WO2013015575A2 - Vane rotary compressor - Google Patents

Abstract

The present invention relates to a vane rotary compressor in which, while a rotor is rotating, the volume of a compressing chamber is reduced and a fluid such as a refrigerant is compressed. The vane rotary compressor according to one embodiment of the present invention is provided with the compressing chamber, the inner circumferential surface of which is formed in the shape of an involute curve, wherein the rotor is hinge-coupled with a plurality of cantilever vanes such that compression efficiency is high and noise is prevented from occurring during the operation of the compressor.

Description

Vane rotary compressor

The present invention relates to a vane rotary compressor in which a fluid, such as a refrigerant, is compressed while the volume of the compression chamber is reduced during rotation of the rotor. More specifically, the compression chamber has an inner circumferential surface in the form of an involute curve, and the rotor has a plurality of cantilever beams. A vane rotary compressor is hinged to the vane.

The vane rotary compressor is used in an air conditioner and the like and compresses a fluid such as a refrigerant to supply it to the outside.

1 is a cross-sectional view schematically showing a conventional vane rotary compressor disclosed in Japanese Patent Laid-Open No. 2009-07937 (Patent Document 1), and FIG. 2 is a cross-sectional view taken along the line A-A of FIG.

As illustrated in FIGS. 1 and 2, a conventional vane rotary compressor includes a hollow cylinder 1, a rotor 2 installed inside the cylinder 1, and a vane slot 3 of the rotor 2. The vane 4 inserted into the slide movably, the rotating shaft 5 integrally formed with the rotor 2 and rotatably supported by the rotor 2, and both ends of the cylinder 1, and having a compression chamber ( And a front cover 6 and a rear cover 7 forming 8).

At this time, the inlet 9 and the outlet 10 communicate with the compression chamber 8, the outlet 10 is provided with a discharge valve 11, the rear housing 13 is mounted on the rear of the rear cover (7) The high pressure passage 12 is formed in the rear cover 7 so as to communicate with the high pressure chamber therein.

On the other hand, the lower portion of the rear housing 13 is formed with an oil room 13a, in which the oil contained in the compressed refrigerant compressed in the compression chamber 8 and discharged into the high pressure chamber is contained in an oil separator (not shown) in the rear housing 13. Are stored in this oil room 13a.

At this time, the oil stored in the oil room (13a) is supplied toward the rotor (2) through the oil supply passage 18 formed on one side of the rear cover (7), the compressed refrigerant in the upper portion of the rear housing (13) air conditioning system A discharge port 14 for discharging the gas is formed.

The space divided into the vane slot 3, the front cover 6, and the rear cover 7 constitutes the back pressure chamber 20, and the vanes 4 are cut by the pressure of the back pressure chamber 20. It slides along and the tip part is supported by the inner peripheral surface of the cylinder 1.

The rear cover 7 is formed with an arc-shaped oil groove 19 communicating with the back pressure chamber 20 at the rear end of the vane 4 and the oil supply passage 18.

The conventional vane rotary compressor configured as described above operates as follows.

First, when the rotor 2 is rotated together with the rotary shaft 5 by receiving power from a driving source such as an engine, low-pressure refrigerant flows into the compression chamber 8 through the inlet 9, and the As the volume of the compression chamber 8 decreases with rotation, the refrigerant is compressed.

Thereafter, the compressed refrigerant is discharged into the high pressure passage 12 through the discharge port 10, flows into the rear housing 13, and is supplied to the air conditioning system through the discharge port 14.

At this time, the oil separated by the oil separator in the upper portion of the rear housing 13 is stored away from the lower oil room (13a), the stored oil is passed through the oil supply passage 18 and the oil groove (19) vanes (4) ) Is supplied to the back pressure chamber 20 to lubricate the vanes 4.

On the other hand, the vane 4 is pushed along the vane slot 3 by the pressure of the oil supplied to the back pressure chamber 20, and its tip is closely supported by the inner circumferential surface of the cylinder 1, The space between the outer circumferential surfaces of the rotor 2 is partitioned into a plurality of compression chambers 8.

By the way, when the vanes 4 are formed in a straight line as in the conventional example described above, in order to maintain the state where the tip portion of the vanes 4 is in close contact with the inner circumferential surface of the cylinder 1, a high pressure is applied to the back pressure chamber 20. Since the oil needs to be continuously supplied, it causes an increase in the power consumption (HP) of the compressor.

Further, as the vane 4 is pushed by the high pressure oil pressure in the back pressure chamber 20, excessive force is concentrated at the point of contact between the tip of the vane 4 and the inner circumferential surface of the cylinder 1. This may cause the torque to rise.

In addition, when the proper refrigerant discharge pressure is not formed at the initial stage of the driving of the compressor, the pressure of the separated oil is also insufficient, so that the force for pushing the vanes 4 in the back pressure chamber 20 is insufficient, so that the cylinder 1 There is also a problem that the tip portion of the vane (4) on the inner circumferential surface of the) causes discontinuous friction and chattering noise.

In addition, since the conventional linear vanes have a limited distance from which they can be buried from the vane slot, the inner circumferential surface shape of the cylinder may be a simple circle as described above (one stroke / one rotation), or an ellipse as shown in FIG. 3 below. It has been used only in (2 strokes / 1 rotation).

3 is a cross-sectional view of a two-stroke vane rotary compressor disclosed in Japanese Patent Application Laid-Open No. 2010-31759 (Patent Document 2), wherein the compression-suction stroke is performed twice at one rotation of the rotor.

However, when the rotor 2 'makes contact with the inner circumferential surface of the cylinder 1' at two points in the cylinder 1 'having an elliptical hollow, the compression stroke is shortened to affect the power consumption HP. This results in a lower COP of the compressor and directly affects the fuel economy of the vehicle.

In addition, as described in the example of the one-stroke compressor in FIGS. 1 and 2, chattering noise is generated by the impact of the vane 4 ′ at the initial stage of compressor operation, or the tip of the vane 4 ′ and the inner circumferential surface of the cylinder 1 ′. The excessive force is concentrated at the contact point of the shaft, which increases the torque of the rotating shaft 5 ', and the compressor consumption power HP increases due to the continuous supply of high pressure oil to the back pressure chamber 20'. This is inevitable.

The present invention has been made to solve the problems as described above, an embodiment of the present invention, it is possible to increase the coefficient of performance (COP) of the compressor, the vane is not in close contact with the inner circumferential surface of the cylinder when operating the cylinder inner circumferential surface Chattering noise generated while hitting is avoided and associated with vane rotary compressors that can reduce packages on the same capacity basis.

According to a preferred embodiment of the present invention, the inner circumferential surface of the hollow cylinder made of an involute curve in the circumferential direction; A front housing having a space formed therein so that the cylinder is installed, and a rear of the space opened; A rear housing coupled to a rear end of the front housing to close the space part; A rotor installed in the cylinder and rotating to receive power of a driving source from a rotating shaft; One vane is hinged to an outer circumferential surface of the rotor, and a vane rotary compressor including a vane having the other end in contact with the inner circumferential surface of the cylinder as the rotor rotates.

Here, the vanes are provided in plurality in the circumferential direction of the rotor spaced apart from each other.

At this time, the outer surface of the vane is formed with a curvature corresponding to the outer peripheral surface of the rotor.

In addition, the outer circumferential surface of the rotor is formed with a receiving groove for accommodating the vane, when the vane is accommodated in the receiving groove, the outer surface of the vane and the outer circumferential surface of the rotor to form a circumferential surface of the same curvature.

Meanwhile, one side of the outer circumferential surface of the front housing protrudes outward to form a first oil room.

In addition, one side of the outer peripheral surface of the cylinder is recessed to form a second oil room.

In addition, the lower end of the cylinder portion of the front housing is protruded to the third oil room and the fourth oil room spaced apart from each other are formed.

At this time, an oil channel for guiding the flow of oil from one side of the fourth oil room to the rear end of the rotary shaft is formed on one side of the rear housing.

At this time, the front and rear sides of the rotor are respectively in contact with the front housing and the rear housing, a plurality of rotor flow paths are formed through the axial direction, the oil supplied through the oil flow path to lubricate the rear sliding surface of the rotor On the other hand, the rotor flow path to lubricate the shear sliding surface of the rotor.

1 is a cross-sectional view schematically showing a conventional single stroke vane rotary compressor.

2 is a cross-sectional view taken along the line A-A of FIG.

3 is a cross-sectional view of a conventional two-stroke vane rotary compressor.

4 is a perspective view of a vane rotary compressor according to an embodiment of the present invention.

Figure 5 is a longitudinal cross-sectional view of the vane rotary compressor according to an embodiment of the present invention.

FIG. 6 is a cross-sectional view taken along the line BB of FIG. 5. FIG.

Figure 7 is a perspective view of the vane rotary compressor according to an embodiment of the present invention from the rear.

8 is a graph showing a change in the volume of the compression chamber according to the suction stroke and compression stroke of a conventional single stroke vane rotary compressor.

9 is a graph showing the change in the volume of the compression chamber according to the suction stroke and compression stroke of the vane rotary compressor according to an embodiment of the present invention.

10 is a graph comparing the rotation shaft torque of the compressor when the conventional linear vanes and cantilever vanes according to an embodiment of the present invention are respectively applied.

Hereinafter, a preferred embodiment of the vane rotary compressor according to an embodiment of the present invention will be described with reference to the accompanying drawings. In this process, the thickness of the lines or the size of the components shown in the drawings may be exaggerated for clarity and convenience of description.

In addition, terms to be described below are terms defined in consideration of functions in the present invention, which may vary according to the intention or convention of a user or an operator. Therefore, definitions of these terms should be made based on the contents throughout the specification.

In addition, the following examples are not intended to limit the scope of the present invention but merely illustrative of the components set forth in the claims of the present invention, which are included in the technical spirit throughout the specification of the present invention and constitute the claims Embodiments that include a substitutable component as an equivalent in the element may be included in the scope of the present invention.

Example

4 is a perspective view of a vane rotary compressor according to an embodiment of the present invention, Figure 5 is a longitudinal cross-sectional view of the vane rotary compressor according to an embodiment of the present invention.

As shown in Figure 4 and 5, the vane rotary compressor 100 according to an embodiment of the present invention, the front housing 300, the rear is open so that the cylinder 200 is accommodated therein, and the front housing ( The overall appearance is formed by the rear housing 400 coupled to the rear end of the 300 and closing the opening of the front housing 300.

In addition, the front housing 300 is formed integrally with the cylinder portion 310 and the cylinder portion 310 in the axial front of the cylinder portion 310 in which the space portion is formed inside to close the front of the space portion. It includes a head portion 320, the hollow portion 200 is mounted to the space portion.

At this time, the inside of the cylinder 200 is rotated by the power of the drive shaft 500, the rotor 600 and the rotor 600 to rotate with the rotary shaft 500 receives the rotational force of the rotary shaft 500, the rotor 600 A plurality of vanes 700 are mounted on the outer circumferential surface of the panel.

In addition, the rear housing 400 is coupled to the axial rear of the front housing 300 to close the rear of the space part.

Meanwhile, a suction port 321 for sucking refrigerant from the outside and a discharge port 322 for discharging high-pressure refrigerant compressed in the cylinder 200 to the outer peripheral surface of the head 320 of the front housing 300 are provided. It is provided spaced apart from each other in the circumferential direction.

In addition, the pulley coupling portion 323 is extended to the front center of the head 320, so that the pulley 800 of the electronic clutch (not shown) is coupled.

FIG. 6 is a cross-sectional view taken along the line B-B in FIG. 5.

Here, the thick arrows shown in Figure 6 indicates the intake and discharge direction of the refrigerant, the solid arrow indicates the rotation direction of the rotary shaft 500, the dashed-dotted arrow indicates the flow of the refrigerant compressed to high pressure, The dashed arrows indicate the flow of the refrigerant from which oil is separated as it passes through the oil separation pipe 324.

As shown in FIG. 6, the rotor 600 having the vanes 700 is inserted into the hollow of the cylinder 200 so that the hollow of the cylinder 200 is compressed by the rotation of the rotor 600. Compression space is achieved.

At this time, one side of the cylinder 200 is formed in each of the inlet port 210 and the outlet port 220 is communicated to one side of the compression space, one side of the inlet port 210 is in communication with the suction port 321 of the head portion 320 One side of the discharge port 220 communicates with the discharge port 322 of the head 320.

Therefore, the refrigerant sucked through the suction port 321 from the outside enters the hollow of the cylinder 200 which is the compression space through the suction port 210, undergoes the compression process, and then discharges the discharge port through the discharge port 220 under high pressure. 322 is supplied to the outside.

The rotor 600 is coupled to a rotating shaft 500 connected to an electromagnetic clutch (not shown) driven by a driving motor (not shown) or an engine belt, and axially rotates together with the rotating shaft 500, wherein the rotor ( A plurality of rotor passages 610 may be formed in the axial direction in the 600.

At this time, the tip portion of the vane 700 that rotates and protrudes from the outer circumferential surface of the rotor 600 is supported by the inner circumferential surface of the cylinder 200, so as to the inner circumferential surface of the cylinder 200, the outer circumferential surface of the rotor 600, and the vane 700. The space formed constitutes the compression chamber 230.

In addition, the front housing 300 and the rear housing 400 are coupled to both openings of the compression chamber 230 to seal the compression chamber 230 in the front and rear directions, respectively, in which the rotor 600 is shown in FIG. 5. The front surface of the front housing 300 is in contact with the head 320, the rotor 600 is in contact with the front surface of the rear housing 400.

Therefore, the refrigerant introduced into the hollow of the cylinder 200 through the suction port 210 is trapped in the sealed compression chamber 230 and compressed by the rotation of the rotor 600.

A plurality of vanes 700 are spaced apart from each other in the circumferential direction along the outer circumferential surface of the rotor 600, and thus the hollow of the cylinder 200 is partitioned into a plurality of compression chambers 230.

The refrigerant trapped in the compression chamber 230 is compressed as the volume of the compression chamber 230 decreases when the rotor 600 rotates. For this purpose, the inner circumferential surface of the cylinder 200 changes the rotation direction of the rotor 600 when the refrigerant is compressed. Accordingly, the diameter of the suction port 210 toward the discharge port 220 is gradually formed in the form of an involute curve.

That is, in the compression rotation direction of the rotor 600, the diameter of the inner circumferential surface of the cylinder 200 gradually decreases from the suction port 210 to the discharge port 220 along the inner circumferential surface of the cylinder 200, and the inner circumferential surface of the cylinder 200. As the gap between the outer circumferential surfaces of the rotor 600 gradually narrows, the volume of the compression chamber 230 is reduced.

At this time, the rotor 600 is installed in the hollow of the cylinder 200 such that the inner circumferential surface of the cylinder 200 and the outer circumferential surface of the rotor 600 are concentric in cross section. That is, in the involute curve drawn along the inner circumferential surface of the cylinder 200, the center of the start point and the end point is the same as the center of the rotor 600.

Therefore, unlike the conventional case, according to one embodiment of the present invention does not require a separate eccentric shaft for revolving the rotor 600 in the cylinder 200, according to the power loss or according to the conventional eccentric shaft installation It is possible to prevent problems of vibration and noise generation.

8 and 9 are graphs showing changes in the compression chamber volume according to the suction stroke and the compression stroke of the conventional single stroke vane rotary compressor and the vane rotary compressor according to an embodiment of the present invention, respectively.

As shown in FIG. 8, in the example in which a conventional single stroke (one stroke, one stroke, see FIG. 2) circular cylinder is applied, the suction stroke and the compression stroke are 5.5 to 4.5, and the suction stroke appears somewhat longer. In view of the fact that the discharge port is not formed at the compression end point precisely because of the difficulty in forming, the suction stroke is much longer than the compression line information. The same is true of the conventional elliptical cylinder (one rotation two stroke, see Fig. 3).

On the other hand, in the case of applying the involute-type cylinder as shown in the embodiment of the present invention shown in Figure 6 as shown in Figure 9 can increase the compression stroke compared to the suction stroke, and thus the effect of reducing the required power (HP) Can be seen.

In addition, as one side of the outer circumferential surface of the rotor 600 is in continuous contact with one side of the inner circumferential surface of the cylinder 200, the pressure difference between the compression chambers 230 may be reduced to reduce the loss due to internal leakage, and the consumption power may be reduced. Compression efficiency is improved.

The vane 700 is hinged to one side of the outer circumferential surface of the rotor 600 to form a cantilever beam. In this case, the vane 700 includes a hinge portion 710 hinged to one side of the outer circumferential surface of the rotor 600, and a wing portion 720 extending from the hinge portion 710.

Here, the hinge portion 710 of the vane 700 is hinged to one side of the outer peripheral surface of the rotor 600, for example, the insertion groove 620 is formed on one side of the outer peripheral surface of the rotor 600, the insertion groove ( The hinge portion 710 may be rotatably inserted into the 620. At this time, when the hinge portion 710 is inserted into the insertion groove 620, it is preferable to prevent the departure in the radial direction of the rotor 600.

The vane 700 of the vane 700 extends to one side from the hinge portion 710, and the outer surface of the wing portion 720 facing the inner circumferential surface of the cylinder 200 corresponds to the outer circumferential surface shape of the rotor 600. It is preferable that it is formed with the curvature which becomes.

This is to allow the outer surface of the vane 700 to contact the inner circumferential surface of the cylinder 200 at a point where the outer circumferential surface of the rotor 600 and the inner circumferential surface of the cylinder 200 are in contact with each other. On the outer circumferential surface of the 600, a plurality of receiving grooves 630 for accommodating the wing portion 720 of the vanes 700 are formed in the circumferential direction corresponding to the number of vanes 700.

At this time, the receiving groove 630, when the wing portion 720 of the vane 700 is completely accommodated in the receiving groove 630, the outer surface of the wing portion 720 and the outer peripheral surface of the rotor 600 is the same curved surface It is preferable to form to achieve. That is, the bottom shape of the receiving groove 630 corresponds to the inner surface shape of the wing portion 720, and the depth of the receiving groove 630 preferably corresponds to the thickness of the wing portion 720.

In this case, the vane 700 of the cantilever shape is completely accommodated in the receiving groove 630 of the rotor 600 at the end of the compression, thereby maximizing the volume change of the compression chamber 230, thereby improving the compression ratio, thereby improving the same package. In the case of the configuration, the capacity of the compressor is increased by the volume of the accommodating grooves 630 than the example of the conventional linear vane, and when configured in the same capacity, there is an advantage that can reduce the overall package than the conventional example. .

The vane 700 is hinged 710 is rotatably coupled to one side of the outer circumferential surface of the rotor 600, by the centrifugal force generated during the rotation of the rotor 600 and the pressure of the refrigerant trapped in the compression chamber 230, The wing portion 720 is rotated to the outside of the rotor 600 around the hinge portion 710 to be deployed.

Therefore, unlike the example in which the conventional linear vanes are applied, the rotor 600 does not need a separate back pressure chamber for pushing the vanes 700 in the direction of the inner circumferential surface of the cylinder 200 on one side of the rotor 600. The overall package can be reduced by reducing the outer diameter.

In addition, it is also possible to avoid the problem that the torque of the compressor rotating shaft is increased while excessive force is concentrated at the point where the tip of the vane is in contact with the inner circumferential surface of the cylinder due to the high pressure of the conventional back pressure chamber. That is, as can be seen in Figure 10, compared to the conventional linear vanes, when the cantilever vanes according to an embodiment of the present invention is applied, the rotation shaft torque of the compressor appears even lower.

In addition, since it is not necessary to supply oil to the back pressure chamber to push the vanes, it is possible to reduce the cost by reducing the oil injection amount of the compressor, and to reduce the circulation amount of oil that hinders the heat exchanger performance, thereby improving the performance of the entire air conditioning system. Is improved.

In addition, since the volume change rate increases in the process of unfolding the cantilever-shaped vane 700, the pressure change is increased when the refrigerant is inhaled, and the flow velocity of the fluid is increased. It is more effective to increase the capacity and performance of the compressor.

On the other hand, the tip of the wing portion 720 of the unfolded vanes 700 is tightly supported by the inner circumferential surface of the cylinder 200 to seal the compression chamber 230, and along the inner circumferential surface of the cylinder 200 with the rotation of the rotor 600. Move.

At this time, as the inner circumferential surface of the cylinder 200 is formed in the involute curve, the gap between the inner circumferential surface of the cylinder 200 and the outer circumferential surface of the rotor 600 is narrowed toward the discharge port 220 in the inlet port 210, and the vane The wing portion 720 of the 700 is folded while the unfolded angle gradually decreases, and the outer surface of the wing portion 720 closely supported on the inner circumferential surface of the cylinder 200 forms a curved surface, so that the cylinder 200 and the vanes ( Air tightness by 700) is improved.

Thereafter, the vane 700 of the vane 700 is completely folded in the receiving groove 630 of the rotor 600 at the point where the outer circumferential surface of the rotor 600 and the inner circumferential surface of the cylinder 200 come into contact with each other, and the vane 700 is accommodated. The outer surface of the contact with the inner peripheral surface of the cylinder 200.

At this time, the wing portion 720 is preferably formed to extend in the direction in which the rotor 600 rotates for the compression of the refrigerant, in this case, between the two compression chambers 230 adjacent to one side of the vane 700 It is possible to prevent the leakage of the refrigerant in the compression chamber 230 by using the pressure difference.

Referring to the example illustrated in FIG. 6, the first compression chamber 231 close to the suction port 210 and the agent close to the discharge port 220 relatively far from the suction port 210 along the rotation direction of the rotor 600. The two compression chambers 232 are adjacent to both sides of the reference vane 700a, respectively.

In more detail, the inner surface of the wing portion 720 of the reference vane 700a is in contact with the second compression chamber 232, and the outer surface of the wing portion 720 of the reference vane 700a is the first compression chamber 231. ).

At this time, since the second compression chamber 232 has a greater compression stroke than the first compression chamber 231, the pressure acting on the inside of the second compression chamber 232 by the refrigerant is the first compression chamber 231. Greater than the pressure acting inside.

That is, on the inner surface of the wing portion 720 of the reference vane 700a in contact with the second compression chamber 232, compared to the outer surface of the wing portion 720 of the reference vane 700a in contact with the first compression chamber 231. Greater pressure acts.

Due to this pressure difference, the wing portion 720 of the reference vane 700a receives a force in the direction of the inner circumferential surface of the cylinder 200, and the front end portion of the wing portion 720 continues to be supported by the inner circumferential surface of the cylinder 200. Will be maintained.

Therefore, even when an air conditioning system such as an air conditioner of an automobile is in an idle state (low RPM, high pressure), the wing portion of the vane 700 is affected by the pressure difference of the refrigerant filled in each of the compression chambers 230. 720 maintains a state in close contact with the inner circumferential surface of the cylinder 200, thereby preventing the leakage of the refrigerant and chattering noise, such as a blow sound due to the deployment of the vane 700 at startup.

Meanwhile, one side of the outer circumferential surface of the cylinder 200 is recessed to form a discharge part 240 through which compressed high-pressure refrigerant is discharged, and one side of the discharge part 240 communicates with the compression chamber 230. ) Is formed through, and a guide flow path 250 for guiding the high-pressure refrigerant in the discharge port 322 direction is formed at the other side of the discharge part 240.

At this time, the muffler space 340 for reducing the pulsation and discharge noise of the refrigerant is formed on one side of the guide flow path 250, the muffler space 340 is formed by protruding one side of the outer peripheral surface of the cylinder portion 310 to the outside. In one side of the muffler space 340, a discharge hole 341 communicating with the discharge port 322 is formed therethrough.

Therefore, the high-pressure refrigerant discharged to the discharge part 240 through the discharge port 220 enters the muffler space 340 along the guide flow path 250 to reduce pulsation and noise, and then discharges through the discharge hole 341. It will flow in the direction of the port 322.

The high pressure refrigerant passing through the discharge hole 341 is rotated along the outer circumferential surface of the oil separation pipe 324 installed in the discharge port 322, and the oil contained in the refrigerant is separated into the lower part of the oil separation pipe 324. The separated oil is stored in the first oil room 331 which protrudes outward from the outer circumferential surface of the cylinder part 310 of the front housing 300.

At this time, a second oil room 332 communicating with the first oil room 331 is formed on one side of the first oil room 331, and the outer circumferential surface of the cylinder 200 below the first oil room 331 has a predetermined shape. It is recessed to form a second oil room 332.

In addition, a third oil room 333 and a fourth oil room 334 are formed below the second oil room 332, and the third oil room 333 and the fourth oil room 334 may have a front housing ( Spaced apart from each other at the lower end of the cylinder portion 310 of 300 is formed to protrude in the outer direction of the outer peripheral surface, respectively.

At this time, a recessed area is formed on the outer circumferential surface of the cylinder 200 facing the third oil room 333 and the fourth oil room 334, and the third oil room 333 and the fourth oil room 334 are the same. It is in communication with each other through the recessed areas.

In addition, the third oil room 333 communicates through a gap between the outer circumferential surface of the cylinder 200 and the inner circumferential surface of the cylinder portion 310 of the front housing 300, so that the oil stored in the first oil room 331 may be transferred to the second oil room 331. The oil room 332 flows to the third oil room 333 and the fourth oil room 334.

Here, the discharge part 240, the guide flow path 250 and the muffler space 340 forms a high pressure chamber in which a high-pressure refrigerant flows in the vane rotary compressor 100, which is one side of the cylinder portion 310, It is formed on one side of the space between the cylinder portion 310 and the cylinder 200.

In addition, each of the oil chambers 331 ˜ 334, which are relatively low pressure, is formed at the other side of the space between the cylinder part 310 and the cylinder 200, wherein the high pressure chamber and the oil rooms 331 ˜ 334 are cylinders 200. The outer circumferential surface and the inner circumferential surface of the cylinder portion 310 is separated by a close contact surface 260.

That is, in the vane rotary compressor 100 according to the exemplary embodiment of the present invention, the oil room, which is formed in the rear housing 13 (see FIG. 1), is formed in the cylinder part 310 of the front housing 300 together with the high pressure chamber. As a result, the package can be compactly configured. In this case, the upper side of the space between the cylinder part 310 and the cylinder 200 of the front housing 300 is utilized as a high pressure chamber, and the cylinder part 310 and the cylinder 200 are generally used. The lower side of the space between the) is utilized as the oil room (331 ~ 334).

7 is a perspective view of the vane rotary compressor according to an embodiment of the present invention viewed from the rear.

The rear housing 400 according to an embodiment of the present invention is coupled to the rear of the front housing 300 to close the space portion at the axial rear of the cylinder portion 310.

At this time, in the center of the outer surface of the rear housing 400, the shaft accommodating portion 410, which is rotatably inserted into the rear end of the rotating shaft 500, is formed to protrude outward.

Meanwhile, the oil stored in the fourth oil room 334 is guided to the shaft accommodating part 410 to lubricate the rotor 600 and the vane 700 together with the rotating shaft 500. An oil passage 420 communicating with the oil room 334 and communicating with the shaft receiving portion 410 is formed at one side of the shaft receiving portion 410 of the rear housing 400.

Accordingly, the oil introduced into the shaft accommodating portion 410 through the oil passage 420 flows in the rear direction of the rotor 600 along the outer circumferential surface of the rotating shaft 500, and thus, the rotation of the rotor 600 is prevented. By lubricating the sliding surface of the rotor 600 and the rear housing 400 while spreading radially outward.

At this time, the oil flows in the front direction of the rotor 600 through the rotor flow path 610 to lubricate the sliding surfaces of the rotor 600 and the front housing 300, the insertion groove 620 and the receiving groove 630. In the process of flowing through the vane 700 is also made of lubrication.

In the case of a conventional linear vane compressor, in order to supply high pressure oil to the back pressure chamber that pushes the vane, a cover (6, 7 and FIG. 1) having a separate oil supply passage had to be disposed in the front and rear direction of the cylinder. As a result, the overall length of the compressor was inevitably lengthened.

However, in the case of the vane rotary compressor 100 according to an embodiment of the present invention, since the low pressure oil passage 420 for lubrication of the vane 700 is sufficient as described above, the compressor can be miniaturized. There is.

According to the vane rotary compressor according to a preferred embodiment of the present invention, the vane of the cantilever shape is completely accommodated on the outer circumferential surface of the rotor at the end of compression, thereby maximizing the compression chamber volume, thereby improving the compression ratio.

In addition, since the receiving groove of the cantilever vanes is present in the compression chamber, the compressor has an effect of increasing the capacity of the compressor by the volume of the receiving groove for accommodating the cantilever vanes than the conventional example in which the linear vanes are applied. In the case of configuring the same capacity, it is possible to reduce the package than conventional.

In addition, in the process of unfolding the cantilever-shaped vanes, the volume change rate during the suction of the refrigerant increases, so that the pressure change is increased and the flow velocity of the fluid is increased, thereby increasing the capacity and performance of the compressor.

In addition, by forming the inner circumferential surface of the cylinder in the form of an involute curve, it is possible to reduce the required power (HP) by increasing the compression stroke compared to the suction stroke, and there is an effect of reducing the internal leakage due to the pressure difference between the compression chambers. In addition, there is an effect of improving the compressor performance coefficient (COP) according to the optimization of suction stroke and compression stroke.

In addition, since the cantilever-shaped vane maintains its tip portion in close contact with the inner circumferential surface of the cylinder due to the pressure difference between the centrifugal force and the compression chamber, it is possible to solve the problem of chattering noise caused by the vane hitting.

In addition, since the conventional back pressure chamber is not formed in the rotor, the excessive pressure is concentrated at the contact point of the vane and the cylinder due to the high pressure of the back pressure chamber, thereby solving the problem of increasing the torque of the compressor rotating shaft, and the outer diameter of the rotor. To reduce the overall package size.

In addition, since it is not necessary to supply oil to the back pressure chamber to push the vanes, it is possible to reduce the cost by reducing the oil injection amount of the compressor, and to reduce the circulation amount of oil that hinders the heat exchanger performance, thereby improving the performance of the entire air conditioning system. There is an effect to be improved.

Claims (9)

1. A hollow cylinder 200 whose inner circumferential surface has an involute curve in the circumferential direction;

   A space part formed therein so that the cylinder 200 is installed, and a front housing 300 in which a rear of the space part is opened;

   A rear housing 400 coupled to a rear end of the front housing 300 to close the space part;

   A rotor (600) installed in the cylinder (200) and receiving and rotating the power of a driving source from the rotating shaft (500);

   A vane rotary compressor having one end hinged to an outer circumferential surface of the rotor 600 and a vane 700 having the other end contacting the inner circumferential surface of the cylinder 200 according to the rotation of the rotor 600.
2. The method according to claim 1,

   The vane 700 is a vane rotary compressor, characterized in that provided with a plurality of spaced apart from each other in the circumferential direction of the rotor (600).
3. The method according to claim 1,

   The outer surface of the vane 700 is a vane rotary compressor, characterized in that formed with a curvature corresponding to the outer peripheral surface of the rotor (600).
4. The method according to claim 3,

   An outer circumferential surface of the rotor 600 is formed with an accommodating groove 630 for accommodating the vane 700. When the vane 700 is accommodated in the accommodating groove 630, an outer surface of the vane 700 is formed. The vane rotary compressor, characterized in that the outer peripheral surface of the rotor 300 forms the circumferential surface of the same curvature.
5. The method according to claim 1,

   A vane rotary compressor, characterized in that the first oil room (331) is formed by protruding outward one side of the outer circumferential surface of the front housing (300).
6. The method according to claim 1,

   One side of the outer peripheral surface of the cylinder 200 is recessed vane rotary compressor, characterized in that the second oil room (332) is formed.
7. The method according to claim 1,

   The vane rotary compressor, characterized in that the lower end of the cylinder portion 310 of the front housing 300 is protruded to the outside and the third oil room 333 and the fourth oil room 334 are spaced apart from each other.
8. The method according to claim 7,

   The vane rotary compressor, characterized in that the oil passage 420 for guiding the flow of oil from one side of the fourth oil room 334 to the rear end of the rotary shaft 500 is formed on one side of the rear housing 400. .
9. The method according to claim 8,

   The front and rear sides of the rotor 600 are respectively in contact with the front housing 300 and the rear housing 400, a plurality of rotor flow path 610 is formed through the axial direction, through the oil flow path 420 A vane rotary compressor, characterized in that the supplied oil lubricates the rear sliding surface of the rotor (600) and the front sliding surface of the rotor (600) through the rotor flow path (610).

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