KR100531288B1 - Rotary compressor - Google Patents

Abstract

The present invention discloses a rotary compressor in which the drive shaft for rotating the roller can rotate both clockwise or counterclockwise and can provide two different capacities. The rotary compressor may include: a compression chamber having a suction port provided at an upper side, and discharge ports provided at a lower side, respectively, for discharging the compressed fluid at a predetermined pressure or more; A rolling member which is eccentric from the center of the compression chamber and compresses a part of the compression chamber while selectively rolling in both directions while rolling along the wall surface of the compression chamber; And a partition member positioned between the discharge ports and partitioning the compression chamber into two independent spaces by maintaining contact with the rolling member at all times.

Description

Rotary compressor

The present invention relates to a compressor, and more particularly to a rotary compressor capable of forward / reverse rotation;

In general, a compressor is a machine that increases the pressure of a working fluid by receiving power from a power generator such as an electric motor or a turbine and applying a compression work to air, a refrigerant, or other special gases. Such compressors are widely used in general household appliances such as the air conditioner field and the refrigerator field to the plant industry.

Such compressors are classified into positive displacement compressors and dynamic compressors or turbo compressors according to the compression method.

Among them, a widely used industrial compressor is a volumetric compressor, which has a compression method of increasing pressure through volume reduction. The volumetric compressor is further classified into a reciprocating compressor and a rotary compressor.

The reciprocating compressor compresses the working fluid by a linear reciprocating piston inside the cylinder, and has an advantage of producing a high compression efficiency with a relatively simple mechanical element. On the other hand, the reciprocating compressor has a limitation in the rotational speed due to the inertia of the piston, there is a disadvantage that significant vibration occurs due to the inertia force.

The rotary compressor compresses the working fluid by a roller revolving with the eccentric inside the cylinder, and can produce a high compression efficiency at a low speed compared to the reciprocating compressor. Therefore, the rotary compressor has an advantage of generating less vibration and noise.

However, the conventional rotary compressors have the advantages described above, but due to structural limitations it was not possible for the rollers to revolve in both directions. That is, the conventional rotary compressor is formed with one suction port and one discharge port communicating with the cylinder, and the roller compresses the working fluid while rolling along the inner circumferential surface of the cylinder from the suction port side to the discharge port side. Therefore, when the roller rolls in the opposite direction (from the discharge port side to the suction port side), compression of the working fluid is inevitably impossible.

In addition, the conventional rotary compressor was unable to vary the compression capacity due to the above-described structure. Recently, compressors capable of varying the compression capacity have emerged to cope with various operating conditions such as air conditioners. However, since the conventional rotary compressor has only one compression capacity, its application range has to be considerably narrow.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a rotary compressor capable of compression while being rotated forward and reverse.

Another object of the present invention is to provide a rotary compressor capable of varying the compression capacity.

It is yet another object of the present invention to provide a rotary compressor capable of preventing the accumulation of lubricating oil flowing into the cylinder with the fluid on the suction line of the fluid.

The present invention for achieving the above object, the compression chamber having a suction port provided on the upper side and two discharge ports provided on the lower side for discharging the compressed fluid at a predetermined pressure or more; A rolling member which is eccentric from the center of the compression chamber and compresses a part of the compression chamber while selectively rolling in both directions while rolling along the wall surface of the compression chamber; And a partition member positioned between the discharge ports and partitioning the compression chamber into two independent spaces by maintaining contact with the rolling member at all times.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention in which the above objects can be specifically realized are described with reference to the accompanying drawings. In describing the present embodiment, the same name and the same reference numerals are used for the same configuration and additional description thereof will be omitted below.

1 is a partial longitudinal cross-sectional view showing an embodiment of a rotary compressor according to the present invention. 2 is an exploded perspective view illustrating an embodiment of a compression unit in the compressor of FIG. 1, and FIG. 3 is a longitudinal cross-sectional view of an embodiment of the compression unit in the compressor of FIG. 1. An embodiment of a rotary compressor according to the present invention will be described in detail with reference to the drawings.

First, as shown in FIG. 1, the rotary compressor according to the present invention includes a case 1 and a power generating unit 10 and a compression unit 20 located inside the case 1. In FIG. 1, the power generator 10 is located at the top of the compressor, and the compression unit 20 is located at the bottom of the compressor, but their positions may be interchanged as necessary. The upper cap 3 and the lower cap 5 are respectively installed on the upper and lower portions of the case 1 to form a sealed inner space. A suction pipe 7 for sucking the working fluid is installed on one side of the case 1 and is connected to an accumulator 8 for separating the lubricant oil from the refrigerant. In addition, a discharge tube 9 through which compressed fluid is discharged is installed at the center of the upper cap 3. In addition, the lower cap 5 is filled with a certain amount of lubricant (O) for lubrication and cooling of the frictional member.

The power generator 10 includes a stator 11 fixed to the case 1, a rotor 12 rotatably supported inside the stator 11, and a driving shaft press-fitted into the rotor 12. (13). The rotor 12 rotates by electromagnetic force, and the drive shaft 13 transmits the rotational force of the rotor 12 to the compression unit 20. Here, the end of the drive shaft 13 is locked to the lubricating oil O. In order to supply external power to the stator 20, a terminal 4 is installed in the upper cap 3.

The compression unit 20 has a cylinder 21 fixed to the case 1 largely, a roller 22 positioned inside the cylinder 21, and upper and lower portions respectively installed at upper and lower portions of the cylinder 21. It consists of bearings 24 and 25. This compression unit 20 will be described in more detail with reference to FIGS. 2, 3 and 4 as follows.

The cylinder 21 has an internal volume of a predetermined size and has sufficient strength to withstand the pressure of the fluid to be compressed. The cylinder 21 also houses an eccentric 13a formed in the drive shaft 13 in the inner volume. The eccentric portion 13a is a kind of eccentric cam, and has a center spaced apart from the rotation center of the drive shaft 13 by a predetermined distance. The cylinder 21 is formed with a groove 21b extending to a predetermined depth from its inner circumferential surface. The grooves 21b are provided with vanes 23 to be described later. The groove 21b has a length sufficient to fully receive the vane 23.

The roller 22 is a ring member having an outer diameter smaller than the inner diameter of the cylinder 21. As shown in FIG. 4, the roller 22 is in contact with the inner circumferential surface of the cylinder 21 and rotatably coupled to the eccentric portion 13a. Therefore, the roller 22 rotates on the inner circumferential surface of the cylinder 21 while rotating on the outer circumferential surface of the eccentric portion 13a when the drive shaft 13 rotates. In addition, during the rolling motion, the roller 22 is simultaneously spaced apart by a predetermined distance by the eccentric portion 13a about the center of rotation, that is, the center of the cylinder 21. Since the outer circumferential surface of the roller 22 is always in contact with the inner circumferential surface of the cylinder by the eccentric portion 13a, the outer circumferential surface and the inner circumferential surface of the roller 22 form a separate fluid chamber 29 in the inner volume. This fluid chamber 29 is used for suction and compression of fluid in a rotary compressor.

The vanes 23 are installed in the grooves 21b of the cylinder 21 as mentioned above. In addition, an elastic member 23a is installed in the groove 21b to elastically support the vane 23, and the vane 23 continuously contacts the roller 22. That is, one end of the elastic member 23a is fixed to the cylinder 21 and the other end is coupled to the vane 23 to push the vane 23 toward the roller 22. Thus, the vane 23 divides the fluid chamber 29 into two independent spaces 29a and 29b as shown in FIGS. 3 and 4. During the rotation of the drive shaft 13, ie the idle of the roller 22, the sizes of the spaces 29a and 29b vary but are complementary. That is, when the roller 22 rotates in the clockwise direction, one space 29a gradually decreases while the other space 29b gradually increases. However, the sum of the spaces 29a and 29b is always constant and generally coincides with the size of the predetermined fluid chamber 29. These spaces 29a and 29b relatively act as suction chambers for sucking the fluid and compression chambers for compressing the fluid in either of the rotational directions of the drive shaft (ie, clockwise or counterclockwise), respectively. Accordingly, as described above, as the roller 22 rotates, the compression chamber of the spaces 29a and 29b gradually shrinks to compress the previously sucked fluid, and the suction chamber gradually expands to relatively suck the fluid. . If the rotation direction of the roller 22 is reversed, the functions of the respective spaces 29a and 29b are also changed. That is, when the roller 22 revolves counterclockwise, the right space 29b of the roller 22 becomes the compression chamber, and when the roller 22 revolves clockwise, the left space 29a is the compression chamber. Becomes

As shown in FIG. 2, the upper bearing 24 and the lower bearing 25 are respectively installed on upper and lower portions of the cylinder 21, and sleeves 24c and 25c are formed therein and through holes 24b formed therein. The drive shaft 13 is rotatably supported by using 25b). More specifically, the upper and lower bearings 24 and 25 and the cylinder 21 include a plurality of fastening holes 24a, 25a and 21a formed to correspond to each other. The cylinder 21 and the upper and lower bearings 24 and 25 are firmly fastened to each other so that the cylinder internal volume, in particular the fluid chamber 29, is sealed using fastening members such as bolts and nuts.

The upper bearing 24 is provided with a suction passage 24d in communication with the suction pipe 7. In addition, a suction port 26 for communicating the fluid chamber 29 with the suction passage 24d is formed. The suction port 26 serves to guide the fluid to be compressed to the fluid chamber 29. On the other hand, the suction passage 24d is formed as a hole passing through the upper bearing 24 as shown in Figs. However, the suction passage 24d is not limited to the hole shown. For example, the suction passage 24d may be provided in the form of a tube connecting the suction port 26 and the suction tube 7 to each other.

On the other hand, the suction passage 24d may directly connect the suction pipe 7 and the suction port 26, but indirectly through the plenum 40 as shown in FIGS. 2 and 3. It is preferable to communicate. The plenum 40 has a large storage space 41 therein to temporarily store the fluid introduced through the suction pipe 7 therein, and as shown in FIG. It is installed to cover the upper part. The plenum 40 is in direct communication with the suction port 26 to supply fluid. The plenum 40 may be directly fixed to the upper bearing 24 by welding, and may be fastened together with the cylinder 21 and the upper and lower bearings 24 and 25 by using a fastening member. The plenum 40 thus comprises a hole 42 for the sleeve 24c. The volume of the plenum 40 is preferably 100% -400% of the volume of the fluid chamber 29 in order to stably supply the fluid. The plenum 40 is also connected to the suction tube 7 for storing fluid. More specifically, the plenum 40 is connected to the suction pipe 7 through a predetermined suction passage 24d. In this case, the suction passage 24d may be formed through the upper bearing 24.

When the plenum 40 is installed as described above, the suction passage 24d communicates with the storage space 41 formed by the top surface of the plenum 40 and the upper bearing 24, and the fluid chamber 29 Is communicated with the plenum 40 by the suction port 26. Here, the suction port 26 penetrates the upper bearing 24 up and down to connect the fluid chamber 29 and the plenum 40, for example, the fluid chamber 29 and the plenum 40 It vertically penetrates the upper bearing 24 so as to be connected at the shortest distance. The plenum 40 forms a space for always storing a certain amount of fluid to buffer the pressure change of the suction fluid and to stably supply the fluid to the suction port 26. This may assist or replace the accumulator 8.

Discharge ports 27a and 27b are formed in the lower bearing 25. The discharge ports 27a and 27b are in communication with the fluid chamber 29 so that the compressed fluid can be discharged. The discharge ports 27a and 27b may be in direct communication with the fluid chamber 29 and on the other hand, through a flow path (not shown) having a predetermined length formed in the cylinder 21 and the lower bearing 25. It may be in communication with the fluid chamber 29. Discharge valves 27c and 27d are installed in the lower bearing 25 to open and close the discharge ports 27a and 27b. The discharge valves 27c and 27d selectively open the discharge ports 27a and 27b only when the pressure in the chamber 29 is higher than or equal to a predetermined pressure. To this end, the discharge valve (27c, 27d), one end is preferably fixed to the discharge port (27a, 27b) near the other end is preferably a freely deformable leaf spring. As shown in FIG. 3, retainers 27e and 27f may be installed on the discharge valves 27c and 27d to limit the amount of deformation so that the valves operate stably. The retainers 27e and 27f are for ensuring stable operation of the discharge valves 27c and 27d. The retainers 27e and 27f are installed to be in contact with the discharge valves 27c and 27d, and the opening degree of the discharge valves 27c and 27d is opened. Restrict In the absence of the retainers 27e and 27f, the discharge valves 27c and 27d may be excessively bent due to high pressure. In this case, reliability of the discharge valves 27c and 27d is lowered.

On the other hand, a lower portion of the lower bearing 25 may be provided with a muffler 30 to reduce the noise generated during the discharge of the compressed fluid. As illustrated in FIG. 3, the muffler 30 is installed under the lower bearing 25 to form a predetermined space between the lower bearing 25 and the muffler 30. When the muffler 30 is installed as described above, the compressed fluid discharged from the fluid chamber 29 through the discharge ports 27a and 27b is expanded in the space part of the muffler 30, thereby reducing noise in the inflatable silencer. Noise is reduced by the same principle as the principle.

The fluid flowing into the muffler 30 after being discharged from the discharge ports 27a and 27b of the lower bearing 25 is discharged into the upper space of the cylinder 21 through the discharge passage 50 as shown in FIG. 3. do. As shown in FIGS. 2 and 3, the discharge flow path 50 is continuously connected by holes 51, 52, and 53 which sequentially pass through the lower bearing 25, the cylinder 21, and the upper bearing 24. Consists of flow passages. When the discharge passage 50 is provided in this way, as shown in FIG. 1, the fluid compressed in the compression unit 20 moves to the space above the compression unit 20, and then discharges through the power generating unit 10. 9) is discharged to the outside of the compressor.

On the other hand, the discharge passage 50 may be made of the holes (51, 52, 53) as shown in Figures 2 and 3, one end is in communication with the muffler (30) as shown in FIG. It may also consist of a discharge pipe 54. The other end of the discharge pipe 54 is in communication with the upper space of the compression section 10, although not shown. On the other hand, in the compressor according to the present invention, although not shown, the muffler 30 may not be provided and the discharge pipe 54 may be configured to be in direct communication with the discharge ports 27a and 27b.

On the other hand, the idle direction of the roller 22 and the position of the suction port 26 is a very important factor in determining the compression capacity in one embodiment of the present invention. Hereinafter, these correlations will be described in detail. 4A is a cross-sectional view showing the interior of a cylinder when the roller rotates counterclockwise in the rotary compressor according to the present invention. In the case of crossing the cylinder 21 as shown in FIG. 4A, the suction port 26 is not actually seen, but the position of the suction port 26 is represented by an imaginary line for convenience of description.

As shown in FIG. 4A, the fluid chamber 29 is divided into two spaces 29a and 29b by a vane 23 and a roller 22, on both sides of the vane 23. The discharge ports 27a and 27b are each located one by one. This is to always compress the gas regardless of the idle direction of the roller 22. That is, no matter which direction the roller 22 revolves, one discharge port 27a or 27b exists between the suction port 26 and the vane 23. At this time, the distance between the vanes 23 and the arbitrary discharge ports 27a and 27b is preferably equal to each other.

Here, any one of the two spaces (29a, 29b) formed by the vanes 23 and the roller 22 during the rotation of the roller 22 is necessarily a discharge portion discharged after the fluid is compressed. At this time, the discharge portion is determined according to the revolution direction of the roller 22. That is, when the roller 22 revolves counterclockwise as shown in FIG. 4A, the right space 29b of the roller 22 becomes a discharge portion, and as shown in FIG. 5A, the roller 22 When it revolves clockwise, the left space 29a becomes a discharge part.

On the other hand, the compression capacity is determined by the volumes of the discharge portions 29a and 29b. Here, if the volumes of the discharge portions 29a and 29b are correctly defined, it is the volume of the space surrounded by the cylinder 21 and the roller 22 from the suction port 26 to the vane 23. Therefore, the compression capacity is determined according to the position of the suction port 26.

For example, when the suction port 26 is located on an imaginary line passing through the vanes 23, that is, about 180 ° with respect to the vanes 23, the fluid chamber 29 is of the same volume. It is divided into two parts having a. Therefore, the compression capacities are the same no matter which direction the roller 22 revolves.

However, when the suction port 26 is located on one side of the virtual line passing through the vanes 23, the compression chamber 29 is divided into two parts having different volumes. That is, as shown in FIG. 4A, the compression chamber 29 has a left space 29a close to the distance from the vane 23 to the suction port 26, and the suction port 26 from the vane 23. The distance to is divided into the far right space 29b. At this time, the spaces 29a and 29b are respectively discharged portions according to the revolving direction of the roller 22. Therefore, the discharge portions are divided into a high pressure discharge portion 29b having a large volume and a low pressure discharge portion 29a having a small volume. Lose. This means that the rotary compressor according to the invention has a double capacity along the idle direction of the roller 22.

At this time, the position of the suction port 26 is determined according to the compression ratio of the high pressure discharge portion 29b and the low pressure discharge portion 29a. As an example, the present invention suggests that the suction port 26 is located in a range between 180 ° and 300 ° clockwise from an imaginary line passing through the vanes 23. In this case, when the compression ratio is 50:50, as described above, the suction port 26 is located on 180 °. In addition, when the compression ratio is 75:25, the suction port 26 is positioned at approximately 270 °.

Hereinafter, the operation of the rotary compressor according to the present invention in detail.

4A to 4D are cross-sectional views sequentially showing the action when the roller rotates counterclockwise in the rotary compressor according to the present invention. FIG. 4A shows the suction start step, FIG. 4B shows the compression and discharge step, FIG. 4C shows the discharge end step, and FIG. 4D shows the vacuum area formed in the compression chamber.

First, the roller 22 revolves counterclockwise while rolling along the inner circumferential surface of the cylinder 21 due to the rotation of the crankshaft 13. During this process, the suction port 26 is opened, and gas is sucked into the compression chamber through the suction port 26. At this time, gas is sucked into the high pressure discharge part 21b by the roller 22. This is as shown in Figure 4A.

Then, as the roller 22 continues to revolve, the gas of the high pressure discharge part 29b is compressed while the volume of the high pressure discharge part 29b is reduced. During this process, the vanes 23 retract elastically back and forth by the spring 23a and the roller 22 to maintain the airtightness of the high pressure discharge part 29b. At the same time, new fluid continues to be sucked through the suction port 26.

After that, when the pressure of the high pressure discharge part 29b becomes higher than or equal to a predetermined pressure, the discharge valve 27d on the side of the high pressure discharge part 29b is opened. Therefore, the fluid of the high pressure discharge part 29b starts to be discharged to the muffler 30 through the discharge port 27b. This is as shown in Figure 4B.

Thereafter, as the roller 22 continues to revolve, all of the fluid of the high pressure discharge part 29b is discharged to the muffler 30 through the discharge port 27b. After all the fluid is discharged through the discharge port 27b, the discharge valve 27d closes the discharge port 27b by its elasticity. This is as shown in Figure 4C.

Thereafter, the roller 22 continues to revolve in the counterclockwise direction, whereby the gas is discharged to the muffler 22 while undergoing suction, compression, and discharge processes as described above.

In the above-described process, the vacuum region V is formed at one side of the fluid chamber 29. As shown in FIG. 4D, after the discharge step is completed, the fluid in the fluid chamber 29 is forcibly moved to the high pressure discharge part 29b by the roller 22 as the roller 22 revolves. Done. On the other hand, a vacuum region V is formed in the area where the roller 22 has passed, that is, the left space 29b partitioned by the vanes 23 and the roller 22. The vacuum region V continues until the roller 22 continues to idle while opening the suction port 26. Therefore, the vacuum region V is formed periodically every time the roller 22 revolves once.

Next, FIGS. 5A to 5D are cross-sectional views sequentially showing the action when the roller rotates clockwise in the rotary compressor according to the present invention. FIG. 5A shows a suction start step, FIG. 5B shows a compression and discharge step, FIG. 5C shows a discharge end step, and FIG. 5D shows a vacuum area formed in the compression chamber.

The roller 22 revolves clockwise while rolling along the inner circumferential surface of the cylinder 21 due to the reverse rotation of the crankshaft 13. During this process, the suction port 26 is opened, and gas is sucked into the fluid chamber 29 through the suction port 26. At this time, the gas is sucked into the low pressure discharge part 29a by the roller 22. This is as shown in Figure 5A.

Next, as the roller 22 continues to revolve, the gas of the low pressure discharge part 29a is compressed while the volume of the low pressure discharge part 29a is reduced. At the same time, new gas continues to be sucked through the suction port 26.

After that, when the pressure of the low pressure discharge part 29a becomes equal to or higher than a predetermined pressure, the discharge valve 27c on the side of the low pressure discharge part 29a is opened. Therefore, the fluid of the low pressure discharge part 29a starts to be discharged to the muffler 30 through the discharge port 27a. This is as shown in Fig. 5B.

Thereafter, as the roller 22 continues to revolve, all of the fluid of the low pressure discharge part 29a is discharged to the muffler 30 through the discharge port 27a. After all the fluid is discharged through the discharge port 27a, the discharge valve 27c closes the discharge port 27a by its elasticity. This is as shown in Figure 5C.

Thereafter, the roller 22 continues to revolve in the clockwise direction, whereby the gas is discharged to the muffler 30 while undergoing suction, compression, and discharge processes as described above.

Similarly, the vacuum region V is formed at one side of the compression chamber during the above-described process. As shown in Fig. 5D, after the discharge step is completed, as the roller 22 revolves, the gas in the compression chamber is forcibly moved to the low pressure discharge part 29b by the roller 2, The vacuum area V is formed in the area where the roller 22 passes. That is, the vacuum region (V) is formed in the right space (29b) partitioned by the vanes 23 and the roller 22, when the roller 22 continues to idle while opening the suction port 26 Lasts until. In this case, the vacuum area V occupies more area for a longer time than when the roller 22 revolves counterclockwise.

Next, as shown in FIG. 1, the compressed gas inside the muffler 140 is discharged into the inner space of the case 1 through the discharge port 141. Subsequently, the compressed gas moves upward through the space between the rotor 30 and the stator 20 or the space between the stator 20 and the case 1. Thereafter, the compressed gas moves to a predetermined destination through the discharge tube 9.

On the other hand, although the rotary compressor according to the present invention has the advantage of varying the compression capacity while the forward / reverse rotation, the following problems are concerned.

As shown in FIGS. 4D and 5D, a vacuum region V is periodically formed in the compression chamber, and the vacuum region V causes a sudden pressure change. That is, when the suction port 26 is opened due to the idle of the roller 22, a significant pressure difference occurs between the vacuum region V and the suction port 26. This pressure change causes some negative effects. First, the pressure change may reduce the efficiency of the compressor. Second, the pressure change acts as a significant load on the crankshaft 13, and as a result, a lot of power can be consumed. Third, the pressure change may generate periodic noise in the suction port 26. In order to overcome this disadvantage, the vacuum area V must be artificially solved. To this end, a structure capable of supplying a fluid to the vacuum region V is required. In particular, in consideration of compression efficiency, the gas is preferably a fluid before compression. Accordingly, an embodiment of the present invention provides a bypass structure capable of supplying the gas of the suction port 26 to the vacuum region (V).

In addition, the bypass structure further has the following features. First, the bypass is a one-way flow path. In other words, the bypass allows only the gas before compression to move into the compression chamber, but not the reverse movement. This is to prevent backflow of compressed gas through the bypass. Secondly, the bypass has a valve member that is opened and closed automatically by a pressure difference. This is because the bypass is a one-way flow path, so a separate valve member for controlling opening and closing is required. Third, the bypass has two one-way flow paths. As described above, the compression chamber is divided into a high pressure discharge part 29b and a low pressure discharge part 29a based on the vanes 23. The high pressure discharge part 29b and the low pressure discharge part 29a each have a vacuum region V in the revolution direction of the roller 22. Therefore, in order to solve the vacuum area V irrespective of the idle direction of the roller 22, any one of the bypasses is connected to the high pressure discharge part 29b, and the other is the low pressure discharge part ( 29a). Fourth, the bypass has a storage member for storing the gas before compression. The bypass is a flow path connecting the suction port 26 and the compression chamber. Therefore, when the bypass is provided, gas can always be supplied to the vacuum region V of the compression chamber.

Hereinafter, an embodiment in which the bypass structure is specified will be described with reference to the accompanying drawings. FIG. 6 is a longitudinal sectional view showing a modification of the compression unit of FIG. 3, showing an embodiment having a simple bypass structure. 6 does not separately show a suction port 26 provided in the upper bearing 24 for convenience of description.

Referring to FIG. 6, bypasses 28a and 28b are provided in the upper bearing 24. The bypasses 28a and 28b are provided to connect the plenum 40 and the fluid chamber 29. More specifically, the bypasses 28a and 28b communicate the plenums 40 and the spaces 29a and 29b of the fluid chamber 29, respectively. The bypasses 28a and 28b provided as described above may be provided to the upper bearing 24 to face the discharge ports 27a and 27b provided to the lower bearing 25, for example.

The bypass valves 28c and 28d are provided in the bypass 28a and 28b. The bypass valves 28c and 28d allow fluid prior to compression to move only from the plenum 40 to the fluid chamber 29 side. The bypass valves 28c and 28d are one type of leaf springs, one end of which is supported on the recess groove of the bypass 28a and 28b and the other end of which is free. Thus, the bypass valves 28c and 28d open and close the bypass by their elasticity. At this time, the bypass valves 28c and 28d open the bypass only when the pressure difference between the bypass and the compression chamber is greater than or equal to a certain level.

On the other hand, retainers 28e and 28f are further installed in the recess grooves. The retainers 28e and 28f ensure stable operation of the bypass valves 28c and 28d. That is, the retainers 28e and 28f are provided in contact with the bypass valves 28c and 28d to limit the opening degree of the bypass valves 28c and 28d.

On the other hand, although not shown, the bypass may consist of holes penetrating the upper bearing 24 and the cylinder 21 to allow the fluid passage 29d or the plenum 40 to communicate with the fluid chamber 29. There will be. In this case, for example, one end of the hole may be in communication with the side wall of the cylinder 21, and the other end of the hole may be connected to the plenum 40 or the suction passage 24d. If the bypass is thus provided, the fluid in the suction flow path 24d or plenum 40 may be supplied into the fluid chamber 29 through the side wall of the cylinder 21 after passing through the hole. It is possible to perform the same function as the embodiment shown in.

A process of eliminating the vacuum region in the rotary compressor having the bypass structure will be described below. While the roller 22 rotates counterclockwise, the fluid in the high pressure discharge part 29b is discharged through the discharge port 27b. If the roller 22 continues to rotate after the ejection is completed as shown in Fig. 4C, a vacuum region is formed between the roller 22 and the vane 23 as shown in Fig. 4D. As the roller 22 continues to rotate, the size of the vacuum area becomes larger. Then, the bypass valve 28c is opened by the pressure difference because the pressure difference between the vacuum region and the plenum 40 increases with respect to the bypass valve 28c. When the bypass valve 28c is opened, the fluid before compression in the plenum 40 is supplied to the space 29a in the fluid chamber 29 through the bypass 28a, thereby eliminating the vacuum region. On the other hand, when the roller 22 rotates clockwise, the fluid before compression in the plenum 40 is supplied to the space 29b of the fluid chamber 29 through the bypass 28b in the same manner as described above. The vacuum area is effectively resolved.

On the other hand, Figure 7 is an exploded perspective view showing another embodiment of the compression unit in the rotary compressor according to the present invention, Figure 8 is a cross-sectional view showing the compression unit in the compressor of Figure 7, Figure 9 shows the inside of the cylinder in the compressor of Figure 7 Cross section view. As shown in the drawings, the present invention may be implemented in another embodiment in which the compression unit is configured differently from the embodiment described with reference to FIGS. 2 to 6. Hereinafter, another embodiment of the present invention will be described in more detail with reference to the accompanying drawings.

Compressor according to another embodiment of the present invention comprises a case, a power generating unit and a compression unit located inside the case. The configuration of the case and the power generation unit is the same as the embodiment described with reference to FIGS. 1 to 6, and thus description thereof will be omitted. As shown in FIG. 7, the upper and lower bearings are respectively installed at upper and lower portions of the cylinder 21 fixed to the case, the roller 22 positioned inside the cylinder 21, and the cylinder 21, respectively. It consists of (24,25). The compression unit includes a valve assembly 60 installed between the lower bearing 24 and the cylinder 21. In addition, the plenum 40 provided above the upper bearing 24, and the muffler 30 provided below the lower bearing 25 further includes. Hereinafter, the parts of the compressor according to another embodiment of the present invention having different configurations from the embodiments described with reference to FIGS. 1 to 6 will be described in more detail with reference to FIGS. 7 to 9.

The upper bearing 24 is formed with suction ports 41a, 41b, 41c in communication with the fluid chamber 29. The suction ports 41a, 41b, and 41c serve to guide the fluid to be compressed to the fluid chamber 29. If a plenum 40 is provided, the suction ports 41a, 41b, 41c are all in communication with the plenum 40. Discharge ports 27a and 27b are formed in the lower bearing 25. The discharge ports 27a and 27b communicate with the fluid chamber 29 to discharge the compressed fluid.

These suction and discharge ports 41a, 41b, 41c, 27a, 27b are important factors in determining the compression capacity of the rotary compressor and will be described in more detail below with reference to FIGS. 9 to 10B. 9 shows the cylinder 21 coupled with the upper bearing 24 without the valve assembly 60 to clearly show the suction ports 41a, 41b, 41c. Although the discharge ports 27a and 27b actually formed in the lower bearing 25 are not shown in FIG. 9, these discharge ports 27a and 27b are shown in phantom in FIG. 9 for clarity.

First, the compressor of the present invention includes at least two discharge ports 27a and 27b. As shown, even if the roller 22 revolves in any direction, a discharge port must exist between the suction port and the vane 23 positioned in the revolving path to discharge the compressed fluid. Therefore, one discharge port is required for each rotation direction, which enables the compressor of the present invention to discharge fluid regardless of the revolution direction of the roller 22, that is, the rotation direction of the drive shaft 13. On the other hand, as described above, the compression chamber in which the fluid is compressed in the spaces 29a and 29b becomes smaller and smaller as the roller 22 approaches the vane 23. Accordingly, in order to discharge the compressed fluid as much as possible, the discharge ports 27a and 27b may be formed to face each other near the vanes 23. That is, as shown, the discharge ports 27a and 27b are positioned on the left and right sides of the vanes 23, respectively. Preferably, the discharge ports 27a and 27b are located as close to the vanes 23 as possible.

The suction ports 41a and 41c are suitably positioned so that the fluid can be compressed between the discharge ports 27a and 27b and the roller 22. In practice, in a rotary compressor the fluid is compressed from any one suction port to any discharge port located within the idle path of the roller 22. That is, the relative position of the suction port with respect to the corresponding discharge port determines the compression capacity. Accordingly, two compression capacities can be obtained by using different suction ports 41a and 41c according to the rotation direction. Therefore, the compressor of the present invention has two first and second suction ports 41a and 41c corresponding to the two discharge ports 27a and 27b, respectively, and these suction ports are different from each other with respect to the center O. Spaced at a predetermined angle from each other for two compression capacities.

Preferably the first suction port 41a is located near the vane 23. Accordingly, the roller 22 compresses the fluid from the first suction port 41a to the second discharge port 27b located opposite the vane 23 in one direction rotation (counterclockwise in the drawing). . By this first suction port 41a, the roller 22 compresses using the entire chamber 29, so that the compressor has a maximum compression capacity in the counterclockwise rotation. That is, the refrigerant as much as the entire volume of the chamber 29 is compressed. As shown in FIG. 9, the first suction port 41a is substantially spaced apart from the vane 23 at an angle θ1 of 10 ° in a clockwise or counterclockwise direction. In the drawings of the present invention, the first suction port 41a is shown spaced apart by the angle θ1 in the counterclockwise direction. At this separation angle θ1, the entire fluid chamber 29 may be used for compression without interference with the vanes 23.

The second suction port 41c is spaced apart from the first suction port 41a by a predetermined angle with respect to the center O. The roller 22 compresses the fluid from the second suction port 41c to the first discharge port 27a during clockwise rotation. Since the second suction port 41c is spaced at a considerable angle clockwise from the vane 22, the roller 22 compresses using only a part of the chamber 29 and thus compresses less than the counterclockwise direction. Pay the capacity. That is, as much volume of the refrigerant of the chamber 29 is compressed. Preferably, the second suction port 41c is spaced apart from the vane 23 by an angle θ2 having a range of 90 ° -180 ° in a clockwise or counterclockwise direction. Further, it is more preferable that the second suction port 41c is located opposite the first suction port 41a for the difference in the appropriate compression capacity in each rotation direction and for the mutual interference cancellation.

The suction ports 41a and 41c may have a circular shape as shown in FIG. 9. In addition, the suction ports 41a and 41c may have various shapes, including a rectangle, to increase the suction amount of the fluid. Furthermore, the rectangular suction ports 41a and 41c can have a predetermined curvature, as shown in FIGS. 7 and 10A and 10B, thus allowing other adjacent parts, in particular the roller 22, to be operated during operation. Interference with can be minimized.

On the other hand, in order to obtain the desired compression capacity in each rotation direction, only one suction port valid in any one rotation direction should exist. If there are two suction ports in the rotation path of the roller 22, no compression occurs between these suction ports. In other words, when the first suction port 41a is opened, the second suction port 41c should be closed and vice versa. Therefore, the valve assembly 60 is installed in the compressor of the present invention to selectively open only one of the suction ports 41a and 41c along the idle direction of the roller 22.

As shown in FIGS. 7 and 10A and 10B, the valve assembly 60 is installed between the cylinder 21 and the upper bearing 24 to be adjacent to the suction ports 41a, 41b, 41c. First and second valves 61, 65.

First, as shown in FIG. 7, the first valve 61 is a disc member installed to contact the eccentric portion 13a more precisely than the drive shaft 13. Therefore, when the drive shaft 13 rotates, that is, the roller 22 revolves, the first valve 61 rotates in the same direction. The first valve 61 preferably has a diameter larger than the inner diameter of the cylinder 21, and thus the outer circumferential portion of the first valve 61 is supported to stably rotate by the cylinder 21.

The first valve 61 is a through hole through which the drive shaft 13 and the first and second openings 61a and 61c communicate with the first and second suction ports 41a and 41c, respectively, in a specific rotational direction. (61a). More specifically, the first opening 61a communicates with the first suction port 41a by the rotation of the first valve 61 when the roller 22 rotates in one direction. The second suction port 41c is closed by the body of the first valve 61. The second opening 61c communicates with the second suction port 41c when the roller 22 rotates in the other direction, and the first suction port 41a is connected to the first valve 61. Is closed by the body. The first and second openings 61a and 61c may be circular or polygonal as shown in FIG. 9. In addition, the openings 61a and 61c may have a rectangular shape having a predetermined curvature, as shown in FIG. 7, and thus the sizes of the openings may be expanded to smoothly suck the fluid. If such openings 61a and 61c are formed adjacent to the center of the first valve 61, the possibility of interfering with the roller 22 and the eccentric portion 13a is increased. In addition, the openings 61a and 61c may communicate with the space between the roller 22 and the eccentric portion 13a, so that fluids may leak out along the drive shaft 13. Therefore, in practice, the openings 61a and 61c are preferably located adjacent to the outer circumference of the first valve 61.

On the other hand, by adjusting the rotation angle of the first valve 61, the first opening 61a can open the first and second suction ports 41a, 41c in their respective rotation directions. That is, in one direction of rotation of the drive shaft 13, the first opening 61a communicates with the first suction port 41a while closing the second suction port 41c. As the first suction port 41a is closed, the first opening 61a may communicate with the second suction port 41c. Control of the suction port using this single opening 61a further simplifies the structure of the first valve 61.

On the other hand, the second valve 65 is fixed between the cylinder 21 and the upper bearing 24 to guide the movement of the rotating first valve 61. The second valve 65 is a member in the form of a ring having seats 65b (seat) for rotatably receiving the first valve 61. The second valve 65 also includes a fastening hole 65a to be fastened by a fastening member together with the cylinder 21 and the upper and lower bearings 24 and 25. In addition, the thickness of the second valve 65 is preferably the same as the thickness of the first valve 61 in order to prevent the leakage of fluid and stable support. In addition, since the first valve 61 is partially supported by the cylinder 21, the thickness of the first valve 61 is formed to form a gap for smooth rotation of the second valve 65. It may be slightly smaller than the thickness of the two valves 65.

Meanwhile, referring to FIG. 9, in the clockwise rotation, while the roller 22 revolves from the vane 23 to the second suction port 41c, between the vane 23 and the roller 22. No suction or discharge of fluid occurs. Therefore, the region V becomes a vacuum state. Such a vacuum region (V) brings a power loss of the drive shaft 13 and generates a loud noise. Therefore, the third suction port 41b is formed in the lower bearing 25 to eliminate the vacuum region V. The third suction port 41b is formed between the second suction port 41c and the vane 23 so that the vacuum state is maintained before the roller 22 passes the second suction port 41c. It serves to supply fluid to the space between the roller 22 and the vanes 23 so as not to be formed. The third suction port 41b is preferably formed near the vane 23 so as to quickly eliminate the vacuum state. However, since the third suction port 41b operates in a rotational direction different from that of the first suction port 27a, the third suction port 41b is positioned to face the first suction port 41a. In practice, the third suction port 41b is spaced apart from the vane 23 at an angle θ3 of 10 ° in a clockwise or counterclockwise direction. The third suction port 41b may be circular or curved rectangular like the first and second suction ports 41a and 41c.

Since the third suction port 41b acts together with the second suction port 41c, these suction ports 41b and 41c must be opened at the same time during idle of the roller 22 in either direction. Accordingly, the first valve 61 may further include a third opening configured to communicate with the third suction port 41b at the same time when the second suction port 41c is opened. In the present invention, the third opening may be formed independently. However, since the first and third suction ports 41a and 41b are adjacent to each other, as shown in FIGS. 10A and 10B, the first opening 61a rotates by increasing the rotation angle of the first valve 61. Preferably, both the first and third suction ports 41a and 41b are opened in a direction.

The first valve 61 may open the suction ports 41a, 41b, 41c according to the rotational direction of the roller 22, but the suction ports should be opened correctly in order to obtain a desired compression capacity. And the correct opening of these suction ports can be obtained by controlling the rotation angle of the first valve. Thus the valve assembly 60 preferably further comprises means for controlling the angle of rotation of the first valve 61, which means are described in detail with reference to FIGS. 10A and 10B.

10A and 10B, the restricting means are formed in the projection 62 and the second valve 65 protruding radially from the first valve 61 and move the projection 62. It may also consist of a groove 66 that possibly accommodates. Here, the groove 66 is formed in the second valve 65 and is not exposed to the internal volume of the cylinder 21, so a dead volume, that is, a region in which compression does not occur or cannot be compressed, inside the cylinder 21. Does not form.

Also, although not shown, the restricting means may include a protrusion projecting radially inwardly from the second valve 65 and a groove formed in the first valve 61 and movable to receive the protrusion. It may be implemented in various modified embodiments.

When the limiting means is used as described above, when the drive shaft 13 rotates counterclockwise, the protrusion 62 is caught at one end of the groove 66 as shown in FIG. 10A. Accordingly, the first opening 61a communicates with the first suction port 41a to suck the fluid, and the remaining second and third suction ports 41c and 41b are closed. On the contrary, when the driving shaft 13 rotates in the clockwise direction, as shown in FIG. 10B, the protrusion 62 is caught by the other end of the groove 66, and the first opening 61a and the first opening 61a are formed. The second opening 61c opens the third suction port 41b and the second suction port 41c together to suck the fluid. The first suction port 41a is closed by the first valve 61.

Hereinafter, the operation of the compressor according to another embodiment of the present invention in detail.

11A to 11C are cross-sectional views sequentially showing the action of the roller rotating in the counterclockwise direction in the rotary compressor according to one embodiment of the present invention.

First, in FIG. 11A, the state of each of the parts inside the cylinder is shown when the drive shaft 13 rotates counterclockwise. First, the first suction port 41a communicates with the first opening 61a, and the remaining second suction port 41c and the third suction port 41b are closed. Since the state of the suction ports in the counterclockwise direction has been described with reference to FIG. 10A, the detailed description is omitted.

In the state where the first suction port 41a is open, the roller 22 revolves counterclockwise while rolling along the inner circumferential surface of the cylinder 21 due to the rotation of the drive shaft 13. As the roller 22 continues to revolve, as shown in FIG. 11B, the size of the space 29b is reduced and the fluid already sucked is compressed. During this process, the vane 23 divides the fluid chamber 29 into two spaces 29a and 29b to be hermetically moved up and down elastically by the elastic member 23a. At the same time, new fluid continues to be sucked into the space 29a through the first suction port 41a to be compressed in the next stroke.

When the fluid pressure in the space 29b becomes a predetermined value or more, the second discharge valve 27b is opened. Therefore, as shown in FIG. 11C, the liquid is discharged through the second discharge port 27b. As the roller 22 continues to revolve, all fluid in the space 29b is discharged through the second discharge port 27b. After all of the fluid is discharged, the second discharge valve 27d closes the second discharge port 27b by its elasticity.

After this one stroke is finished, the roller 22 continues to revolve counterclockwise, repeating the same stroke and discharging the fluid. In the counterclockwise stroke, the roller 22 compresses the fluid while revolving from the first suction port 41a to the second discharge port 27b. As described above, since the first suction port 41a and the second discharge port 27b are positioned near the vanes 23 so as to face each other, the volume of the entire fluid chamber 29 during the counterclockwise stroke is used. The fluid is compressed so that a maximum compressive capacity is obtained.

12A to 12C are cross-sectional views sequentially showing the action when the roller rotates clockwise in the rotary compressor according to the present invention.

First, in FIG. 12A, the state of each of the parts inside the cylinder is shown when the drive shaft 13 rotates clockwise. The first suction port 41a is closed and the second suction port 41c and the third suction port 41b communicate with the second opening 61c and the first opening 61a, respectively. If the first valve 61 additionally has a third opening (not shown), the third suction port 41b is in communication with the third opening. Since the state of the suction ports in the clockwise direction has been described with reference to FIG. 10B, the detailed description is omitted.

In the state in which the second and third suction ports 41c and 41b are open, the roller 22 is clocked while rolling along the inner circumferential surface of the cylinder 21 due to the clockwise rotation of the drive shaft 13. Start to rotate in the direction. During this initial stage of idle, the fluids sucked in until the roller 22 reaches the second suction port 41c are not compressed and are removed by the roller 22 as shown in Fig. 12A. 2 is pushed out of the cylinder 21 through the suction port 41c. Accordingly, the fluids begin to compress after the roller 22 passes the second suction port 41c as shown in FIG. 12B. At the same time, the space between the second suction port 41c and the vane 23, that is, the space 29b, becomes a vacuum state. However, as described above, when the idle of the roller 22 is started, the third suction port 41b is opened in communication with the first opening 61a to suck the fluid. Therefore, the vacuum state is eliminated by the sucked fluid, and the generation of noise and power loss are suppressed.

As the roller 22 continues to revolve, the size of the space 29a is reduced and the fluid already sucked is compressed. During this compression process, the vane 23 divides the fluid chamber 29 into two spaces 29a and 29b to be hermetically moved up and down elastically by the elastic member 23a. New fluid is continuously sucked into the space 29b through the second suction port 41c and the third suction port 41b to be compressed in the next stroke.

When the fluid pressure in the space 29a is greater than or equal to a predetermined value, the first discharge valve 27c is opened as shown in FIG. 12C and is discharged through the first discharge port 27a. After all of the fluid is discharged, the first discharge valve 27c closes the first discharge port 27a by its elasticity.

After this one stroke is finished, the roller 22 continues to idle clockwise, repeats the same stroke and discharges the fluid. In the counterclockwise stroke, the roller 22 compresses the fluid while revolving from the second suction port 41c to the first discharge port 27a. Thus, the fluid is compressed using only a portion of the entire fluid chamber 29 during the counterclockwise stroke and a compression capacity less than the clockwise compression capacity is obtained.

In each of the above-described strokes (that is, clockwise and counterclockwise strokes), the compressed fluid discharged through the discharge ports 27a and 27b flows into the muffler 30, and the rotor inside the case 1 through the discharge passage. After moving to the space between the 12 and the stator 11 and the space between the stator 11 and the case 1, it is finally discharged to the outside of the compressor through the discharge pipe (9). Here, various embodiments of the discharge passage are the same as the embodiment described with reference to FIGS. 1 to 6, and thus description thereof is omitted.

Although several embodiments have been described above, it will be apparent to those skilled in the art that the present invention may be embodied in many other forms without departing from the spirit and scope thereof.

Accordingly, the described embodiments are to be considered as illustrative and not restrictive, and all embodiments within the scope of the appended claims and their equivalents are included within the scope of the present invention.

The rotary compressor according to the present invention can compress the fluid in any direction in which the drive shaft rotates and has compression capacities that vary according to the rotational direction of the drive shaft. Furthermore, the rotary compressor of the present invention has an appropriately arranged suction and discharge ports and a simple valve assembly which selectively opens the suction ports in a rotational direction, thereby compressing the fluid using the entire designed fluid chamber. can do. This rotary compressor of the present invention provides the following effects.

First, in the prior art, various devices were combined to realize double capacity compression. For example, two compressors and inverters with different compression capacities were combined for double compression capacities. In this case, the structure is considerably complicated and the unit price has to rise. However, the present invention can realize double capacity compression with only one compressor. In particular, the present invention can realize double capacity compression by changing only minimal components in the conventional rotary compressor.

Second, conventional compressors having a single compression capacity could not produce a compression capacity suitable for various operating conditions such as an air conditioner or a refrigerator. In this case, power consumption was inevitably wasted more than necessary. However, the present invention can produce a suitable compression capacity corresponding to the operating conditions of the device.

Third, the rotary compressor of the present invention uses the entire predesigned fluid chamber in producing the double compression capacity. This means that the compressor of the invention has at least the same compression capacity as a conventional rotary compressor having the same cylinder size, ie the same fluid chamber size. That is, the rotary compressor of the present invention can replace the conventional rotary compressor without changing the design of the basic parts such as the cylinder size. Therefore, the rotary compressor of the present invention can be freely applied to the required system without considering the compression capacity and increasing the production cost.

Fourth, the rotary compressor of the present invention is designed such that a suction port for sucking fluid and a plenum for temporarily storing the fluid introduced through the suction pipe are positioned at the top of the cylinder. Generally, refrigerant and lubricant are introduced into the fluid chamber. If the suction port and the plenum are located at the bottom of the cylinder, the lubricant is difficult to be sucked into the cylinder. This may cause lubrication problems of the cylinder. However, in the rotary compressor of the present invention, since both the suction port and the plenum are located at the upper portion of the cylinder, the problem of lubricating oil accumulation on the plenum can be completely solved, and the lubricant can always be supplied with an appropriate level.

1 is a partial longitudinal sectional view showing one embodiment of a rotary compressor according to the present invention;

Figure 2 is an exploded perspective view showing an embodiment of the compression unit in the compressor of Figure 1;

Figure 3 is a longitudinal sectional view showing an embodiment of the compression unit in the compressor of Figure 1;

4A to 4D are cross-sectional views sequentially showing the interior of a cylinder when the roller rotates counterclockwise in the rotary compressor according to the present invention;

5A to 5D are cross-sectional views sequentially showing the inside of a cylinder when the roller rotates clockwise in the rotary compressor according to the present invention;

6 is a longitudinal sectional view showing a modification of the compression unit of FIG. 3;

7 is an exploded perspective view showing another embodiment of a compression unit in a rotary compressor according to the present invention;

8 is a sectional view showing a compression unit in the compressor of FIG.

9 is a cross-sectional view showing the inside of the cylinder in the compressor of FIG.

10A to 10B are plan views showing one embodiment of the rotation limiting means in the compressor of FIG.

11A-11C are cross-sectional views sequentially illustrating the interior of a cylinder when the roller rotates counterclockwise in the compressor of FIG. And

12A to 12C are cross-sectional views sequentially showing the inside of the cylinder when the roller rotates clockwise in the compressor of FIG.

Explanation of symbols on the main parts of the drawings

10: power generating unit 13: drive shaft

13a: eccentric 20: compression

21: cylinder 22: roller

23: vane 24: upper bearing

25: lower bearing 26, 41a, 41b, 41c: suction port

27a, 27b: discharge port 29: fluid chamber

30: muffler 40: plenum

50: discharge passage 60: valve assembly

61: first valve 65: second valve

Claims (55)

A compression chamber having a plurality of suction ports provided at an upper side, and a plurality of discharge ports provided at a lower side, respectively, for discharging the compressed fluid at a predetermined pressure or more; A rolling member which is eccentric from the center of the compression chamber and compresses a part of the compression chamber while selectively rolling in both directions while rolling along the wall surface of the compression chamber; A partition member positioned between the discharge ports and partitioning the compression chamber into two independent spaces by always keeping contact with the rolling member; And And a valve assembly for selectively opening and closing the suction ports in accordance with an idle direction of the rolling member. The method of claim 1, The discharge ports are provided to be spaced apart at equal intervals based on the partition member. The method of claim 1, And each of the discharge ports is provided with an opening / closing member which opens the respective discharge ports when the pressure of the discharge portion is equal to or greater than a predetermined pressure. The method of claim 1, And a member in direct communication with the suction port and forming a wide space filled with the fluid to be supplied to the cylinder. The method of claim 4, wherein And a suction passage for supplying a fluid before compression is connected to the member. The method of claim 1, And a discharge passage connected to the discharge port and guiding the compressed fluid discharged from the discharge port to the outside of the compression chamber. The method of claim 1, And a noise reduction means provided under the compression chamber so as to communicate with the discharge port, and reducing noise by expanding the compressed fluid discharged from the discharge port. The method of claim 1, The suction port is located on any one side of the virtual line passing through the partition member. The method of claim 8, The suction port is located in the range of 180 ° ~ 300 ° in any direction with respect to the partition member. The method of claim 1, The suction port is located on the virtual line passing through the partition member. A drive shaft having an eccentric portion and rotatable in a forward / reverse direction; A cylinder accommodating the eccentric portion therein and forming a compression chamber; An upper bearing which closes the open upper part of the cylinder, rotatably supports the drive shaft, and has a plurality of suction ports in communication with the cylinder; A lower bearing which closes the open lower part of the cylinder, rotatably supports the drive shaft, and has a plurality of discharge ports in communication with the cylinder; A valve assembly selectively opening the suction ports in accordance with a rotational direction of the drive shaft; A discharge valve which opens the discharge port when the pressure in the compression chamber is equal to or greater than a predetermined pressure; A roller rotatably installed in the eccentric to perform rolling motion along the inner circumferential surface of the cylinder; And And a vane elastically installed in the cylinder so as to be positioned between the discharge ports, and partitioning the compression chamber into two independent spaces while always keeping contact with the roller. The method of claim 11, Each of the discharge ports is spaced at equal intervals from the vane. The method of claim 11, And a retainer installed to be in contact with the discharge valve to limit an opening degree of the discharge valve. The method of claim 11, And the upper bearing has a suction passage for communicating the suction port with a suction pipe for supplying a fluid before compression. The method of claim 14, And a plenum in direct communication with the suction port and the suction passage and forming a wide space filled with the fluid introduced through the suction passage. The method of claim 15, The plenum is a rotary compressor installed to surround the upper portion of the upper bearing. The method of claim 15, And the suction port is provided to penetrate the upper bearing vertically so that the plenum and the compression chamber communicate with each other. The method of claim 11, A bypass for supplying a fluid before compression to a vacuum space generated between the roller and the vane when the roller is idle; And And a bypass valve provided in the bypass and configured to control opening and closing of the bypass by a pressure difference. The method of claim 18, And the bypass is provided to the upper bearing such that the suction space and the two spaces in the cylinder defined by the vanes communicate with each other. The method of claim 18, The bypass valve further comprises a retainer installed in contact with the bypass valve to limit the opening degree of the bypass valve. The method of claim 15, A bypass for supplying a fluid before compression to a vacuum space generated between the roller and the vane when the roller is idle; And And a bypass valve provided to the bypass to control opening and closing of the bypass by a pressure difference. The method of claim 21, And the bypass is provided to the upper bearing such that the plenum and the compression chamber communicate with each other. The method of claim 21, The bypass valve further comprises a retainer installed in contact with the bypass valve to limit the opening degree of the bypass valve. The method of claim 11, And a discharge passage connected to the discharge port and configured to guide and discharge the compressed fluid discharged from the discharge port to the upper side. The method of claim 24, And one end is connected to the discharge port and the other end is in communication with an upper space of the upper bearing. The method of claim 25, And a discharge pipe having one end connected to the discharge port and the other end communicating with an upper space of the upper bearing. The method of claim 24, The discharge passage A first flow passage communicating with an upper space of the upper bearing, and And a muffler communicating the first flow path and the discharge port. The method of claim 27, The muffler is provided below the lower bearing to expand the compressed fluid discharged from the discharge port to reduce the noise. The method of claim 27, The first flow path, And one end of which communicates with the muffler and the other end of which communicates with the upper space of the upper bearing in order to sequentially pass through the lower bearing, the cylinder and the upper bearing. The method of claim 27, The first flow path, And a pipe provided outside the cylinder such that one end communicates with the muffler and the other end communicates with an upper space of the upper bearing. The method of claim 11, Any one of the suction port is located on any one side of the virtual line passing through the partition member. The method of claim 31, wherein Any one of the suction port is located in the range of 180 ° ~ 300 ° in any direction with respect to the partition member. The method of claim 11, Any one of the suction ports is located on an imaginary line passing through the partition member. The method of claim 11, The vane is a rotary compressor is provided with an elastic force from the spring provided between the cylinder and the vane. delete The method of claim 12, And the discharge ports include first and second discharge ports positioned to face each other with respect to the vanes. delete The method of claim 11, The suction port, A first suction port positioned adjacent said vane; And And a second suction port spaced apart from the first suction port by a predetermined angle with respect to the center of the cylinder. The method of claim 38, The valve assembly, A first valve rotatably installed between the eccentric portion and the upper bearing, the first valve being in contact with the eccentric portion and rotating in the rotational direction of the drive shaft; And And a second valve provided between the cylinder and the upper bearing to guide rotational movement of the first valve. The method of claim 39, The first valve has an outer diameter larger than the inner diameter of the cylinder. The method of claim 39, The first valve, A first opening communicating with the first suction port when the driving shaft is rotated in any one direction; And And a second opening communicating with the second suction port when the driving shaft is rotated in another direction. The method of claim 41, wherein The first and second openings are positioned adjacent to an outer circumferential surface of the first valve. The method of claim 39, And the second valve has a seat in the center for receiving the first valve. The method of claim 39, The suction port further comprises a third suction port and a third suction port located on the vane, And the first opening of the first valve opens the third suction port when the second suction port is opened. The method of claim 39, The valve assembly further comprises means for controlling the rotational angle of the first valve to precisely open the suction port in each rotational direction. The method of claim 45, The control means, A protrusion protruding in the radial direction to the first valve; And And a groove formed in the second valve, the groove movably receiving the protrusion. delete delete delete delete delete delete delete delete delete