at one side of the discharge port along the circumferential direction in a separated mode, and the backpressure groove closest to the discharge port in the plurality of backpressure grooves is communicated with the inner space of the shell through a backpressure passage part penetrating through at least one of the main bearing and the sub bearing.

Description

Rotary compressor

Technical Field

The utility model relates to a blade rotary compressor of rotatory roller is inserted to blade slidable.

Background

The rotary compressor may be classified into a manner in which the vane is slidably inserted into the cylinder and is in contact with the roller, and a manner in which the vane is slidably inserted into the roller and is in contact with the cylinder. The former is generally called a roller eccentric rotary compressor (hereinafter, referred to as a rotary compressor), and the latter is called a vane concentric rotary compressor (hereinafter, referred to as a vane rotary compressor).

In the rotary compressor, the vane inserted into the cylinder is drawn out toward the roller by an elastic force or a back pressure force and is brought into contact with the outer circumferential surface of the roller. In contrast, in the vane rotary compressor, the vanes inserted into the rollers are rotated together with the rollers, drawn out toward the cylinder tube by the centrifugal force and the back pressure, and are brought into contact with the inner circumferential surface of the cylinder tube.

In the rotary compressor, compression chambers corresponding to the number of vanes are formed independently for each rotation of the roller, and the suction stroke, the compression stroke, and the discharge stroke are simultaneously executed in each compression chamber. On the other hand, in the vane rotary compressor, compression chambers corresponding to the number of vanes are formed continuously for each rotation of the roller, and the suction stroke, the compression stroke, and the discharge stroke are sequentially executed in each compression chamber. Therefore, the compression ratio of the vane rotary compressor will be higher than that of the rotary compressor. Therefore, the vane rotary compressor is more suitable for using high-pressure refrigerants such as R32, R410a, CO2 having low Ozone Depletion Potential (ODP) and Global Warming Potential (GWP).

Such a vane rotary compressor is disclosed in patent document 1 (japanese patent laid-open: JP 2013-213438A), patent document 2 (US 2015/0132168A 1), and patent document 3 (korean patent laid-open No. 10-2020-0057542), respectively. The vane rotary compressor disclosed in these patent documents discloses a structure in which a plurality of vanes are slidably inserted into a rotating roller.

In these patent documents, back pressure chambers are formed in the rear end portions of the blades, respectively, and the back pressure chambers communicate with back pressure grooves provided in the main bearing and the sub-bearing. The back pressure groove is divided into a first groove for forming an intermediate pressure and a second groove for forming a discharge pressure or an intermediate pressure close to the discharge pressure. The first groove communicates with the back pressure chamber on the upstream side and the second groove communicates with the back pressure chamber on the downstream side with reference to a reference point (approach point or contact point) at which the roller approaches the cylinder.

However, in the conventional vane rotary compressor as described above, the compression cycle becomes short, so that the pressure difference between the front and rear sides of the vane will increase. Therefore, the operation of the blade becomes unstable, and there is a possibility that a so-called blade fluttering phenomenon occurs in which the front surface of the blade collides with the inner circumferential surface of the cylinder. The chattering phenomenon may be concentrated around a reference point near the final discharge port, which is a position where the pressure in the compression chamber is highest. This may cause wear of the inner circumferential surface of the cylinder tube or the front surface of the vane in the periphery of the reference point. Therefore, not only vibration noise around the reference point may be increased, but also leakage between compression chambers may be generated due to abrasion between the cylinder tube and the vane, thereby generating a suction loss as the specific volume of the sucked refrigerant increases, and consequently, the compressor efficiency may be lowered.

In addition, in the conventional vane rotary compressor, a shaking phenomenon around a reference point is serious at the initial start of the compressor, which may cause an initial start failure, and thus, the efficiency of the compressor may be further reduced, and a cooling and heating effect of a cooling and heating apparatus to which the compressor is applied may be delayed.

In addition, in the conventional vane rotary compressor, the vanes reciprocate in a state where the axial side surfaces thereof are in contact with the main bearing and/or the sub bearing, and in this process, the vanes may be excessively closely attached to the main bearing and/or the sub bearing, so that the reciprocating motion of the vanes is discontinuously performed. As a result, the blade fluttering phenomenon becomes further large, which not only increases the damage of the cylinder and/or the blade but also increases the suction loss.

In addition, in the case of using a high-pressure refrigerant such as R32, R410a, CO2, the above problem may be further aggravated. That is, in the case of using a high-pressure refrigerant, even if the volume of the compression chamber is reduced by increasing the number of the vanes, only a cooling capacity of the same level as that in the case of using a relatively low-pressure refrigerant such as R134a can be obtained. However, if the number of vanes is increased, the compression period between the vanes and the cylinder is correspondingly shortened, so that the fluttering phenomenon of the vanes around the reference point may be aggravated. This may be more affected under heating low temperature conditions, high pressure ratio conditions (Pd/Ps ≧ 6), and high speed operating conditions (80 Hz or more).

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a can reduce the rotary compressor of the vibration noise that produces because of the blade shake when compressor operation.

Another object of the present invention is to provide a rotary compressor capable of suppressing a chattering phenomenon of a vane by increasing a force applied to the cylinder side by the vane passing through the vicinity of a reference point adjacent to a final discharge port when the compressor is in operation.

Further, an object of the present invention is to provide a rotary compressor capable of suppressing uneven wear of blades by uniformly applying a pressing force to the blades passing through the vicinity of a reference point when the compressor is in operation.

Another object of the present invention is to provide a rotary compressor capable of improving the efficiency of the compressor by suppressing the initial start delay of the compressor.

Another object of the present invention is to provide a rotary compressor capable of quickly starting initial start-up by suppressing leakage of refrigerant near a reference point during operation of the compressor.

Further, the present invention has an object to provide a rotary compressor capable of further improving the compressor efficiency by suppressing the refrigerant leakage near the reference point during the operation of the compressor and reducing the friction loss in the other sections except for the vicinity of the reference point.

It is still another object of the present invention to provide a rotary compressor capable of continuously reciprocating the blades.

Further, an object of the present invention is to provide a rotary compressor capable of continuously reciprocating blades by reducing friction loss between the blades and a main bearing and/or a sub-bearing facing the blades.

Further, an object of the present invention is to provide a rotary compressor capable of improving a lubrication effect by smoothly supplying oil between a blade and a main bearing and/or a sub-bearing facing the blade.

It is still another object of the present invention to provide a rotary compressor capable of effectively suppressing a fluttering phenomenon of a vane even when a high-pressure refrigerant such as R32, R410a, or CO2 is used.

In order to realize the utility model discloses a purpose, the utility model provides a rotary compressor, include: a driving motor disposed in the inner space of the housing; a rotating shaft coupled to a rotor of the driving motor, the rotating shaft having a hollow shape through which an oil supply passage passes; a cylinder barrel disposed in an inner space of the housing to form a compression space; a roller that is provided on the rotary shaft and is accommodated in the compression space, the roller being disposed eccentrically with respect to an inner peripheral surface of the cylinder tube; a vane slidably inserted into a vane groove provided in the roller; and a main bearing and a sub bearing which are respectively arranged on both axial sides of the cylinder tube and form the compression space together with the cylinder tube, wherein at least one of the main bearing and the sub bearing is provided with a discharge port for discharging the refrigerant compressed in the compression space into the internal space of the housing, a plurality of back pressure grooves communicating with the rear side of the blade are formed at one side of the discharge port and are separated from each other in the circumferential direction, and the back pressure groove closest to the discharge port among the plurality of back pressure grooves communicates with the internal space of the housing through a back pressure passage portion penetrating at least one of the main bearing and the sub bearing.

In order to realize the purpose of the utility model, the utility model provides a rotary compressor who includes casing, driving motor, rotation axis, cylinder, roller, blade, main bearing and auxiliary bearing is provided. The driving motor is disposed in the inner space of the housing. The rotating shaft is coupled to a rotor of the driving motor, and an interior of the rotating shaft is formed in a hollow shape through which an oil supply passage passes. The cylinder is disposed in the inner space of the housing and forms a compression space. The roller is provided on the rotary shaft, is accommodated in the compression space, and is disposed eccentrically with respect to an inner circumferential surface of the cylinder tube. The vane is slidably inserted into a vane groove provided in the roller. The main bearing and the auxiliary bearing are respectively arranged on two axial sides of the cylinder barrel and form the compression space together with the cylinder barrel. A discharge port for discharging the refrigerant compressed in the compression space to the internal space of the casing is formed in at least one of the main bearing and the sub bearing, and a plurality of back pressure grooves communicating with the rear side of the vane are formed at positions spaced apart from each other in the circumferential direction on the side of the discharge port.

Among the plurality of back pressure grooves, the back pressure groove closest to the discharge port may communicate with the internal space of the housing through a back pressure passage portion that penetrates at least one of the main bearing and the sub-bearing. Thereby, the back pressure groove closest to the discharge port can form the discharge pressure or the super discharge pressure higher than the discharge pressure, and strongly support the vane passing near the reference point adjacent to the discharge port toward the cylinder side. Thereby, the vibration noise can be reduced by suppressing the flutter phenomenon of the vane near the reference point, and the compression efficiency can be improved by suppressing the abrasion between the vane and the cylinder. In addition, by suppressing leakage between the compression chambers, it is possible to prevent an initial start-up delay of the compressor, and thus it is possible to prevent a cooling and heating effect from being delayed when the compressor is applied to a cooling and heating apparatus.

As an example, bearing holes into which the rotating shaft is inserted and which support the rotating shaft are formed in the main bearing and the sub bearing, respectively. The back pressure groove closest to the discharge port may be radially spaced from an inner circumferential surface of the bearing hole to be separated from the bearing hole. Thus, the back pressure groove closest to the discharge port forms a substantially closed space, and the vane can be strongly supported to the cylinder side by securing the discharge pressure or the back pressure higher than the discharge pressure.

As another example, one or more oil supply holes may be formed in the middle of the oil supply passage, and the one or more oil supply holes may penetrate from the inner circumferential surface of the oil supply passage to the outer circumferential surface of the rotary shaft. The back pressure passage portion may have an inner diameter smaller than or equal to an inner diameter of the oil supply hole. This can suppress oil shortage in the other back pressure groove due to excessive outflow of the oil sucked to the upper side through the oil supply passage through the back pressure passage portion.

As another example, one or more oil supply holes may be formed in the middle of the oil supply passage, and the one or more oil supply holes may penetrate from the inner circumferential surface of the oil supply passage to the outer circumferential surface of the rotary shaft. The back pressure passage portion may be located on one axial side of the oil supply hole. This makes it possible to ensure the rigidity of the rotary shaft while the oil sucked to the upper side through the oil supply passage is rapidly moved to the back pressure passage portion.

As another example, the back pressure passage portion may eccentrically communicate from the center of the back pressure groove to a reference point side where the roller and the cylinder are closest to each other. Thus, the vane blocks the back pressure passage portion at a position closest to the discharge port, so that the corresponding back pressure groove is closed and a high back pressure can be ensured.

As another example, the back pressure passage portion may be formed at a position that periodically overlaps with the vane when the vane reciprocates. Thereby, the back pressure passage portion is periodically shielded by the vane, so that the corresponding back pressure groove forms a closed space and a high back pressure can be ensured.

As another example, the back pressure passage portion may have an inner diameter smaller than a width of the vane. Thereby, the back pressure passage portion is shielded by the vane, so that the corresponding back pressure groove forms a closed space and a high back pressure can be ensured.

As another example, the back pressure passage portion may include a first back pressure hole and a second back pressure hole. The first back pressure hole may penetrate from an inner circumferential surface of the oil supply passage to an outer circumferential surface of the rotary shaft. The second back pressure hole may penetrate at least one of the main bearing and the sub bearing to communicate with the first back pressure hole, and the second back pressure hole may communicate with the back pressure groove. Thus, the high-pressure oil can flow into the back pressure groove closest to the discharge port by the centrifugal force generated when the rotary shaft rotates.

Specifically, the inner diameter of the second back pressure hole may be smaller than or equal to the inner diameter of the first back pressure hole. Therefore, the oil that has flowed into the back pressure groove closest to the discharge port is prevented from easily flowing out through the back pressure passage portion when the vane moves backward, and the back pressure of the corresponding back pressure groove can be maintained.

Further, a communication groove may be formed between the first back pressure hole and the second back pressure hole. The communication groove may have a sectional area larger than a sectional area of at least one of the first back pressure hole and the second back pressure hole. Thus, not only the back pressure passage portion can be provided in the rotary shaft, the main bearing, and the sub-bearing, but also machining errors in the back pressure passage portion can be reduced, and by preventing the back pressure passage portion from being clogged, oil can be smoothly supplied to the back pressure groove.

Specifically, the communication groove may be formed in a circular arc shape to periodically communicate the first back pressure hole and the second back pressure hole. Thus, in the operation of the compressor, the back pressure passage portions are periodically blocked so that the respective back pressure grooves periodically form closed spaces and oil outflow in the respective back pressure grooves is minimized, thereby making it possible to secure a high back pressure.

In addition, the communication groove may be formed in a circular shape to continuously communicate the first back pressure hole and the second back pressure hole. Thus, oil is continuously supplied to the back pressure groove nearest to the discharge port without interruption, and the back pressure in the corresponding back pressure groove can be prevented from being weakened by the lack of oil.

As another example, one end of the back pressure passage portion may communicate with the back pressure groove closest to the discharge port, and the other end thereof may communicate with the internal space of the housing through at least one of the main bearing and the sub bearing. This makes it possible to easily form the back pressure passage portion and to quickly flow the oil into the back pressure groove.

As another example, a volume of a back pressure groove, which is the closest to the discharge port, among the plurality of back pressure grooves may be smaller than volumes of the back pressure grooves other than the back pressure groove closest to the discharge port. Thus, the pressure of the back pressure groove closest to the discharge port can be maintained at a higher pressure than the other back pressure grooves.

Specifically, the circular arc length of the back pressure groove, which is the most adjacent to the discharge port, among the plurality of back pressure grooves, may be smaller than the circular arc lengths of the other back pressure grooves except for the back pressure groove which is the most adjacent to the discharge port. Thus, the increase in friction loss can be suppressed by keeping the pressure of the back pressure groove closest to the discharge port at a higher pressure than the other back pressure grooves and minimizing the section where the vane and the cylinder tube are in close contact with each other.

In addition, a depth of a back pressure groove, which is most adjacent to the discharge port, of the plurality of back pressure grooves may be smaller than depths of other back pressure grooves except the back pressure groove which is most adjacent to the discharge port. This makes it possible to easily maintain the pressure in the back pressure groove closest to the discharge port at a higher pressure than the other back pressure grooves.

As another example, a lubrication portion may be formed on a radially outer side of the back pressure groove of at least one of the main bearing and the sub bearing. The lubrication portion may be formed such that at least a portion thereof overlaps in the radial direction with the back pressure groove that is most adjacent to the discharge port. This makes it possible to suppress discontinuous sliding of the blades due to close contact with the main bearing and/or the sub-bearing, and to improve the compression efficiency and reliability by reducing the chattering phenomenon of the blades.

Specifically, the lubrication portion may include a lubrication groove and a lubrication passage. The lubrication groove may be spaced apart from the back pressure groove. The lubrication passage may connect between the lubrication groove and the inner space of the housing, and guide the oil stored in the inner space of the housing to the lubrication groove. Thereby, the oil stored in the inner space of the housing is quickly supplied to the lubrication groove, so that a wide and thick oil film can be formed between the vane and the bearing surface facing thereto.

In addition, the lubrication groove may be formed as one groove extending in the circumferential direction. The lubrication passage may be formed in one or more than one in a circumferential direction of the lubrication groove. Thus, by increasing the circumferential length of the lubrication groove that is in contact with the vane, an oil film can be formed quickly and uniformly between the vane and the bearing surface that faces the vane.

In addition, the lubrication groove may be formed as a plurality of grooves spaced apart from each other in a circumferential direction. The lubrication passage may be independently communicated with the plurality of lubrication grooves, respectively. Thus, by shortening the circumferential length of the lubrication groove, the friction loss between the vane and the lubrication groove intersecting the reciprocation direction of the vane can be reduced.

In addition, the lubrication portion may include one or more lubrication passages penetrating the sub-bearing. One end of the lubrication passage may be open to the vane at one axial side of the sub-bearing, and the other end thereof may be open to the inner space of the housing at the other axial side of the sub-bearing. This makes it possible to further reduce the friction loss between the vane and the lubrication groove intersecting the reciprocating direction of the vane by further shortening the circumferential length of the lubrication portion while facilitating the formation of the lubrication portion.

In addition, the lubrication portion may include a lubrication groove and a lubrication passage. The lubrication groove may be spaced apart from the back pressure groove. The lubrication passage may extend from at least one of the back pressure grooves other than the back pressure groove nearest to the discharge port and communicate with the lubrication groove. Thereby, the lubrication portion can be easily formed and the oil supply length of the lubrication portion can be minimized, so that oil can be quickly supplied between the vane and the bearing.

Specifically, the axial depth of the lubrication groove may be less than or equal to the axial depth of the back pressure groove connected to the lubrication groove. Thus, the back pressure of the back pressure groove can be appropriately maintained by suppressing excessive outflow of the oil of the back pressure groove to the lubrication groove.

Drawings

Fig. 1 is a sectional view showing an embodiment of a vane rotary compressor of the present embodiment.

Fig. 2 is a perspective view showing a part of the compression unit of fig. 1 in an exploded manner.

Fig. 3 is a plan view showing the compression unit of fig. 2 assembled.

Fig. 4 is a perspective view showing the sub-bearing and the rotary shaft of fig. 2 in an exploded manner.

Fig. 5 is an assembled top view of fig. 4.

Fig. 6 is a cross-sectional view taken along the "I-view" line of fig. 5.

FIG. 7 is a cross-sectional view taken along line X of FIG. 5.

Fig. 8 is a perspective view showing another example of the communication groove of fig. 2.

Fig. 9 is a sectional view illustrating a process of supplying oil to the back pressure groove in the rotary compressor of the present embodiment.

Fig. 10 is a graph comparing blade contact force at different rotation angles of the vane rotary compressor of the present embodiment with that of the prior art and shown.

Fig. 11 is a perspective view showing another embodiment of the back pressure passage portion of fig. 2.

Fig. 12 is an assembled sectional view of fig. 11.

Fig. 13 is an exploded perspective view of another embodiment of the back pressure passage portion.

Fig. 14 is an assembled sectional view of fig. 13.

Fig. 15 is an exploded perspective view of another embodiment of the compression unit of fig. 1.

Fig. 16 is a plan view showing the main bearing of fig. 15.

Fig. 17 is a plan view showing the sub-bearing of fig. 15.

Fig. 18 is an assembled cross-sectional view of fig. 15.

Fig. 19 is a perspective view showing another embodiment of the lubrication portion of fig. 15.

Fig. 20 is a cross-sectional view of fig. 19.

Fig. 21 is a perspective view showing still another embodiment of the lubrication portion of fig. 15.

Fig. 22 is a cross-sectional view of fig. 21.

Detailed Description

Hereinafter, the vane rotary compressor according to the present invention will be described in detail with reference to the illustrated embodiment.

In the present invention, the blade spring is provided in the roller, which can be equally applied to the blade rotary compressor in which the blade is slidably inserted into the roller. For example, the present invention can be applied not only to a vane rotary compressor provided with an elliptical (hereinafter, asymmetric elliptical) cylinder tube in which the inner peripheral surface of the cylinder tube is formed with a plurality of curvatures, but also to a vane rotary compressor provided with a circular cylinder tube in which the inner peripheral surface of the cylinder tube is formed with a single curvature. In addition, the present invention can be applied not only to a vane rotary compressor in which the vane grooves into which the vanes are slidably inserted are formed to be inclined at a predetermined angle with respect to the radial direction of the roller, but also to a vane rotary compressor in which the vane grooves are formed in the radial direction of the roller in the same manner. Hereinafter, a typical example will be described in which the inner circumferential surface of the cylinder has an asymmetric elliptical shape and the vane grooves are inclined with respect to the radial direction of the roller.

Fig. 1 is a sectional view showing an embodiment of a vane rotary compressor of the present embodiment, fig. 2 is a perspective view showing a portion of a compression part of fig. 1 in an exploded manner, and fig. 3 is a plan view showing the compression part of fig. 2 in an assembled manner.

Referring to fig. 1, the vane rotary compressor of the present embodiment includes: a housing 110, a driving motor 120, and a compression part 130. The driving motor 120 is disposed in the upper internal space 110a of the housing 110, the compressing unit 130 is disposed in the lower internal space 110a of the housing 110, and the driving motor 120 and the compressing unit 130 are connected by the rotating shaft 123.

The housing 110 is a portion constituting an external appearance of the compressor, and may be classified into a vertical type or a horizontal type according to an installation form of the compressor. The vertical type is a configuration in which the drive motor 120 and the compression unit 130 are arranged on both the upper and lower sides in the axial direction, and the horizontal type is a configuration in which the drive motor 120 and the compression unit 130 are arranged on both the left and right sides. The housing of the present embodiment is explained mainly in a vertical type. However, the same applies to the case where the housing is configured to be horizontal.

The housing 110 includes: an intermediate housing 111 formed in a cylindrical shape; a lower case 112 covering a lower end of the middle case 111; and an upper case 113 covering an upper end of the middle case 111.

The driving motor 120 and the compressing part 130 may be inserted and fixedly coupled to the middle casing 111, and the suction pipe 115 penetrates the middle casing 111 and is directly connected to the compressing part 130. The lower housing 112 may be hermetically coupled to a lower end of the middle housing 111, and an oil storage space 110b for storing oil to be supplied to the compression part 130 may be formed at a lower side of the compression part 130. The upper housing 113 may be hermetically coupled to an upper end of the intermediate housing 111, and an oil separation space 110c may be formed above the driving motor 120 to separate oil from the refrigerant discharged from the compression part 130.

The driving motor 120 is a part constituting an electric part, which provides power for driving the compression part 130. The driving motor 120 includes: stator 121, rotor 122, and rotation shaft 123.

The stator 121 is fixedly provided inside the housing 110, and may be press-fitted and fixed to an inner circumferential surface of the housing 110 by a shrink fit or the like. For example, the stator 121 may be press-fitted and fixed to the inner circumferential surface of the intermediate housing 110 a.

The rotor 122 may be rotatably inserted into the stator 121, and the rotation shaft 123 may be press-fitted into the center of the rotor 122. Thereby, the rotation shaft 123 rotates concentrically with the rotor 122.

An oil supply passage 125 having a hollow hole shape is formed at the center of the rotary shaft 123, and a first oil through hole 126a, a second oil through hole 126b, and a first back pressure hole 138a formed to penetrate the outer circumferential surface of the rotary shaft 123 are formed in the middle of the oil supply passage 125. The first oil supply hole 126a is formed to belong to a range of a main bushing portion 1312 described later, and the second oil supply hole 126b and the first back pressure hole 138a are formed to belong to a range of a sub bearing portion 1322.

One or a plurality of first oil supply holes 126a and second oil supply holes 126b may be formed. In this embodiment, a plurality of first oil supply holes 126a and second oil supply holes 126b are formed in the circumferential direction.

The first back pressure hole 138a may communicate with a second back pressure hole 138b described later. Accordingly, the high-pressure oil passing through the first back pressure hole 138a can be directly supplied to the third sub back pressure groove 1325c, which will be described later, through the second back pressure hole 138b. Later, the first back pressure hole 138a is explained again together with the second back pressure hole 138b.

An oil suction device 127 may be provided at the middle or lower end of the oil supply passage 125. The oil absorber 127 may use a gear pump, a viscous pump, a centrifugal pump, or the like. This embodiment shows an example in which a centrifugal pump is used. Thus, if the rotary shaft 123 rotates, the oil filled in the oil storage space 110b of the housing 110 may be pumped up by the oil suction device 127 and sucked up along the oil supply passage 125, and as described above, a portion of the oil may be supplied to the third sub back pressure groove 1325c through the first back pressure hole 138a, another portion of the oil may be supplied to the sub bearing surface 1322b of the sub bush portion 1322 through the second oil supply hole 126b, and another portion of the oil may be supplied to the main bearing surface 1312b of the main bush portion 1312 through the first oil supply hole 126 a.

On the other hand, a roller 134 described later may be provided on the rotation shaft 123. The roller 134 may be extended as a single body at the rotation shaft 123, or may be post-assembled after the rotation shaft 123 and the roller 134 are separately fabricated. In the present embodiment, the rotation shaft 123 is inserted into the roller 134 and then assembled, for example, a shaft hole 1341 provided at the center of the roller 134 is axially inserted, the rotation shaft 123 may be press-fitted into the shaft hole 1341 and coupled thereto, or the rotation shaft 123 may be coupled to the shaft hole 1341 so as to be movable in the axial direction. When the rotary shaft 123 is coupled to the roller 134 so as to be movable in the axial direction, a rotation preventing portion (not shown) is provided between the rotary shaft 123 and the roller 134, so that the rotary shaft 123 can be restrained in the circumferential direction with respect to the roller 134.

The compressing part 130 includes: main bearing 131, sub-bearing 132, cylinder 133, roller 134, and blade 135. The main bearing 131 and the sub bearing 132 are respectively disposed at upper and lower sides of the cylinder 133, and form a compression space V together with the cylinder 133, the roller 134 is rotatably disposed in the compression space V, and the vane 135 is slidably inserted into the roller 134 to divide the compression space V into a plurality of compression chambers.

Referring to fig. 1 to 3, the main bearing 131 may be fixedly provided to the middle housing 111 of the shell 110. For example, the main bearing 131 may be inserted and welded to the middle housing 111.

The main bearing 131 may be closely fitted and coupled to the upper end of the cylinder 133. Thereby, main bearing 131 forms the upper side of compression space V, and supports the top surfaces of rollers 134 in the axial direction and the upper half of rotary shaft 123 in the radial direction.

The main bearing 131 may include a main plate portion 1311 and a main bushing portion 1312. The main plate 1311 covers the upper side of the cylinder 133 and is coupled to the cylinder 133, and the main bushing 1312 extends in the axial direction from the center of the main plate 1311 toward the drive motor 120 and supports the upper half of the rotary shaft 123.

The main plate 1311 may be formed in a disc shape, and the outer peripheral surface of the main plate 1311 may be closely attached and fixed to the inner peripheral surface of the intermediate case 111. The main plate 1311 may have one or more discharge ports 1313 penetrating therethrough in the axial direction. In the present embodiment, a plurality of

discharge ports

1313a, 1313b, 1313c are formed at predetermined intervals from each other in the circumferential direction, and a plurality of

discharge valves

1361, 1362, 1363 for opening and closing the

discharge ports

1313a, 1313b, 1313c are provided on the top surface of the main plate 1311. A discharge muffler 137 having a discharge space (not shown) may be provided above the main plate 1311 to accommodate the plurality of

discharge ports

1313a, 1313b, 1313c and the

discharge valves

1361, 1362, 1363.

As described above, as the

discharge ports

1313a, 1313b, 1313c are formed in the main bearing (or sub bearing) 131 instead of the cylinder 133, the structure of the cylinder 133 is simplified, and the cylinder can be easily processed. In addition, by keeping the surface pressure constant while reducing the surface pressure between the front side of the blades 135 on the peripheries of the

discharge ports

1313a, 1313b, 1313c and the inner peripheral surface of the cylinder 133 facing the front surface of the blades 135, and on the other hand, reducing the chattering phenomenon of the

blades

1351, 1352, 1353, it is possible to suppress wear and vibration noise between the front side of the

blades

1351, 1352, 1353 and the inner peripheral surface of the cylinder 133 facing the front surface of the

blades

1351, 1352, 1353.

A main back pressure groove (pocket) 1315 may be formed in the main sliding surface 1311a, which is the bottom surface of the main plate portion 1311 facing the top surface of the roller 134, in both side surfaces in the axial direction of the main plate portion 1311.

The main back pressure groove 1315 may be formed in one, but may be formed in plural in the circumferential direction. As shown in fig. 2 and 3, in the present embodiment, a plurality of main

back pressure grooves

1315a, 1315b, 1315c are formed at a predetermined interval from each other in the rotation direction of the roller 134 with reference to a reference point P to be described later.

For example, the main back pressure groove 1315 of the present embodiment may be constituted by a first main back pressure groove 1315a, a second main back pressure groove 1315b, and a third main back pressure groove 1315c. These first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c may be formed in a circular arc shape and spaced apart from each other at a predetermined interval in the circumferential direction.

The inner and outer circumferential surfaces of the first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c may be formed in a circular shape, respectively, or the inner circumferential surface thereof may be formed in a circular shape and the outer circumferential surface thereof may be formed in an elliptical shape in consideration of a blade groove 1343 described later. In the present embodiment, an example is shown in which the outer peripheral surface of the first main back pressure groove 1315a is formed in an elliptical shape.

The first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c may be formed within the outer diameter range of the roller 134. Thereby, the first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c may be separated from the compression space V. However, the first main back pressure groove 1315a, the second main back pressure groove 1315b, and the third main back pressure groove 1315c may finely communicate through a gap between both side surfaces as long as there is no additional sealing member between the main sliding surface 1311a, which is the bottom surface of the main plate portion 1311, and the top surface of the roller 134 facing the main sliding surface 1311 a.

The first main back pressure groove 1315a may form a pressure lower than that of the second main back pressure groove 1315b, for example, an intermediate pressure between the suction pressure and the discharge pressure. In other words, oil (refrigerant oil) can flow into the first main back pressure groove 1315a through a fine passage between the first main bearing convex portion 1316a and the top surface of the roller 134, which will be described later. The first main back pressure groove 1315a may be formed in a range of a compression chamber constituting an intermediate pressure in the compression space V. Thereby, the first main back pressure groove 1315a will maintain the first intermediate pressure.

The second main back pressure groove 1315b forms a higher pressure than the first main back pressure groove 1315a, for example, forms a discharge pressure or forms a second intermediate pressure between a first intermediate pressure close to the discharge pressure and the discharge pressure. In other words, as the inner circumferential surface of the second main back pressure groove 1315b is completely opened toward the main bearing hole 1312a, or a part of the inner circumferential surface thereof is opened, the oil flowing into the main bearing hole 1312a of the main bearing 1312 through the first oil supply hole 126a may flow into the second main back pressure groove 1315b with almost no pressure reduction. In addition, the second main back pressure groove 1315b may be formed in a range that constitutes a compression chamber of the discharge pressure or substantially the discharge pressure in the compression space V. Thereby, the second main back pressure groove 1315b will maintain the discharge pressure or a second intermediate pressure close to the discharge pressure.

The third main back pressure groove 1315c forms a higher pressure than the second main back pressure groove 1315b, for example, forms an excess discharge pressure higher than the discharge pressure. In other words, the inner peripheral surface of the third main back pressure groove 1315c is spaced apart from the main bearing hole 1312a and blocked, while the third main back pressure groove 1315c is separated from the inner space of the housing. In addition, the third main back pressure groove 1315c may be formed in a range that constitutes a compression chamber of the discharge pressure in the compression space V. Thereby, the third main back pressure groove 1315c maintains the excessive discharge pressure higher than the discharge pressure. The third primary back pressure groove 1315c will be described again later together with a third secondary back pressure groove 1325c described later.

Further, a first main bearing convex portion 1316a, a second main bearing convex portion 1316b, and a third main bearing convex portion 1316c extending from the main bearing surface 1312b of the main bushing portion 1312 may be formed on the inner peripheral side of the first main back pressure groove 1315a, the second main back pressure groove 1315b, and the third main back pressure groove 1315c, respectively. Accordingly, the first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c can stably support the rotary shaft 123 while being sealed from the outside.

First main bearing convex portion 1316a, second main bearing convex portion 1316b, and third main bearing convex portion 1316c may be formed to have the same height or may be formed to have different heights.

For example, when first main bearing convex portion 1316a, second main bearing convex portion 1316b, and third main bearing convex portion 1316c are formed to have the same height, an oil communication groove (not shown) or an oil communication hole (not shown) may be formed in an end surface of second main bearing convex portion 1316b so that an inner peripheral surface and an outer peripheral surface of second main bearing convex portion 1316b communicate with each other. Accordingly, high-pressure oil (refrigerant oil) flowing into the main bearing surface 1312b can be made to flow into the second main back pressure groove 1315b through the oil communication groove (not shown) or the oil communication hole (not shown).

On the other hand, when first main bearing convex portion 1316a, second main bearing convex portion 1316b, and third main bearing convex portion 1316c are formed to have different heights from each other, the height of second main bearing convex portion 1316b may be lower than the heights of first main bearing convex portion 1316a and third main bearing convex portion 1316c. Accordingly, high-pressure oil (refrigerant oil) flowing into the main bearing hole 1312a can flow into the second main back pressure recess 1315b over the second main bearing protrusion 1316 b.

Referring to fig. 1 to 3, the sub-bearing 132 may be closely attached and coupled to a lower end of the cylinder 133. Thereby, the sub-bearing 132 forms the lower side surface of the compression space V, and supports the lower half of the rotary shaft 123 in the radial direction while supporting the bottom surface of the roller 134 in the axial direction.

The secondary bearing 132 may include a secondary plate portion 1321 and a secondary bushing portion 1322. The sub plate portion 1321 covers the lower side of the cylinder 133 and is coupled to the cylinder 133, and the sub bush portion 1322 extends axially from the center of the sub plate portion 1321 toward the lower housing 112 and supports the lower half of the rotary shaft 123.

The sub-plate portion 1321 may be formed in a disc shape like the main plate portion 1311, and the outer peripheral surface of the sub-plate portion 1321 may be spaced from the inner peripheral surface of the intermediate case 111.

On both side surfaces of the sub-plate portion 1321 in the axial direction, a sub back pressure groove 1325 corresponding to the above-described main back pressure groove 1315 may be formed on a sub sliding surface 1321a, which is a top surface of the sub-plate portion 1321 facing the bottom surface of the roller 134. One or a plurality of the sub back pressure grooves 1325 may be formed. As shown in fig. 2 and 3, in the present embodiment, a plurality of secondary

back pressure grooves

1325a, 1325b, 1325c may be formed at a predetermined interval from each other in a circumferential direction.

For example, the sub back pressure groove 1325 may be configured as a first sub back pressure groove 1325a, a second sub back pressure groove 1325b, and a third sub back pressure groove 1325c in the rotation direction of the roller 134 with reference to the reference point P, and the first sub back pressure groove 1325a, the second sub back pressure groove 1325b, and the third sub back pressure groove 1325c may be formed symmetrically with the first main back pressure groove 1315a, the second main back pressure groove 1315b, and the third main back pressure groove 1315c, respectively, with the roller 134 as the center.

In other words, the first sub back pressure groove 1325a may be formed symmetrically to the first main back pressure groove 1315a, the second sub back pressure groove 1325b may be formed symmetrically to the second main back pressure groove 1315b, and the third sub back pressure groove 1325c may be formed symmetrically to the third main back pressure groove 1315c. Thus, the first sub bearing convex portions 1326a may be formed on the inner peripheral side of the first sub back pressure recessed groove 1325a, the second sub bearing convex portions 1326b may be formed on the inner peripheral side of the second sub back pressure recessed groove 1325b, and the third sub bearing convex portions 1326c may be formed on the inner peripheral side of the third sub back pressure recessed groove 1325c.

The description of the first, second, and third sub back

pressure grooves

1325a, 1325b, and 1325c will be replaced by the description of the first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c. Note that the description of the first sub-bearing convex portion 1326a, the second sub-bearing convex portion 1326b, and the third sub-bearing convex portion 1326c will be replaced by the description of the first main bearing convex portion 1316a, the second main bearing convex portion 1316b, and the third main bearing convex portion 1316c.

However, according to circumstances, the first, second, and third sub back

pressure grooves

1325a, 1325b, and 1325c may be formed asymmetrically with respect to the first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c, respectively, centering on the roller 134. For example, the first sub back pressure groove 1325a may be formed deeper than the first main back pressure groove 1315a, the second sub back pressure groove 1325b may be formed deeper than the second main back pressure groove 1315b, and the third sub back pressure groove 1325c may be formed deeper than the third main back pressure groove 1315c.

The third sub back pressure groove 1325c forms a higher pressure than the second sub back pressure groove 1325b, that is, a super discharge pressure, similarly to the third main back pressure groove 1315c described above. Later, the third sub back pressure groove 1325c is explained again together with the third main back pressure groove 1315c.

Although not shown, only any one of the main

back pressure grooves

1315a, 1315b, and 1315c and the sub back

pressure grooves

1325a, 1325b, and 1325c may be formed. In this case, the sub back

pressure grooves

1325a, 1325b, 1325c may be formed to be relatively adjacent to the oil storage space.

The sub-bush 1322 has the second back pressure hole 138b formed therein. For example, one end of the second back pressure hole 138b may be opened to the inner circumferential surface of the sub bush portion 1322 toward the first back pressure hole 138a of the rotary shaft 123, and the other end of the second back pressure hole 138b may be opened to the bottom surface of the third sub back pressure groove 1325c to communicate with the third sub back pressure groove 1325c. Accordingly, the oil that has flowed through the first back pressure hole 138a between the outer circumferential surface of the rotary shaft 123 and the inner circumferential surface of the sub bushing portion 1322 flows directly into the third sub back pressure recess 1325c through the second back pressure hole 138b, and when the corresponding vane 135 that has passed through the third sub back pressure recess 1325c is retracted in the third sub back pressure recess 1325c that is almost closed except for the second back pressure hole 138b, the oil forms ultrahigh pressure together with the corresponding back pressure chamber 1344. Which will be explained again later.

On the other hand, as described above, the discharge port 1313 may be formed in the main bearing 131. However, the discharge port 1313 may be formed in the sub-bearing 132, formed separately from the main bearing 131 and the sub-bearing 132, or may be formed so as to penetrate between the inner circumferential surface and the outer circumferential surface of the cylinder 133. In the present embodiment, an example is shown in which the discharge port 1313 is formed in the main bearing 131.

As described above, the discharge port 1313 may be formed with the plurality of

discharge ports

1313a, 1313b, 1313c at predetermined intervals in the compression travel direction (or the rotation direction of the roller), and the plurality of

discharge ports

1313a, 1313b, 1313c may be arranged at predetermined intervals from each other in the circumferential direction, that is, the rotation direction of the roller 134.

The plurality of

discharge ports

1313a, 1313b, 1313c may be formed one for each, but may be formed in pairs of two as in the present embodiment. For example, the discharge port 1313 may be arranged in the order of the first discharge port 1313a, the second discharge port 1313b, and the third discharge port 1313c from the discharge port closest to the proximity portion 1332a. Accordingly, even if the distance between the inner circumferential surface 1332 of the cylinder 133 and the outer circumferential surface 1342 of the roller 134 is narrowed as the distance approaches the reference point P in the compression space V, the compressed refrigerant can be smoothly discharged by securing the discharge area of the discharge port 1313, and over-compression or pressure pulsation can be suppressed.

Although not shown, when the

vane grooves

1343a, 1343b, 1343c described later are formed at unequal intervals, the circumferential lengths of the compression chambers V1, V2, V3 may be formed differently, and a plurality of discharge ports may communicate with one compression chamber or a plurality of compression chambers may communicate with one discharge port.

Referring to fig. 1 to 3, the cylinder tube 133 of the present embodiment may be closely attached to the bottom surface of the main bearing 131 and fastened to the main bearing 131 together with the sub-bearing 132 by bolts. Thus, the cylinder tube 133 can be fixedly coupled to the housing 110 by the main bearing 131.

The cylinder 133 may be formed in a ring shape having a hollow space portion to form a compression space V at the center thereof. The hollow space portion is sealed by the main bearing 131 and the sub-bearing 132 to form the compression space V, and the roller 134 described later may be rotatably coupled to the compression space V.

The cylinder 133 may have a suction port 1331 formed to penetrate from the outer circumferential surface to the inner circumferential surface. However, the suction port may be formed through the main bearing 131 or the sub-bearing 132.

The suction port 1331 may be formed on one side in the circumferential direction around a reference point P described later. The discharge port 1313 may be formed on the main bearing 131 on the other side in the circumferential direction, which is the opposite side of the suction port 1331, with the reference point P as the center.

The inner peripheral surface 1332 of the cylinder 133 may be formed in an elliptical shape. The inner peripheral surface 1332 of the cylinder tube 133 of the present embodiment may be formed in an asymmetrical elliptical shape by combining a plurality of ellipses, for example, four ellipses having different aspect ratios from each other so as to have two origins.

Specifically, the inner peripheral surface 1332 of the cylinder 133 of the present embodiment may be formed to have a first origin O, which is a center of the roller 134 Or a rotation center (a shaft center Or an outer diameter center of the cylinder) Or of the roller 134 described later, and a second origin O' which is offset to the reference point P side from the first origin O.

An X-Y plane formed with the first origin O as a center forms a third quadrant Q3 and a fourth quadrant Q4, and an X-Y plane formed with the second origin O' as a center forms a first quadrant Q1 and a second quadrant Q2. The third quadrant Q3 is formed by a third ellipse, the fourth quadrant Q4 is formed by a fourth ellipse, the first quadrant Q1 is formed by a first ellipse, and the second quadrant Q2 is formed by a second ellipse.

The inner peripheral surface 1332 of the cylinder tube 133 of the present embodiment may include a proximal portion 1332a, a distal portion 1332b, and a curved surface portion 1332c. The proximal portion 1332a is a portion closest to the outer circumferential surface 1341 of the roller 134 (or the rotation center of the roller), the distal portion 1332b is a portion farthest from the outer circumferential surface 1342 of the roller 134, and the curved portion 1332c is a portion connecting between the proximal portion 1332a and the distal portion 1332 b.

The proximity portion 1332a may be defined as a reference point P, and the first quadrant Q1 and the fourth quadrant Q4 may be divided with the proximity portion 1332a as a center. The suction port 1331 may be formed in the first quadrant Q1 and the discharge port 1313 may be formed in the fourth quadrant Q4 about the proximity portion 1332a. Thus, when the

vanes

1351, 1352, 1353 pass through the reference point P, the compression surfaces of the

rollers

1351, 1352, 1353 on the rotation direction side receive a low suction pressure, while the compression rear surfaces on the opposite side to the rotation direction side receive a high discharge pressure. Then, during the passage of the roller 134 through the reference point P, the maximum variable pressure is applied between the

front faces

1351a, 1352a, 1353a of the

respective blades

1351, 1352, 1353, which are in contact with the inner peripheral surface of the cylinder 133, and the rear faces 1351b, 1352b, 1353b of the

respective blades

1351, 1352, 1353, which face the

back pressure chambers

1344a, 1344b, 1344c, and therefore, the

blades

1351, 1352, 1353 may be greatly shaken.

Referring to fig. 1 to 3, the roller 134 of the present embodiment is rotatably provided in the compression space V of the cylinder 133, and a plurality of

vanes

1351, 1352, 1353, which will be described later, may be inserted into the roller 134 at predetermined intervals in a circumferential direction. Thus, the compression space V may be divided into compression chambers corresponding to the number of the plurality of

blades

1351, 1352, 1353. In the present embodiment, an example will be described mainly in which the plurality of

blades

1351, 1352, 1353 are three and the compression space V is divided into three compression chambers V1, V2, V3.

As described above, the roller 134 may be post-assembled after the rotation shaft 123 is extended as a single body or the rotation shaft 123 and the roller 134 may be separately manufactured. In the present embodiment, the following description will be focused on an example in which the roller 134 and the rotation shaft 123 are post-assembled.

However, even in the case where the roller 134 extends as a single body at the rotation shaft 123, the rotation shaft 123 and the roller 134 may be formed similarly to the present embodiment, and the basic operation effect thereof may be approximately similar to the present embodiment. However, in the case where the roller 134 is assembled to the rotation shaft 123 after being assembled as in the present embodiment, the roller 134 may be formed of a material different from the rotation shaft 123, for example, a hard material lighter than the rotation shaft 123. In this case, not only the roller 134 can be easily processed, but also the compressor efficiency can be improved by reducing the weight of the rotating body including the roller 134.

The roller 134 of this embodiment may be formed as a single body, i.e., a one-piece roller formed of a roller body (not labeled). However, the roller 134 is not necessarily formed as an integral roller. For example, the roller 134 may be formed as a separate roller separated into a plurality of roller bodies (not shown). This will be described later using another embodiment in which the integrated roller 134 configured as a single body is mainly described.

Referring to fig. 1 to 3, the roller 134 of the present embodiment may be formed in a ring shape having a shaft hole 1341 provided at the center thereof. For example, the roller 134 may have an inner circumferential surface and an outer circumferential surface, and the inner circumferential surface and the outer circumferential surface of the roller 134 may be respectively formed in a circular shape. However, the inner peripheral surface of the roller 134 may be formed as a continuous surface, and the outer peripheral surface of the roller 134 may be formed as a discontinuous surface provided with the opening surfaces of the vane grooves 1343. Only one vane groove 1343 may be formed, or a plurality of vane grooves may be formed. In the present embodiment, an example is shown in which a plurality of

blade grooves

1343a, 1343b, 1343c are formed at a predetermined interval from each other in the circumferential direction. Thus, the outer peripheral surface of the roller 134 of the present embodiment can be formed as discontinuous surfaces corresponding to the number of the

blade grooves

1343a, 1343b, 1343c.

In addition, the rotation center Or of the roller 134 may be positioned coaxially with the axial center (not labeled) of the rotation shaft 123, and the roller 134 may concentrically rotate together with the rotation shaft 123. However, as described above, the inner peripheral surface 1332 of the cylinder 133 is formed in an asymmetric elliptical shape that is biased in a specific direction, and the rotation center Or of the roller 134 may be disposed eccentrically with respect to the outer diameter center Oc of the cylinder 133. Thus, the outer peripheral surface 1342 of the roller 134 is almost in contact with the inner peripheral surface 1332 of the cylinder 133, more precisely, the proximity portion 1332a to form the reference point P.

As described above, the reference point P may be formed at the proximity portion 1332a. Thus, the imaginary line passing through the reference point P can correspond to the minor axis of the elliptic curve constituting the inner peripheral surface 1332 of the cylinder 133.

Specifically, the roller 134 may be formed with a plurality of

blade grooves

1343a, 1343b, 1343c, and the

blades

1351, 1352, 1353 described later may be slidably inserted into and coupled to the

blade grooves

1343a, 1343b, 1343c, respectively. The plurality of

blade grooves

1343a, 1343b, 1343c may be formed at predetermined intervals in the circumferential direction, the outer circumferential surface 1342 of the roller 134 may be formed with an opening surface that opens in the radial direction, and the inner end portions on the opposite sides of the opening surface may be formed in a shape that is closed in the radial direction by being provided with

back pressure chambers

1344, 1344a, 1344b, 1344c, which will be described later, respectively.

The plurality of

blade slots

1343a, 1343b, 1343c may be defined as a first blade slot 1343a, a second blade slot 1343b, and a third blade slot 1343c in the compression traveling direction (the rotation direction of the roller), and the first blade slot 1343a, the second blade slot 1343b, and the third blade slot 1343c may be equally or unequally spaced apart from each other in the circumferential direction and formed identically to each other, respectively.

For example, each of the

blade slots

1343a, 1343b, 1343c may be formed to be inclined at a predetermined angle with respect to the radial direction, respectively, so that the length of the

blades

1351, 1352, 1353 can be sufficiently secured. Accordingly, when the inner peripheral surface 1332 of the cylinder 133 is formed in an asymmetric elliptical shape, even if the distance from the outer peripheral surface 1342 of the roller 134 to the inner peripheral surface 1332 of the cylinder 133 is long, the

blades

1351, 1352, 1353 can be suppressed from escaping from the

blade grooves

1343a, 1343b, 1343c, and the degree of freedom in designing the inner peripheral surface 1332 of the cylinder 133 can be increased, and the degree of freedom in designing the roller 134 can also be increased.

Preferably, the

vane grooves

1343a, 1343b, 1343c are inclined in a direction opposite to the rotation direction of the roller 134, that is, the front faces 1351a, 1352a, 1353a of the

respective vanes

1351, 1352, 1353 contacting the inner peripheral surface 1332 of the cylinder 133 are inclined toward the rotation direction side of the roller 134, so that the compression start angle can be advanced toward the rotation direction side of the roller 134 to enable rapid start of compression.

A back pressure chamber 1344 is formed at the center of the roller 134, i.e., at the inner end of the vane groove 1343. The back pressure chamber 1344 extends laterally from the vane slot 1343. Thus, the back pressure chamber 1344 communicates with the blade groove 1343 to form a back pressure space for supporting the blade 135 slidably inserted into the blade groove 1343 toward the inner peripheral surface 1332 of the cylinder tube 133.

The back pressure chamber 1344 is formed by the number corresponding to the vane groove 1343. The back pressure chamber 1344 of the present embodiment is formed with three

back pressure chambers

1344a, 1344b and 1344c in the same manner as the

blade grooves

1343a, 1343b and 1343c, and these three

back pressure chambers

1344a, 1344b and 1344c are formed in one-to-one correspondence with the three

blade grooves

1343a, 1343b and 1343c, respectively.

The plurality of

back pressure chambers

1344a, 1344b, 1344c receive oil (or refrigerant) of a spit pressure or an intermediate pressure at a rear side of each of the

blades

1351, 1352, 1353, i.e., a rear face 1351c, 1352c, 1353c side of the

blade

1351, 1352, 1353, under which the pressure of the oil (or refrigerant) can press toward the inner circumferential surface of the cylinder 133. Hereinafter, the direction toward the inner circumferential surface of the cylinder is defined as the front side and the opposite side as the rear side with reference to the moving direction of the blade.

Although not shown, the plurality of

blade grooves

1343a, 1343b, 1343c may be formed radially with respect to the rotation center Or of the roller 134, that is, in a radial shape. The operation and effect are similar to those of the later-described embodiment in which the plurality of

vane grooves

1343a, 1343b, 1343c are formed to be inclined with respect to the rotation center Or of the roller 134, and therefore, the description thereof is replaced with the description of the later-described embodiment.

A plurality of

back pressure chambers

1344a, 1344b, 1344c may be formed to be sealed by the main bearing 131 and the sub bearing 132, respectively. In other words, the

back pressure chambers

1344a, 1344b, 1344c may be formed to communicate with the respective

back pressure grooves

1315, 1325 independently, or may also be formed to communicate with each other through the

back pressure grooves

1315, 1325. In the present embodiment, an example is shown in which a part of the back pressure chambers 1344 communicate with each other through a part of the

back pressure grooves

1315, 1325.

Specifically, as the plurality of

back pressure chambers

1344a, 1344b, 1344c axially penetrate, respectively, one axial end of each

back pressure chamber

1344a, 1344b, 1344c communicates with the primary

back pressure groove

1315a, 1315b, 1315c, and the other axial end of each

back pressure chamber

1344a, 1344b, 1344c communicates with the secondary

back pressure groove

1325a, 1325b, 1325c. Therefore, the oil passing through the two side back

pressure grooves

1315, 1325 flows into and fills the inside of each

back pressure chamber

1344a, 1344b, 1344 c. Therefore, it can be understood that, in theory, the internal pressure (back pressure) of the back pressure chamber 1344 is the same as the internal pressure of each

back pressure groove

1315, 1325. Hereinafter, the back pressure may be mixed as the pressure of the back pressure chamber 1344 and the pressures of the

vane grooves

1315, 1325.

Referring to fig. 1 to 3, the blade 135 of the present embodiment may be formed in plural numbers to be individually inserted into the

plural blade grooves

1343a, 1343b, 1343c, respectively. In other words, a plurality of

blades

1351, 1352, 1353 may be slidably inserted into each

blade slot

1343a, 1343b, 1343c. Thus, the plurality of

blades

1351, 1352, 1353 may be formed in almost the same shape as the

respective blade slots

1343a, 1343b, 1343c.

For example, a plurality of

blades

1351, 1352, 1353 may be defined as a first blade 1351, a second blade 1352, and a third blade 1353 along the direction of rotation of the roller 134. The first blade 1351 may be inserted into the first blade slot 1343a, the second blade 1352 may be inserted into the second blade slot 1343b, and the third blade 1353 may be inserted into the third blade slot 1343c.

The plurality of

blades

1351, 1352, 1353 may be formed in approximately the same shape. For example, the plurality of

blades

1351, 1352, and 1353 may be formed in a substantially rectangular parallelepiped shape, and the

front surfaces

1351a, 1352a, and 1353a of the

blades

1351, 1352, and 1353 contacting the inner peripheral surface 1332 of the cylinder 133 may be formed in a curved surface in the circumferential direction. Thereby, the

front surfaces

1351a, 1352a, 1353a of the

blades

1351, 1352, 1353 can make line contact with the inner peripheral surface 1332 of the cylinder 133, and friction loss can be reduced.

The vane rotary compressor provided with the mixing cylinder as described above operates as follows.

That is, when power is applied to the driving motor 120, the rotor 122 of the driving motor 120 and the rotation shaft 123 coupled to the rotor 122 rotate, and the roller 134 coupled to the rotation shaft 123 or integrally formed with the rotation shaft 123 rotates together with the rotation shaft 123.

Then, the plurality of

blades

1351, 1352, 1353 are drawn out from the

blade grooves

1343a, 1343b, 1343c by the centrifugal force generated by the rotation of the roller 134 and are brought into contact with the inner peripheral surface 1332 of the cylinder 133.

Then, the compression space V of the cylinder 133 is divided by the plurality of

vanes

1351, 1352, 1353 into compression chambers (including suction chambers or discharge chambers) V1, V2, V3 corresponding to the number of the plurality of

vanes

1351, 1352, 1353.

Then, the compression chambers V1, V2, and V3 move with the rotation of the roller 134, and the volumes of the compression chambers V1, V2, and V3 change due to the shape of the inner peripheral surface 1332 of the cylinder 133 and the eccentricity of the roller 134, and the refrigerant sucked into the compression chambers V1, V2, and V3 repeats a series of processes as follows: the refrigerant is compressed while moving along the rollers 134 and the

blades

1351, 1352, and 1353, and is discharged to the inner space of the casing 110 through the

discharge ports

1313a, 1313b, and 1313 c.

At this time, the refrigerant compressed in the compression chamber generates a gas reaction force to push the

vanes

1351, 1352, 1353 drawn out from the rollers 134 toward the inner sides of the vane grooves, but the gas reaction force is offset by a centrifugal force generated by the rotation of the rollers 134 and a back pressure of the

back pressure chambers

1344a, 1344b, 1344c supporting the

rear surfaces

1351a, 1351b, 1351c of the

vanes

1351, 1352, 1353. Then, the

blades

1351, 1352, 1353 keep the

front surfaces

1351a, 1352a, 1353a in contact with the inner peripheral surface 1332 of the cylinder 133, and can suppress leakage between the compression chambers V1, V2, V3.

However, as described above, in the vane rotary compressor of the present embodiment, the front faces 1351a, 1352a, 1353a of the

respective vanes

1351, 1352, 1353 receive both the compression pressure and the suction pressure in the section from the reference point P between the cylinder 133 and the roller 134 to the suction port 1331. Therefore, the flutter of the

blades

1351, 1352, 1353 generated by the pressure imbalance in the above-mentioned intervals of the

respective blades

1351, 1352, 1353 may be larger than in other intervals. Leakage between the compression chambers may occur due to such a flutter phenomenon of the

vanes

1351, 1352, 1353, impact noise and vibration between the cylinder 1333 and the

respective vanes

1351, 1352, 1353 may occur, and the inner peripheral surface 1332 of the cylinder 133 or the front faces 1351a, 1352a, 1353a of the

respective vanes

1351, 1352, 1353 may be worn, thereby exacerbating suction loss and compression loss.

Therefore, in the present embodiment, the pressure of the

back pressure grooves

1315, 1325 that press the blade 135 toward the inner peripheral surface 1332 of the cylinder 133 is formed in a large number of ways, whereby the blade 135 can be stably supported by the cylinder 133. In particular, by maintaining the

back pressure grooves

1315c, 1325c around the reference point P at the discharge pressure or at a pressure higher than the discharge pressure, the vane 135 passing around the reference point P is prevented from being pushed due to insufficient back pressure, and the chattering of the vane 135 can be effectively suppressed.

Fig. 4 is a perspective view showing the sub-bearing and the rotary shaft of fig. 2 in an exploded manner, fig. 5 is an assembled plan view of fig. 4, fig. 6 is a sectional view taken along the line "I-view" in fig. 5, fig. 7 is a sectional view taken along the line "x-view" in fig. 5, and fig. 8 is a perspective view showing another example of the communication groove of fig. 2.

Referring again to fig. 1 to 3, the main bearing 131 and the sub-bearing 132 in the present embodiment are formed with a main back pressure groove 1315 and a sub back pressure groove 1325, respectively, and the main back pressure groove 1315 and the sub back pressure groove 1325 may be constituted by a plurality of

back pressure grooves

1315a, 1315b, 1315c and a plurality of

back pressure grooves

1325a, 1325b, 1325c having pressures different from each other in a circumferential direction, respectively.

For example, the primary back pressure groove 1315 and the secondary back pressure groove 1325 may be respectively configured by three

back pressure grooves

1315a, 1315b, 1315c and three

back pressure grooves

1325a, 1325b, 1325c, and these three

back pressure grooves

1315a, 1315b, 1315c and three

back pressure grooves

1325a, 1325b, 1325c may respectively form a first intermediate pressure, a second intermediate pressure (or a first discharge pressure), and a super discharge pressure (or a second discharge pressure).

Although not shown, the main back pressure groove 1315 and the sub back pressure groove 1325 may be formed by more than three back pressure grooves. However, in this case, the back pressure grooves may be formed to have different pressures from each other in the rotation direction of the roller 134, for example, to have gradually higher pressures in the rotation direction of the roller 134 with reference to the reference point P.

As described above, since the main back pressure groove 1315 and the sub back pressure groove 1325 are formed to correspond to each other around the roller 134 except the back pressure passage 138 described later, the description will be given below with the sub back pressure groove 1325 as the center, and the description of the sub back pressure groove 1325 will be substituted for the description of the main back pressure groove 1315.

Referring to fig. 4 and 5, the secondary back pressure groove 1325 may include: a first sub back pressure groove 1325a, a second sub back pressure groove 1325b, and a third sub back pressure groove 1325c. The first, second, and third sub back

pressure grooves

1325a, 1325b, and 1325c may be sequentially arranged at a predetermined interval from the reference point P in the rotation direction of the roller 134.

For example, the first sub back pressure groove 1325a may be located in a region constituting the suction pressure to the intermediate pressure in the compression space V, the second sub back pressure groove 1325b may be located in a region constituting the intermediate pressure to the discharge pressure, and the third sub back pressure groove 1325c may be located in a region constituting the discharge pressure or the super discharge pressure. Thereby, the first sub back pressure pocket 1325a forms a first intermediate pressure, the second sub back pressure pocket 1325b forms a second intermediate pressure (or a first discharge pressure) higher than the first intermediate pressure, and the third sub back pressure pocket 1325c forms a super discharge pressure (or a second discharge pressure) higher than the second intermediate pressure.

The first sub back pressure groove 1325a may be formed as a nearly closed space in structure. For example, the inner peripheral side of the first sub back pressure recess 1325a is blocked by the first sub bearing convex portion 1326a so as to be almost separated from the inner space 110a of the housing 110. Thereby, the pressure of the oil flowing into the first sub back pressure groove 1325a beyond the first sub bearing convex portion 1326a is reduced to the first intermediate pressure.

Further, as the outer peripheral side of the first sub back pressure pocket 1325a is disposed in a relatively low suction pressure and first intermediate pressure region, oil of the first sub back pressure pocket 1325a may leak to the compression space V through a gap between the sub bearing 132 and the roller 134. Thus, the first sub back pressure groove 1325a has the largest groove volume, and the groove pressure (back pressure) forms the lowest first intermediate pressure. Hereinafter, the formation of the back pressure groove as a closed space does not mean a completely sealed closed space, and for convenience of description, a case where a passage communicating with the back pressure groove is not specifically provided is defined as a closed space and will be described. Therefore, for convenience of explanation, a case where a communication flow path communicating with the back pressure groove is not specifically provided as the second sub back pressure groove 1325b described later is defined as an open space and explained.

The second sub back pressure groove 1325b may be formed as an open space. For example, the second sub-bearing convex portion 1326b is low in height or provided with a communication flow path (not indicated) so that the inner peripheral side of the second sub-back pressure recess 1325b is opened with respect to the inner space 110a of the housing 110 through the oil supply passage 125 of the rotary shaft 123. Thereby, the second sub back pressure groove 1325b is formed as an open space, and a second intermediate pressure (or a first discharge pressure) higher than the first intermediate pressure is formed.

The third sub back pressure groove 1325c may be formed as a semi-closed space. For example, the inner peripheral side of the third sub back pressure recess 1325c is closed by the third sub bearing convex portion 1326c, and can be closed with respect to the inner space 110a of the housing 110. However, as described above, the third sub back pressure recess 1325c directly communicates with the oil supply passage 125 of the rotary shaft 123 through the back pressure passage portion 138 described later, and is not structurally formed as a completely closed space with respect to the internal space 110a of the housing 110.

However, the third sub back pressure recess 1325c is formed in the discharge pressure region, and even if the inner peripheral side thereof is closed by the third sub bearing convex portion 1326c, since the inner diameter of the back pressure passage portion 138 is small, it can be understood that a substantially closed space is formed. Thus, the third sub back pressure groove 1325c may be formed as a semi-closed space, and a super discharge pressure (second discharge pressure) higher than the second intermediate pressure (or the first discharge pressure) will be formed.

Referring to fig. 4 to 7, the volume of the third sub back pressure groove 1325c of the present embodiment may be smaller than not only the volume of the first sub back pressure groove 1325a but also the volume of the second sub back pressure groove 1325b. Thereby, it is facilitated that the internal pressure of the third sub back pressure groove 1325c is formed to a higher pressure than the internal pressure of the second sub back pressure groove 1325b.

The arc length L1 of the first sub back pressure groove 1325a may be formed to be the longest, and the arc length L3 of the third sub back pressure groove 1325c may be formed to be the shortest. In other words, the arc length L3 of the third sub back pressure groove 1325c may be smaller than the arc length L1 of the first sub back pressure groove 1325a and smaller than or equal to the arc length L2 of the second sub back pressure groove 1325b. This can prevent the vane 135 from receiving a back pressure exceeding the discharge pressure for an excessively long period. This can suppress the chattering phenomenon between the blade 135 and the cylinder 133 occurring in the vicinity of the reference point P, and can effectively suppress an increase in the friction loss in this section.

For example, when the reference point P is set to 0 °, the first sub back pressure groove 1325a may be formed to have an interval around about 0 ° to about 150 °, the second sub back pressure groove 1325b may be formed to have an interval around about 160 ° to about 260 °, and the third sub back pressure groove 1325c may be formed to have an interval around about 270 ° to about 350 °. Then, as shown in the present embodiment, in the case where the vane 135 Or the vane groove 1343 is inclined at a preset angle with respect to the radial direction passing through the rotation center Or of the roller 134, the back pressure chamber 1344 to which the corresponding vane 135 belongs will communicate with the third sub back pressure groove 1325c during the period when the corresponding vane 135 passes through the reference point P. Then, the

rear surfaces

1351b, 1352b, 1353b of the corresponding vanes 135 receive the pressure of the third sub back pressure groove 1325c, that is, the back pressure corresponding to the super discharge pressure, and the

front surfaces

1351a, 1352a, 1353a of the corresponding vanes 135 are brought into close contact with the inner peripheral surface 1332 of the cylinder 133 against the high discharge pressure in the vicinity of the reference point P.

Referring to fig. 6 and 7, a radial width (hereinafter, mixed with a width) (not labeled) of the third sub back pressure groove 1325c may be smaller than a radial width (not labeled) of the other sub back

pressure grooves

1325a, 1325b, and an axial depth (hereinafter, mixed with a depth) H3 of the third sub back pressure groove 1325c may be smaller than axial depths H1, H2 of the other sub back

pressure grooves

1325a, 1325b. In addition, the length L3 of the third sub back pressure grooves 1325c and/or the width (not shown) and/or the depth H3 of the third sub back pressure grooves 1325c may be formed to be smallest compared to the lengths L1, L2, the width (not shown), and the depths H1, D2 of the other

back pressure grooves

1325a, 1325b. In the present embodiment, an example is shown in which the length L3, the width (not shown), and the depth H3 of the third sub back pressure groove 1325c are formed to be the smallest compared to the lengths L1, L2, the width (not shown), and the depths H1, D2 of the other sub back

pressure grooves

1325a, 1325b.

Thus, the volume of the third sub back pressure groove 1325c may be smaller than not only the volume of the first sub back pressure groove 1325a but also the volume of the second sub back pressure groove 1325b. Therefore, as described above, it is possible to facilitate not only the pressure of the third sub back pressure groove 1325c to be maintained at a higher pressure than the internal pressure of the first sub back pressure groove 1325a, but also the pressure of the second sub back pressure groove 1325b.

Although not shown, the length L3, the width (not shown), and the depth H3 of the third sub back pressure groove 1325c may not necessarily be the smallest compared to the lengths L1, L2, the width (not shown), and the depths H1, D2 of the other sub back

pressure grooves

1325a, 1325b. For example, the length L3, the width (not labeled), and the depth H3 of the third sub back pressure groove 1325c may also be formed to be at least the same as or slightly larger than the length L2, the width (not labeled), and the depth H2 of the adjacent second sub back pressure groove 1325b.

In this case, the second sub back pressure recess 1325b may be formed so that an inner peripheral side thereof is opened or a communication passage (not shown) is provided to form a so-called open space. On the other hand, the third sub back pressure recess 1325c communicates with the internal space 110a of the housing 110 through the back pressure passage portion 138 described above to form a semi-closed space, but as shown in fig. 5, as the back pressure passage portion 138 has a small inner diameter and is closed by the vane 135 when the vane 135 reciprocates, a substantially closed space is formed, and the third sub back pressure recess 1325c can form a higher pressure than the second sub back pressure recess 1325b.

Referring to fig. 4 to 7, as described above, the third sub back pressure recess 1325c of the present embodiment communicates with the internal space 110a of the housing 110, more precisely, the oil supply passage 125 as the internal passage of the rotary shaft 123, through the back pressure passage portion 138. Thus, a part of the oil sucked to the upper side through the oil supply passage 125 of the rotary shaft 123 directly flows into the third sub back pressure recess 1325c through the back pressure passage portion 138.

The back pressure passage portion 138 includes: a first back pressure hole 138a, a second back pressure hole 138b, and a communication groove 138c. A first back pressure hole 138a is formed through the rotary shaft 123, and a second back pressure hole 138b is formed through the sub-bearing 132. The first back pressure hole 138a and the second back pressure hole 138b may be periodically communicated, or may be continuously communicated through the communication groove 138c. In the present embodiment, an example in which the first back pressure hole 138a and the second back pressure hole 138b periodically communicate will be described first, and an example in which they continuously communicate will be described later.

Referring to fig. 4 and 5, the first back pressure hole 138a of the present embodiment may be understood as a third oil supply hole, which penetrates from the inner circumferential surface of the oil supply passage 125 constituting the inner circumferential surface of the rotary shaft 123 to the outer circumferential surface of the rotary shaft 123. In other words, as described above, in the rotary shaft 123, the first oil supply hole 126a, the second oil supply hole 126b, and the first back pressure hole 138a are formed at predetermined intervals from each other in the axial direction. The first oil supply hole 126a radially penetrates the main bearing hole 1312a, and the second oil supply hole 126b and the first back pressure hole 138a radially penetrate the sub bearing hole 1322 a. The first back pressure hole 138a may be formed to communicate with the second back pressure hole 138b at a position lower than the second oil supply hole 126b.

The first back pressure hole 138a may be formed in only one circumferential direction, or may be formed in plural. In the present embodiment, an example in which only one first back pressure hole 138a is formed is shown. However, the same applies to the case where a plurality of first back pressure holes 138a are formed.

The first back pressure hole 138a may be less than or equal to the first oil supply hole 126a and/or the second oil supply hole 126b. For example, the inner diameter D31 of the first back pressure hole 138a may be smaller than the inner diameter D1 of the first oil supply hole 126a and/or the inner diameter D2 of the second oil supply hole 126b in a range where the oil passing through the back pressure passage portion 138 is not depressurized. This can prevent oil from flowing out excessively through the first back pressure hole 138a before the oil sucked upward through the oil supply passage 125 reaches the first oil supply hole 126a or the second oil supply hole 126b, thereby preventing oil from flowing out of the other back pressure grooves.

As the inner diameter D31 of the first back pressure hole 138a is smaller than the inner diameter D1 of the first oil supply hole 126a and/or the inner diameter D2 of the second oil supply hole 126b as in the present embodiment, the inner diameter D1 of the first oil supply hole 126a or the inner diameter D2 of the second oil supply hole 126b will be larger than the inner diameter D3 of the back pressure passage portion 138. Thus, the oil sucked to the upper side through the oil supply passage 125 may be sufficiently supplied to the first and second main back pressure grooves 1315a and 13125b and the first and second sub back

pressure grooves

1325a and 1325b through the first and second

oil supply holes

126a and 126b. This can prevent a back pressure shortage due to oil shortage in the first main back pressure groove 1315a, the second main back pressure groove 1315b, the first sub back pressure groove 1325a, or the second sub back pressure groove 1325b. At the same time, friction loss due to oil shortage in the main bearing surface 1312b and/or the sub bearing surface 1322b can be prevented in advance.

In addition, the first back pressure hole 138a may be formed on the same circumference as the second oil supply hole 126b, but is preferably formed at a different height from the second oil supply hole 126b as much as possible. For example, the first back pressure hole 138a may be located at a lower position than the second oil supply hole 126b, i.e., at the lower end side of the rotating shaft 123. Thus, the first back pressure hole 138a will be closer to the oil storage space 110b of the housing 110 than the second oil supply hole 126b.

Then, the oil drawn upward through the oil supply passage 125 flows into the first back pressure hole 138a before flowing into the second oil supply hole 126b, and thus can be supplied to the third main back pressure groove 1315c and the third sub back pressure groove 1325c earlier than the other

back pressure grooves

1315a, 1325a, 1315b, and 1325b. This can prevent the vane 135 from being spaced from the cylinder 133 near the reference point P at the initial start, thereby preventing an initial start failure. Therefore, the situation that the cooling and heating effects are delayed when the compressor is applied to the cooling and heating equipment can be prevented.

Meanwhile, when the first back pressure hole 138a and the second oil supply hole 126b are formed on the same circumference, there is a possibility that the rigidity of the rotating shaft 123 is lowered, but as the first back pressure hole 138a and the second oil supply hole 126b are spaced in the axial direction, the rigidity of the rotating shaft 123 can be suppressed from being lowered and the reliability can be improved.

Referring to fig. 4 to 7, the second back pressure hole 138b of the present embodiment may be formed to penetrate between the third sub back pressure groove 1325c and the inner circumferential surface of the sub bearing 132. For example, one end of the second back pressure hole 138b opens to the bottom surface of the third sub back pressure recess 1325c, and the other end of the second back pressure hole 138b opens to a sub bearing surface 1322b constituting the inner peripheral surface of the sub bearing hole 1322 a. Thus, the third sub back pressure groove 1325c may communicate with the first back pressure hole 138a through the second back pressure hole 138b.

The second back pressure hole 138b may be less than or equal to the first back pressure hole 138a. For example, the inner diameter D32 of the second back pressure hole 138b may be formed the same as the inner diameter D31 of the first back pressure hole 138a. In other words, the inner diameter D32 of the second back pressure hole 138b may be smaller than the inner diameter D1 of the first oil supply hole 126a and/or the inner diameter D2 of the second oil supply hole 126b. Accordingly, the oil flowing into the third sub back pressure pocket 1325c is suppressed from easily flowing out through the second back pressure hole 138b and the first oil supply hole 138a when the vane 135 retreats, and thus the back pressure of the third sub back pressure pocket 1325c can be sufficiently maintained.

Although not shown, the inner diameter D32 of the second back pressure hole 138b may be larger than the inner diameter D31 of the first back pressure hole 138a. In other words, the inner diameter D31 of the first back pressure hole 138a may be greater than the inner diameter D32 of the second back pressure hole 138b and smaller than the inner diameters D1, D2 of the first and second

oil supply holes

126a, 126b.

In this case, a part of the oil sucked through the oil supply passage 125 flows out from between the inner circumferential surface of the sub bearing 132 and the outer circumferential surface of the rotary shaft 123 through the first back pressure hole 138a, and the part of the oil is guided to the third sub back pressure recess 1325c through the second back pressure hole 138b again, while the remaining oil lubricates between the inner circumferential surface of the sub bearing 132 and the outer circumferential surface of the rotary shaft 123. Thereby, the oil can be sufficiently supplied to the third sub back pressure groove 1325c, and also the sub bearing surface 1322b between the inner circumferential surface of the sub bearing 132 and the outer circumferential surface of the rotary shaft 123 can be effectively lubricated.

The second back pressure hole 138b may be formed through the center of the third sub back pressure recess 1325c, or may be formed through an eccentric position of the third sub back pressure recess 1325c. In the present embodiment, an example is shown in which the second back pressure hole 138b is formed so as to penetrate the sub bearing surface 1322b at a position offset to one side from the center of the third sub back pressure recess 1325c, more precisely, at a position offset to the reference point P side.

In other words, the second oil supply hole may be formed at a position intermittently overlapping the vane 135 when the vane 135 reciprocates, and the inner diameter D32 of the second oil supply hole 138b may be smaller than the width t of the vane 135. As a result, as shown in fig. 3 and 5, the vane 135 passing through the third sub back pressure groove 1325c can block the second back pressure hole 138b at a position receiving a relatively high gas reaction force from the compression space V, in other words, at a position close to the third discharge port 1313 c. Thus, the third sub back pressure groove 1325c may form a closed space when the vane 135 is most adjacent to the third discharge port 1313c, and form a high back pressure. If the second back pressure hole 138b is formed in the center of the third sub back pressure groove 1325c or on the opposite side of the present embodiment, the second back pressure hole 138b is opened when the vane 135 is closest to the third ejection port 1313c, so that the third sub back pressure groove 1325c will not form a closed space. Then, when the vane 135 approaches the third discharge port 1313c, the back pressure of the third sub back pressure groove 1325c becomes low, and the vane 135 may not be supported effectively.

In addition, the second back pressure hole 138b may be formed obliquely in a diagonal manner. Thus, the oil passing through the first back pressure hole 138a may smoothly enter the third sub back pressure groove 1325c without being blocked.

Although not shown, the second back pressure hole 138b may be formed by bending. For example, in the second back pressure hole 138b, a first through hole portion (not shown) may extend in the axial direction from the third sub back pressure groove 1325c, and a second through hole portion (not shown) may penetrate from the outer circumferential surface of the sub bearing 132 to the inner circumferential surface of the sub bearing hole 1322a through the first through hole portion. In this case, the back pressure passage portion 138 functions as an oil storage space, and a predetermined amount of oil can be stored in the back pressure passage portion 138 when the compressor is stopped, and can be rapidly supplied to the third sub back pressure groove 1325c or rapidly lubricate the sub bearing surface 1322b at the time of restart.

The communication groove 138c of the present embodiment is formed between the first back pressure hole 138a and the second back pressure hole 138b. Thereby, the first back pressure hole 138a and the second back pressure hole 138b can communicate with each other through the communication groove 138c.

The communication groove 138c may be formed at least one side of an outer end of the first back pressure hole 138a and an inner end of the second back pressure hole 138b facing the outer end of the first back pressure hole 138a. In other words, the communication groove 1413 may be formed on at least one side of the outer circumferential surface of the rotation shaft 123 and the sub bearing surface 1322b facing thereto and constituting the inner circumferential surface of the sub bearing 132. In the present embodiment, an example is shown in which the communication groove 138c is formed in the sub bearing surface 1322b, which is the inner end of the second back pressure hole 138b. However, the communication groove 138c may be formed on the outer peripheral surface of the rotary shaft 123, or may be formed on the outer peripheral surface of the rotary shaft 123 and the sub-bearing surface 1322b, respectively.

However, as described above, in the case where the communication groove 138c is formed in the sub bearing 132, the communication groove 138c may be formed by being recessed by a predetermined depth in the sub bearing surface 1322b. However, a bearing (not shown) made of a bush bearing may be inserted into the sub bearing surface 1322b. In this case, the communication groove 138c may be formed directly in the sub bearing surface 1322b, but may be formed so as to penetrate a bearing (not shown) inserted into the sub bearing surface 1322b. For convenience of description, a case where the communication groove 138c is formed in the sub-bearing surface 1322b will be described below as an example. The second communicating groove 1382c, which will be described later as another embodiment, is also described by taking a case where it is formed in the main bearing surface 1312b as an example.

As shown in fig. 4, the communication groove 138c may be formed in a circular arc shape that is long in the circumferential direction. In this case, the communication groove 138c may be formed to have the same width and depth in the circumferential direction, or may be formed to be deep at the center thereof and shallow at both ends thereof. In other words, in the case where the communication groove 138c is concavely formed in the sub-bearing surface 1322b, as described above, the width or depth of the communication groove 138c may be formed such that the center thereof is large and both ends thereof are small. However, when the communication groove 138c is formed to penetrate a bearing (not shown) inserted into the sub-bearing surface 1322b, it is understood that the communication groove 138c is formed to have the same width and depth in the circumferential direction.

However, in the present embodiment, the communication groove 138c is formed in the sub-bearing surface 1322b as an example, and therefore, it is understood that the communication groove 138c is formed such that the width and depth of the center thereof are larger than those of the both ends thereof. In this case, not only the communication groove 138c can be easily processed in a circular arc shape, but also the oil can be smoothly guided to the second back pressure hole 138b.

In the case where the communication groove 138c is formed in a circular arc shape, the communication groove 138c may be formed to have a circular arc length larger than the inner diameter D31 of the first back pressure hole 138a and to periodically communicate with the first back pressure hole 138a. For example, the circular arc length of the communication groove 138c may be formed such that the total circumferential angle added in connection with the first back pressure hole 138a is at least less than 360 °, that is, less than 180 °. Thus, the communication groove 138c may periodically communicate with the first back pressure hole 138a without continuously communicating. Thus, in the section (rotation angle) where the communication groove 138c and the first back pressure hole 138a do not communicate during the compressor operation, the back pressure passage portion 138 is periodically closed. Then, the third sub back pressure groove 1325c is formed as a closed space so that oil outflow in the third sub back pressure groove 1325c is minimized, so that a high back pressure can be maintained, whereby the vane can be supported more stably.

However, the communication groove 138c may be formed in a circular shape. The communication grooves 138c may be formed to have the same depth in the circumferential direction. Thus, when the rotary shaft 123 rotates, the first back pressure hole 138a and the second back pressure hole 138b can be continuously communicated through the communication groove 138c.

However, when the communication groove 138c is circular, the outer peripheral surface of the rotary shaft 123 is formed more easily than the inner peripheral surface of the sub-bearing 132. In other words, as a bearing (not shown) made of a bush bearing is inserted into the sub-bearing surface 1322b, it is difficult to form a circular communication groove in the sub-bearing surface 1322b, which is the inner peripheral surface of the sub-bearing 132. Therefore, as shown in fig. 8, the communication groove 138c may be formed in a circular shape extending in the circumferential direction along the outer circumferential surface of the rotary shaft 123.

As described above, if the communication groove 138c is formed in a circular shape to continuously communicate with the first back pressure hole 138a, the oil passing through the first back pressure hole 138a may be continuously supplied to the second back pressure hole 138b through the communication groove 138c, and the oil may be continuously supplied to the third sub back pressure groove 1325c without interruption. This can prevent the third sub back pressure groove 1325c, more precisely, the back pressure chamber 1344 from being weakened due to the lack of oil.

On the other hand, as described above, in addition to the first and second main

back pressure grooves

1315a and 1315b, a third main back pressure groove 1315c may be provided at the main bearing 131. These first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c may be formed symmetrically with the first, second, and third sub back

pressure grooves

1325a, 1325b, and 1325c. However, unlike the third sub back pressure groove 1325c, the third main back pressure groove 1315c may be formed without additionally providing the back pressure passage portion 138 directly communicating with the oil supply passage 125, and the oil flowing in from the third sub back pressure groove 1325c will move to the third main back pressure groove 1315c through the back pressure chamber 1344.

The first, second, and third primary

back pressure grooves

1315a, 1315b, and 1315c may communicate with the first, second, and third secondary

back pressure grooves

1325a, 1325b, and 1325c, respectively, with the corresponding back pressure chamber 1344 passing therethrough. Thus, the back pressure of the back pressure chamber 1344, in which the vane 135 is formed to have the same pressure as the

back pressure groove

1315, 1325, is pressed against the cylinder 133, and the

front surfaces

1351a, 1352a, 1353a of the vane 135 are brought into sliding contact with the inner peripheral surface 1332 of the cylinder 133.

As described above, in the vane rotary compressor of the present embodiment, the back pressure passage portion has the following operational effects. Fig. 9 is a sectional view illustrating a process of supplying oil to the back pressure groove in the rotary compressor of the present embodiment.

Referring to fig. 9, in the main bearing 131 and/or the sub-bearing 132 of the vane rotary compressor of the present embodiment, a plurality of

back pressure grooves

1315, 1325 having back pressure different from each other may be formed respectively in the rotation direction of the rollers 134, and a third main back pressure groove 1315c and a third sub back pressure groove 1325c, which are most adjacent to the third discharge port 1313c, may form a higher pressure than the other

back pressure grooves

1315, 1325.

In other words, as the third sub back pressure recess 1325c is directly connected to the oil supply passage 125 of the rotary shaft 123 by the back pressure passage portion 138, a part of the oil sucked to the upper side along the oil supply passage 125 directly flows into the third sub back pressure recess 1325c by the back pressure passage portion 138. As a result, the oil in the third sub back pressure pocket 1325c and the third main back pressure pocket 1315c communicating therewith increases the pressure due to the centrifugal force and the pressure in the closed space, and forms the super discharge pressure (second discharge pressure) higher than the discharge pressure (first discharge pressure).

Then, the

rear surfaces

1351b, 1352b, 1353b of the vane 135 passing through the reference point P receive a high back pressure, which is an excessive discharge pressure (second discharge pressure), transmitted from the corresponding back pressure chamber 1344 through the third main back pressure groove 1315c and/or the third sub back pressure groove 1325c.

Then, the vane 135 passing through the reference point P receives a high back pressure by the third main back pressure groove and the third sub back pressure groove and is pressed against the inner peripheral surface 1332 of the cylinder 133, and the

front surfaces

1351a, 1352a, 1353a of the vanes 135 passing through the vicinity of the reference point P are brought into close contact with the inner peripheral surface 1332 of the cylinder 133, whereby the chattering of the vane 135 can be suppressed. This can suppress wear of the inner peripheral surface 1332 of the cylinder 133 or the

front surfaces

1351a, 1352a, 1353a of the vane 135 around the reference point P, reduce vibration noise around the reference point P, and suppress leakage between compression chambers to improve compression efficiency.

Although the fluttering phenomenon of the vane 135 may be more serious at the initial start of the compressor, the vane near the reference point can be brought into close contact with the cylinder tube even at the initial start of the compressor as the oil is rapidly supplied to the third sub back pressure pocket 1325c around the reference point P through the back pressure passage portion 138 communicating with the lower end portion of the oil supply passage 125. Accordingly, the compressor efficiency can be improved by suppressing the initial start failure, and when the compressor is applied to a cooling and heating apparatus, the cooling and heating effect is rapidly exhibited, and the reliability can be improved.

This can also be confirmed by the graph shown in fig. 10. Fig. 10 is a graph comparing blade contact force at different rotation angles of the vane rotary compressor of the present embodiment with that of the prior art and shown.

As shown in fig. 10, when the rotation angle of the rotation shaft 123 reaches about 240 °, the blade contact force N exceeds zero (zero) which is a reference value, and the

front surfaces

1351a, 1352a, 1353a of the blade 135 can be maintained in close contact with the inner peripheral surface 1332 of the cylinder 133. However, the blade contact force N may be sharply decreased after the rotation angle of the rotation shaft 123 exceeds about 240 °. This is because the pressure in the compression chamber V3 near the reference point P is greatly increased as described above.

In the conventional technique (indicated by a chain line), the main back pressure groove 1315 and the sub back pressure groove 1325 also form the discharge pressure (first discharge pressure) or the second intermediate pressure lower than the discharge pressure at the position closest to the reference point (to be precise, the third discharge port) P, and the blade contact force N becomes lower than the reference value 0. Therefore, in the related art, the front faces 1351a, 1352a, 1353a of the vane 135 are spaced from the inner peripheral surface 1332 of the cylinder 133 in the vicinity of the reference point P, so that a fluttering phenomenon of the vane 135 and leakage between compression chambers may occur.

However, in the present embodiment (indicated by the solid line), as described above, as the primary back pressure groove 1315 and the secondary back pressure groove 1325 constituting the over discharge pressure (the second discharge pressure) are formed at the positions closest to the third discharge port 1313c, the blade contact force N is maintained at a value greater than the reference value 0 even if the rotation angle of the rotation shaft 123 exceeds about 240 °. Thus, in the present embodiment, the

front surfaces

1351a, 1352a, 1353a of the vane 135 are also held in contact with the inner peripheral surface 1332 of the cylinder 133 in the vicinity of the reference point P, and the fluttering phenomenon of the vane 135 and leakage between the compression chambers can be suppressed.

In the rotary compressor of the present embodiment, the above-described effects can be expected even more when a high-pressure refrigerant such as R32, R410a, or CO2 is used.

On the other hand, other embodiments of the back pressure passage portion will be described below.

That is, in the above-described embodiment, the back pressure passage portion is formed continuously through the sub-bearing and the rotary shaft, but may be formed only through the sub-bearing in some cases.

Fig. 11 is a perspective view showing another embodiment of the back pressure passage portion of fig. 2, and fig. 12 is an assembled sectional view of fig. 11.

Referring to fig. 11 and 12, the basic structure of the vane rotary compressor of the present embodiment and the operational effects thereof are almost the same as those of the previous embodiments, and thus, the detailed description thereof is replaced with the description of the previous embodiments. For example, in the vane rotary compressor of the present embodiment, the basic structures of the main bearing 131, the sub-bearing 132, the cylinder 133, the roller 134, and the vane 135 constituting the compression portion are almost the same as those of the previous embodiments.

The first sub back pressure groove 1325a, the second sub back pressure groove 1325b, and the third sub back pressure groove 1325c are arranged in order in the rotation direction of the roller 134 from the reference point P as a start point on the sub sliding surface 1321a of the sub bearing 132. The first sub back pressure groove 1325a is formed to extend from the suction pressure region to the intermediate pressure region, the second sub back pressure groove 1325b is formed to extend from the intermediate pressure region to the discharge pressure region, and the third sub back pressure groove 1325c is formed in the discharge pressure region, connected to the back pressure passage portion 13, and directly communicates with the internal space 110a of the housing 110 that constitutes the discharge pressure. Thereby, the first sub back pressure pocket 1325a forms a first intermediate pressure, the second sub back pressure pocket 1325b forms a second intermediate pressure (or a first discharge pressure) higher than the first intermediate pressure, and the third sub back pressure pocket 1325c forms a super discharge pressure (or a second discharge pressure) higher than the second intermediate pressure.

However, the back pressure passage portion 138 of the present embodiment may be formed through the sub-bearing 132 such that the third sub-back pressure groove 1325c is directly connected to the inner space 110a of the housing 110. For example, the back pressure passage portion 138 may be formed by a single through-hole, an upper end of the back pressure passage portion 138 penetrates through a bottom surface of the third sub back pressure recess 1325c to communicate with the third sub back pressure recess 1325c, and a lower end of the back pressure passage portion 138 penetrates through a lower end of the sub bearing 132, that is, a bottom surface of the sub plate portion 1321 constituting an opposite surface of the sub sliding surface 1321a, and is immersed in the oil storage space 110b of the housing 110.

The back pressure passage portion 138 may be formed eccentrically from the center of the third sub back pressure recess 1325c to the side close to the reference point P. The operation and effect are the same as those in the foregoing embodiment.

As described in the foregoing embodiments, the inner diameter D33 of the back pressure passage portion 138 may be smaller than the inner diameters D1 and D2 of the first and second

oil supply holes

126a and 126b. The effect is similar to that of the previous embodiment. However, in the foregoing embodiment, as the back pressure passage portion 138 communicates with the oil supply passage 125 of the rotary shaft 123, the oil is pumped by the centrifugal force generated when the rotary shaft 123 rotates, but in the present embodiment, the oil is supplied by the pressure of the inner space 110a of the housing 110. Therefore, in terms of oil supply, it may be more advantageous for the inner diameter D33 of the back pressure passage portion 138 to be formed slightly larger than the inner diameters D31, D32 of the back pressure passage portion 138 in the foregoing embodiment of fig. 4.

However, in this case, if the inner diameter D33 of the back pressure passage portion 138 is too large, for example, is formed to be larger than or equal to the inner diameter D1 of the first oil supply hole 126a and the inner diameter D2 of the second oil supply hole 126b, the oil in the third sub back pressure recess 1325c flows out to the back pressure passage portion 138 when the vane retreats, and it is not favorable to form a sufficient second discharge pressure. Thus, in the present embodiment, the inner diameter D33 of the back pressure passage portion 138 is preferably smaller than the inner diameter D1 of the first oil supply hole 126a and/or the inner diameter D2 of the second oil supply hole 126b.

As described above, when the back pressure passage portion 138 is formed to penetrate the sub-bearing 132, the back pressure passage portion 138 can be easily processed, and manufacturing costs can be saved. In addition, in this case, not only the length of the back pressure passage portion 138 can be shortened, but also the back pressure passage portion 138 can be maintained in an open state, so that oil can be quickly supplied to the third sub back pressure recess 1325c at the initial start. This can more effectively suppress the initial startup failure.

On the other hand, another embodiment of the back pressure passage portion will be described below.

That is, in the above-described embodiment, the back pressure passage portion is formed only in the sub-bearing, but the back pressure passage portion may be formed in each of the sub-bearing and the main bearing in some cases.

Fig. 13 is a perspective view showing a disassembled back pressure passage portion according to still another embodiment, and fig. 14 is an assembled sectional view of fig. 13.

Referring to fig. 13 and 14, the basic structure of the vane rotary compressor of the present embodiment and the operational effects thereof are almost the same as those of the previous embodiments, and thus, the detailed description thereof is replaced with the description of the previous embodiments. For example, in the vane rotary compressor of the present embodiment, the basic structures of the main bearing 131, the sub-bearing 132, the cylinder 133, the roller 134, and the vane 135 constituting the compression portion are almost the same as those of the previous embodiments.

The first sub back pressure groove 1325a, the second sub back pressure groove 1325b, and the third sub back pressure groove 1325c are arranged in order in the rotation direction of the rollers 134 from the reference point P as a starting point on the sub sliding surface 1321a of the sub bearing 132, and the first main back pressure groove 1315a, the second main back pressure groove 1315b, and the third main back pressure groove 1315c are arranged in order in the rotation direction of the rollers 134 from the reference point P as a starting point on the main sliding surface 1312a of the main bearing 131.

However, in the present embodiment, the third sub back pressure recess 1325c and the oil supply passage 125 of the rotary shaft 123 may communicate with each other through the first back pressure passage portion 1381, and the third main back pressure recess 1315c and the oil supply passage 125 of the rotary shaft 123 may communicate with each other through the second back pressure passage portion 1382. Thus, a part of the oil sucked to the upper side through the oil supply passage 125 may be supplied to the third sub back pressure groove 1325c through the first back pressure passage part 1381, and may be supplied to the third main back pressure groove 1315c through the second back pressure passage part 1382. Accordingly, the back pressure of the third sub back pressure groove 1325c and the third main back pressure groove 1315c is increased to the excess discharge pressure (or the second discharge pressure), and thereby the rear surface of the vane 135 passing through the reference point P can be supported more effectively.

Specifically, the first back pressure passage portion 1381 may include: a first back pressure hole 1381a, a second back pressure hole 1381b and a first communicating groove 1381c. The first back pressure hole 1381a is identical to the first back pressure hole 138a of the aforementioned embodiment of fig. 4, the second back pressure hole 1381b is identical to the second back pressure hole 138b of the aforementioned embodiment of fig. 4, and the first communicating groove 1381c is identical to the communicating groove 138c of the aforementioned embodiment of fig. 4. Therefore, the specific configurations and the operational effects of the first back pressure hole 1381a, the second back pressure hole 1381b and the first connecting groove 1381c are replaced with those of the first back pressure hole 138a, the second back pressure hole 138b and the connecting groove 1381c of the embodiment of fig. 4 described above.

The second back pressure passage 1382 of the present embodiment may include: a third back pressure hole 1382a, a fourth back pressure through hole 1382b and a second communicating groove 1382c.

The third back pressure hole 1382a may penetrate from the inner peripheral surface of the rotating shaft 123 constituting the inner peripheral surface of the oil supply passage 125 to the outer peripheral surface of the rotating shaft 123, similarly to the first back pressure hole 1381a, the fourth back pressure through hole 1382b may penetrate between the main bearing hole 1312a and the third main back pressure groove 1315c of the main bearing 131, similarly to the second back pressure hole 1381b, and the second communication groove 1382c may be formed by recessing in a circular arc shape or a circular shape on the inner peripheral surface of the main bearing hole 1312a and/or the outer peripheral surface of the rotating shaft 123, similarly to the first communication groove 1381c.

The third back pressure hole 1382a is almost the same as the first back pressure hole 1381a, the fourth back pressure hole 1382b is almost the same as the second back pressure hole 1381b, and the second communicating groove 1382c is almost the same as the first communicating groove 1381c. Therefore, the descriptions of the third back pressure hole 1382a, the fourth back pressure through hole 1382b, and the second communication groove 1382c of the second back pressure passage portion 1382 are replaced with the descriptions of the first back pressure hole 1381a, the second back pressure hole 1381b, and the first communication groove 1381c of the embodiment of fig. 4 described above.

As described above, in the case where the first and second back

pressure passage parts

1381 and 1382 are provided, respectively, oil is directly supplied from the oil supply passage 125 of the rotation shaft 123 to the third sub back pressure recess 1325c and the third main back pressure recess 1315c through the first and second back

pressure passage parts

1381 and 1382, respectively. Thereby, the pressures of the third sub back pressure groove 1325c and the third main back pressure groove 1315c are maintained almost uniformly, so that the back pressure of the corresponding back pressure chamber 1344 between the third sub back pressure groove 1325c and the third main back pressure groove 1315c can be distributed uniformly in the axial direction. Thereby, the back pressure applied to the corresponding vane 135 passing between the third sub back pressure groove 1325c and the third main back pressure groove 1315c may be uniformly distributed in the axial direction, so that the chattering phenomenon and/or the eccentric wear between the vane 135 and the cylinder 133 may be more effectively reduced.

This may be particularly advantageous in a vertical (or longitudinal) rotary compressor. That is, in the vertical rotary compressor, since oil drops due to its own weight, the oil amount of the third main back pressure groove 1315c is relatively smaller than the oil amount of the third sub back pressure groove 1325c. Therefore, in the vicinity of the reference point P, the back pressure on the rear side of the vane 135 is unevenly distributed in the axial direction, so that the chattering phenomenon and/or the eccentric wear between the vane 135 and the cylinder 133 may increase. However, as shown in the present embodiment, in the case where the first back pressure passage portion 1381 is connected to the third sub back pressure groove 1325c and the second back pressure passage portion 1382 is connected to the third main back pressure groove 1315c, the back pressure applied to the corresponding vane 135 may be approximately uniformly distributed in the axial direction. Accordingly, in the case of the vertical rotary compressor, the friction loss or wear due to the chattering phenomenon between the vane 135 and the cylinder 133 near the reference point P can be reduced, thereby improving the compression efficiency.

Although not shown, the first back pressure passage 1381 may not communicate with the oil supply passage 125 of the rotary shaft 123, but may directly communicate with the internal space 110a of the housing 110 through the sub-bearing 132 as in the embodiment of fig. 11. The description thereof is replaced by the description of the embodiment of fig. 11.

On the other hand, other embodiments of the main bearing and the sub-bearing will be described below.

That is, in the foregoing embodiment, only the primary and secondary back pressure grooves are formed in the primary and secondary sliding surfaces, respectively, but depending on the case, a lubrication portion may be formed in at least one side of the primary and secondary sliding surfaces in addition to the primary or secondary back pressure grooves. Hereinafter, description will be given mainly on an example in which the first lubricating portion and the second lubricating portion are formed on the main sliding surface and the sub sliding surface, respectively.

Fig. 15 is a perspective view showing another embodiment of the compression part of fig. 1 in an exploded manner, fig. 16 is a plan view showing the main bearing of fig. 15, fig. 17 is a plan view showing the sub-bearing of fig. 15, and fig. 18 is an assembled sectional view of fig. 15.

Referring to fig. 15 to 18, the basic structure of the vane rotary compressor of the present embodiment and the operational effects thereof are almost the same as those of the previous embodiments, and thus, the detailed description thereof is replaced with the description of the previous embodiments. For example, in the vane rotary compressor of the present embodiment, the basic structures of the main bearing 131, the sub-bearing 132, the cylinder 133, the roller 134, and the vane 135 constituting the compression portion are almost the same as those of the previous embodiments.

In addition, in the secondary sliding surface 1321a of the secondary bearing 132 of the present embodiment, the first secondary back pressure groove 1325a, the second secondary back pressure groove 1325b, and the third secondary back pressure groove 1325c are arranged in order in the rotation direction of the rollers 134 with the reference point P as a start point. The first sub back pressure groove 1325a is formed to extend from the suction pressure region to the intermediate pressure region, the second sub back pressure groove 1325b is formed to extend from the intermediate pressure region to the discharge pressure region, and the third sub back pressure groove 1325c is formed in the discharge pressure region. Thereby, the first sub back pressure groove 1325a forms a first intermediate pressure, the second sub back pressure groove 1325b forms a second intermediate pressure (or a first discharge pressure), and the third sub back pressure groove 1325c forms a super discharge pressure (or a second discharge pressure).

Further, the third sub back pressure recess 1325c may communicate with the oil supply passage 125 of the rotary shaft 123 through the first back pressure passage portion 1381, and the third main back pressure recess 1315c may communicate with the oil supply passage 125 of the rotary shaft 123 through the second back pressure passage portion 1382. The first back pressure passage 1381 and the second back pressure passage 1382 are the same as those in the embodiment of fig. 13, and therefore, the description thereof is replaced with the description of the embodiment of fig. 13.

However, in the present embodiment, a first lubrication section 1391 may be formed in the secondary sliding surface 1321a of the secondary bearing 132, and a second lubrication section 1392 may be formed in the primary sliding surface 1312a of the main bearing 131. First lubrication section 1391 and second lubrication section 1392 may be formed at positions corresponding to each other in the axial direction with roller 134 or vane 135 interposed therebetween.

First lubrication 1391 may include a first lubrication groove 1391a and a first lubrication passageway 1391b. First lubrication groove 1391a is a portion of space forming substantial first lubrication section 1391, and first lubrication passage 1391b is a portion that directs oil to first lubrication groove 1391b.

The first lubrication groove 1391a may be formed to be spaced apart from the outer peripheral sides of the second and third sub back

pressure grooves

1325b and 1325c in the radial direction by a preset interval and to surround these second and third sub back

pressure grooves

1325b and 1325c. Thus, the first lubrication groove 1391a may radially overlap with the second and third sub back

pressure grooves

1325b and 1325c.

Specifically, the first lubrication groove 1391a is formed in a circular arc shape, and the circular arc length L4 of the first lubrication groove 1391a may be greater than or equal to the length of the sum of the circular arc length L2 of the second sub back pressure groove 1325b and the circular arc length L3 of the third sub back pressure groove 1325c. In the present embodiment, an example is shown in which the circular arc length L4 of the first lubrication groove 1391a is larger than the length of the sum of the circular arc length L2 of the second sub back pressure groove 1325b and the circular arc length L3 of the third sub back pressure groove 1325c. Thus, the axial top faces of the respective vanes 135 passing through the second and third secondary

back pressure grooves

1325b, 1325c will almost necessarily straddle the first lubrication groove 1391a to slide laterally through the first lubrication groove 1391a.

The first lubrication passage 1391b may be formed to communicate between the first lubrication groove 1391a and the oil storage space 110b of the housing 110. For example, an axially upper end of the first lubrication passage 1391b may penetrate through a bottom surface of the first lubrication groove 1391a to communicate with the first lubrication groove 1391a, and an axially lower end of the first lubrication passage 1391b may penetrate through a bottom surface of the sub-plate portion 1321 to be submerged in and communicate with the oil storage space 110b of the housing 110. Thus, the oil stored in the oil storage space 110b of the housing 110 can be directly supplied to the first lubrication groove 1391a through the first lubrication passage 1391b.

The inner diameter D4 of the first lubrication passage 1391b may be greater than or equal to the inner diameter D3 of the first back pressure passage 1381. Thereby, the oil of the oil storage space 110b stored in the housing 110 can be rapidly moved toward the first lubrication groove 1391a through the first lubrication passage 1391b.

Second lubrication 1392 may include a second lubrication groove 1392a and a second lubrication passageway 1392b. Second lubrication groove 1392a is a portion of space forming a substantial second lubrication section 1392, and second lubrication passage 1392b is a portion that directs oil to second lubrication groove 1392a.

The second lubrication groove 1392a may be formed symmetrically with respect to the aforementioned first lubrication groove 1391a with reference to the roller 134. Thus, the description of the second lubrication groove 1392a is replaced by the description of the first lubrication groove 1391a.

The second lubrication passage 1392b may be formed to connect between the inner peripheral surface of the second lubrication groove 1392a and the outer peripheral surface of the second main back pressure groove 1315b or the third main back pressure groove 1315c facing thereto. In the present embodiment, an example is shown in which the second lubrication passage 1392b extends from the second main back pressure groove 1315b to the second lubrication groove 1392a.

If second lubrication passage 1392b extends from third main back pressure groove 1315c to second lubrication groove 1392a, the volume of third main back pressure groove 1315c will be greater than the volume of second main back pressure groove 1315b, which may correspondingly be detrimental to increasing the pressure of third main back pressure groove 1315c. Therefore, in the case where the second lubrication passage 1392b is separated from the third main back pressure groove 1315c and connected to the second main back pressure groove 1315b, it will be possible to facilitate securing of the super discharge pressure (or the second discharge pressure) of the third main back pressure groove 1315c.

In addition, as second lubrication passage 1392b is connected to second main back pressure groove 1315b, oil of second main back pressure groove 1315b may be supplied to second lubrication groove 1392a. Thereby, oil can be quickly supplied to the second lubrication groove 1392a without adding an additional lubrication passage.

As with the present embodiment, where second lubrication groove 1392a is connected to second primary back pressure groove 1315b by second lubrication passage 1392b, the width (not labeled) and/or axial depth H4 of second lubrication groove 1392a may be less than or equal to the width (not labeled) and/or axial depth H2 of second primary back pressure groove 1315b.

For example, in the case where the width and/or axial depth H4 of the second lubrication groove 1392a is greater than the width and/or axial depth H2 of the second primary back pressure groove 1315b, oil of the second primary back pressure groove 1315b may excessively flow out to the second lubrication groove 1392a through the second lubrication passage 1392b. Accordingly, the amount of oil supplied to the corresponding back pressure chamber 1344 is reduced, so that the back pressure applied to the corresponding vane 135 is weakened. Thus, where the width and/or axial depth H4 of second lubrication groove 1392a is less than or equal to the width and/or axial depth H2 of second and/or third primary

back pressure grooves

1315b and 1315c, it would be possible to be advantageous in terms of back pressure.

As described above, in the case where the secondary bearing 132 is formed with the first lubrication 1391 and the main bearing 131 is formed with the second lubrication 1392, the axial side faces of the respective vanes 135 passing through the second secondary back pressure groove 1325b and the second main back pressure groove 1315b, the third secondary back pressure groove 1325c and the third main back pressure groove 1315c will straddle the first lubrication groove 1391a and the second lubrication groove 1392a and slide in the lateral direction through the first lubrication groove 1391a and the second lubrication groove 1392a. Thus, the oil contained in the first and

second lubricating grooves

1391a, 1392a forms a wide and thick oil film between the axial side surfaces of the vane 135 passing through the first and

second lubricating grooves

1391a, 1392a and the

counter sliding surface

1321a, 1311a facing the same.

This prevents a so-called "discontinuous sliding phenomenon" in which the axial side surfaces of the corresponding vanes 135 slide again after being temporarily stopped due to excessive contact with the secondary sliding surface 1321a and/or the primary sliding surface 1311 a. Accordingly, the vane 135 smoothly slides along the vane groove 1343, and the chattering phenomenon of the vane 135 can be suppressed. Furthermore, by suppressing the increase of the collision force with the cylinder 133 due to the discontinuous sliding phenomenon of the vane 135, the abrasion of the vane 135 and/or the cylinder 133 can be more effectively prevented.

On the other hand, other embodiments of the first lubricating portion and the second lubricating portion will be described below.

That is, in the foregoing embodiment, the first lubrication groove and the second lubrication groove are formed as one long groove, respectively, but at least one of the first lubrication groove and the second lubrication groove may be formed as a plurality of grooves according to circumstances.

Fig. 19 is a perspective view showing another example of the lubrication portion of fig. 15, and fig. 20 is a sectional view of fig. 19.

Referring to fig. 19 and 20, the vane rotary compressor of the present embodiment may be constructed in a basic structure and its operational effects almost the same as those of the previous embodiments. For example, in the vane rotary compressor of the present embodiment, the basic structures of the main bearing 131, the sub-bearing 132, the cylinder 133, the roller 134, and the vane 135 constituting the compression portion are almost the same as those of the previous embodiments.

In addition, in the vane rotary compressor of the present embodiment, the first main back pressure groove 1315a, the second main back pressure groove 1315b, and the third main back pressure groove 1315c are provided at the main bearing 131 at a predetermined interval from each other in the circumferential direction, the first sub back pressure groove 1325a, the second sub back pressure groove 1325b, and the third sub back pressure groove 1325c are provided at the sub bearing 132 at a predetermined interval from each other in the circumferential direction, and these main

back pressure grooves

1315a, 1315b, 1315c and sub back

pressure grooves

1325a, 1325b, 1325c may be formed similarly to the main back pressure groove 1315 and the sub back pressure groove 1325 of the foregoing embodiment.

The vane rotary compressor of the present embodiment is provided with a first back pressure passage 1381 and a second back pressure passage 1382, and these

back pressure passages

1381, 1382 may be formed in the same manner as the

back pressure passages

1381, 1382 of the above-described embodiments.

However, the vane rotary compressor of the present embodiment is provided with the first lubrication section 1391 and the second lubrication section 1392, and the first lubrication groove 1391a and/or the second lubrication groove 1392a may be formed as a plurality of grooves differently from the aforementioned embodiment of fig. 15. In the present embodiment, an example is shown in which the first lubrication groove 1391a is formed as a plurality of grooves, and on the other hand, the second lubrication groove 1392a is formed as one groove.

For example, as shown in fig. 19, the first lubrication grooves 1391a may be separated into a plurality of grooves and disposed at a predetermined interval from each other in the circumferential direction. In this case, the first lubrication grooves 1391a formed as a plurality of grooves may be formed in a circular shape, respectively, or may also be formed in a short circular arc shape.

In addition, a first lubrication passage 1391b may independently communicate with each first lubrication groove 1391a. In this case, as shown in the aforementioned embodiment of fig. 15, one end of each first lubrication passage 1391b may directly communicate with the first lubrication groove 1391a, and the other end thereof may directly communicate with the oil storage space 110b of the housing 110. Thereby, the oil stored in the oil storage space 110b of the housing 110 can be quickly supplied to the respective first lubrication grooves 1391a through the respective first lubrication passages 1391b.

As described above, in the case where the first lubrication groove 1391a is formed as a plurality of grooves, oil is continuously supplied to the first lubrication groove 1391a, and therefore, the oil passes over the first lubrication groove 1391a to form a wide and thick oil film over the entire secondary sliding surface 1321a, whereby the friction loss between the vanes 135 and the secondary sliding surface 1321a can be reduced.

In addition, in the present embodiment, as the first lubrication groove 1391a becomes shorter, the cross section generated in the circumferential direction between the blade 135 and the first lubrication portion (to be exact, the first lubrication groove) 1391 becomes shorter. As a result, the vane 135 contacts the flat secondary sliding surface 1321a more in the circumferential direction, and the friction loss between the vane 135 and the secondary sliding surface 1321a can be reduced.

On the other hand, a further embodiment of the first lubricating portion and the second lubricating portion will be described below.

That is, the lubrication groove is provided in the foregoing embodiment, but according to circumstances, only the lubrication passage may be formed without the lubrication groove.

Fig. 21 is a perspective view showing still another embodiment of the lubricating portion of fig. 15, and fig. 22 is a sectional view of fig. 21.

Referring to fig. 21 and 22, the vane rotary compressor of the present embodiment may be constructed in a basic structure and its operational effects almost the same as those of the previous embodiments. For example, in the vane rotary compressor of the present embodiment, the basic structures of the main bearing 131, the sub-bearing 132, the cylinder 133, the roller 134, and the vane 135 constituting the compression portion are almost the same as those of the previous embodiments.

In addition, in the vane rotary compressor of the present embodiment, the first, second, and third main

back pressure grooves

1315a, 1315b, and 1315c may be provided at the main bearing 131 at predetermined intervals from each other in the circumferential direction, and the first, second, and third sub back

pressure grooves

1325a, 1325b, and 1325c may be provided at the sub bearing 132 at predetermined intervals from each other in the circumferential direction. These primary

back pressure grooves

1315a, 1315b, 1315c and secondary

back pressure grooves

1325a, 1325b, 1325c may be formed the same as the primary back pressure groove 1315 and secondary back pressure groove 1325 of the foregoing embodiment.

back pressure passages

1381, 1382 may be formed in the same manner as the

back pressure passages

1381, 1382 of the above-described embodiments.

However, the vane rotary compressor of the present embodiment is provided with the first lubrication section 1391 and the second lubrication section 1392, and at least one side of the first lubrication section 1391 and the second lubrication section 1392 may be constituted only by a lubrication passage. In the present embodiment, an example is shown in which first lubrication section 1391 is constituted by a plurality of first lubrication passages 1391b. Second lubrication section 1392 is identical to the embodiment of fig. 15 described above, and therefore the description thereof is replaced by the description of the embodiment of fig. 15.

First lubrication section 1391 of the present embodiment may include a plurality of first lubrication passages 1391b.

A plurality of first lubrication passages 1391b may pass through the sub-bearing 132 to communicate with the oil reservoir 110b of the housing 110. For example, an axial upper end of the first lubrication passage 1391b may penetrate the sub-sliding surface 1321a, and an axial lower end of the first lubrication passage 1391b may penetrate the bottom surface of the sub-plate portion 1321 and be submerged in the oil storage space 110b of the housing 110 to communicate therewith. Thus, the oil stored in the oil storage space 110b of the housing 110 can directly flow into the secondary sliding surface 1321a through the first lubrication passage 1391b.

The inner diameter D4 of the plurality of first lubrication passages 1391b may be greater than or equal to the inner diameter D3 of the first back pressure passage 1381. Thereby, the oil stored in the oil storage space 110b of the housing 110 can rapidly move to the secondary sliding surface 1321a through the first lubrication passage 1391b.

The plurality of first lubrication passages 1391b may be formed at approximately equal intervals in the circumferential direction. The plurality of first lubrication passages 1391b may be formed to have the same inner diameter as each other, or may be formed to have different inner diameters from each other. For example, the inner diameter of the first lubrication passage 1391b may be formed to increase as it approaches the reference point P with reference to the rotation direction of the roller 134. In the present embodiment, an example is shown in which the plurality of first lubrication passages 1391b have the same inner diameter as each other. This facilitates machining of the first lubrication passage 1391b, and allows oil to flow into the secondary sliding surface 1321a almost uniformly.

As described above, in the case where the first lubrication section 1391 is formed only of the plurality of first lubrication passages 1391b, the oil stored in the oil storage space 110b of the housing 110 is also continuously supplied to the secondary sliding surface 1321a through the first lubrication passages 1391b, and the oil is widely spread at the secondary sliding surface 1321a. Thus, even if the lubrication groove 1391a as in the foregoing embodiment is not formed in the secondary sliding surface 1321a, a wide and thick oil film is formed on the secondary sliding surface 1321a, so that the friction loss between the vane 135 and the secondary sliding surface 1321a can be reduced. This prevents the discontinuous sliding phenomenon of the vane 135, and thus can suppress the chattering phenomenon of the vane 135.

In addition, in the present embodiment, as the first lubrication groove 1391a of the aforementioned embodiment of fig. 15 and 19 is eliminated, the intersection interval between the vane 135 and the first lubrication section 1391 in the circumferential direction will be greatly shortened. Thereby, the vane 135 contacts the nearly flat secondary sliding surface 1321a in the circumferential direction, and the friction loss between the vane 135 and the secondary sliding surface 1321a can be further reduced.

Although not shown, the discharge port may be formed in the cylinder instead of the main bearing and the sub-bearing. In this case, the blade support structure using the aforementioned compression coil spring can be similarly applied.

Claims

1. A rotary compressor is characterized in that the rotary compressor is provided with a compressor body,

the method comprises the following steps:

a driving motor disposed in the inner space of the housing;

a rotating shaft coupled to a rotor of the driving motor, the rotating shaft having a hollow shape through which an oil supply passage passes;

a cylinder barrel disposed in the inner space of the housing to form a compression space;

a roller that is provided on the rotary shaft and is accommodated in the compression space, the roller being disposed eccentrically with respect to an inner peripheral surface of the cylinder tube;

a blade slidably inserted into a blade groove provided in the roller; and

a main bearing and a sub bearing respectively arranged at two axial sides of the cylinder barrel and forming the compression space together with the cylinder barrel,

a discharge port for discharging the refrigerant compressed in the compression space into the internal space of the housing is formed in at least one of the main bearing and the sub bearing, a plurality of back pressure grooves communicating with a rear side of the blade are formed at a position on one side of the discharge port so as to be spaced apart from each other in a circumferential direction, and a back pressure groove closest to the discharge port among the plurality of back pressure grooves communicates with the internal space of the housing through a back pressure passage portion penetrating through at least one of the main bearing and the sub bearing.

2. The rotary compressor of claim 1,

bearing holes into which the rotating shaft is inserted and which support the rotating shaft are formed in the main bearing and the sub-bearing, respectively,

the back pressure groove closest to the discharge port is radially spaced from the inner peripheral surface of the bearing hole to be separated from the bearing hole.

3. The rotary compressor of claim 1,

at least one oil supply hole is formed in the middle of the oil supply passage, the at least one oil supply hole penetrates from the inner circumferential surface of the oil supply passage to the outer circumferential surface of the rotary shaft,

the back pressure passage portion has an inner diameter smaller than or equal to an inner diameter of the oil supply hole.

4. The rotary compressor of claim 1,

the back pressure passage is located on one axial side of the oil supply hole.

5. The rotary compressor of claim 1,

the back pressure passage portion eccentrically communicates from the center of the back pressure groove to a reference point side where the roller and the cylinder are closest to each other.

6. The rotary compressor of claim 1,

the back pressure passage portion is formed at a position periodically overlapping the vane when the vane reciprocates.

7. The rotary compressor of claim 1,

the back pressure passage portion has an inner diameter smaller than a width of the vane.

8. The rotary compressor of claim 1,

the back pressure passage portion includes:

a first back pressure hole penetrating from an inner circumferential surface of the oil supply passage to an outer circumferential surface of the rotary shaft; and

a second back pressure hole penetrating at least one of the main bearing and the sub bearing to communicate with the first back pressure hole, and communicating with the back pressure groove,

the inner diameter of the second back pressure hole is smaller than or equal to the inner diameter of the first back pressure hole.

9. The rotary compressor of claim 8,

a communication groove is formed between the first back pressure hole and the second back pressure hole,

the communication groove has a cross-sectional area larger than a cross-sectional area of at least one of the first back pressure hole and the second back pressure hole.

10. The rotary compressor of claim 9,

the communication groove is formed in a circular arc shape to periodically communicate the first back pressure hole with the second back pressure hole, or is formed in a circular shape to continuously communicate the first back pressure hole with the second back pressure hole.

11. The rotary compressor of claim 1,

one end of the back pressure passage portion communicates with the back pressure groove closest to the discharge port, and the other end of the back pressure passage portion communicates with the internal space of the housing through at least one of the main bearing and the sub bearing,

the volume of a back pressure groove of the plurality of back pressure grooves which is most adjacent to the discharge port is smaller than the volumes of the back pressure grooves other than the back pressure groove which is most adjacent to the discharge port.

12. The rotary compressor of claim 11,

the length of an arc of a back pressure groove of the plurality of back pressure grooves which is most adjacent to the discharge port is smaller than the lengths of arcs of the other back pressure grooves except the back pressure groove which is most adjacent to the discharge port,

alternatively, the depth of a back pressure groove in the plurality of back pressure grooves, which is most adjacent to the discharge port, is smaller than the depths of the back pressure grooves other than the back pressure groove most adjacent to the discharge port.

13. The rotary compressor of any one of claims 1 to 12,

a lubrication portion is formed on at least one of the main bearing and the sub-bearing radially outside the back pressure groove,

the lubricating portion is formed such that at least a part thereof overlaps in the radial direction with the back pressure groove that is most adjacent to the discharge port.

14. The rotary compressor of claim 13,

the lubrication portion includes:

a lubrication groove spaced from the back pressure groove; and

a lubrication passage connecting between the lubrication groove and the inner space of the housing, guiding the oil stored in the inner space of the housing to the lubrication groove,

the lubrication groove is formed as a groove extending in the circumferential direction,

the lubricating passage is formed in at least one number in the circumferential direction of the lubricating groove.

15. The rotary compressor of claim 13,

the lubrication portion includes:

a lubrication groove spaced from the back pressure groove; and

the lubrication groove is formed as a plurality of grooves spaced apart from each other in a circumferential direction,

the lubrication passages are independently communicated with the plurality of lubrication grooves respectively.

16. The rotary compressor of claim 13,

the lubrication portion includes one or more lubrication passages penetrating the sub-bearing,

one end of the lubrication passage opens to the vane at one axial side of the sub-bearing, and the other end of the lubrication passage opens to the inner space of the housing at the other axial side of the sub-bearing.

17. The rotary compressor of claim 13,

the lubrication section includes:

a lubrication groove spaced from the back pressure groove; and

a lubrication passage extending from at least one of the back pressure grooves other than the back pressure groove closest to the discharge port and communicating with the lubrication groove.

18. The rotary compressor of claim 17,

the axial depth of the lubrication groove is less than or equal to the axial depth of the back pressure groove connected with the lubrication groove.