KR20040097740A - Rotary Type Compressor - Google Patents

Abstract

PURPOSE: A rotary compressor is provided to vary compressive capacity according to a mode while rotating a roller of the rotary compressor in a direction and to obtain compressive capacity corresponding to the compressive capacity of a usual rotary compressor even in compression of large capacity. CONSTITUTION: A rotary compressor comprises a driving shaft rotating by a motor; a cylinder in which a compression chamber(200) is formed; a suction port(51) communicating with the compression chamber to suck a fluid into the compression chamber from the outside; a bypass port(57) arranged to a position standoff from the suction port; a discharge port(61) for discharging the fluid compressed from the compression chamber; a roller(80) eccentrically combined to the driving shaft, to roll along the inner wall surface of the compression chamber while eccentrically rotating inside the compression chamber; a vane(90) installed between the suction port and the discharge port, to partition the compression chamber into a suction space and a discharge space while maintaining electric contact with a rolling member; an upper bearing part and a lower bearing part rotatably supporting the driving shaft on the upper and lower parts of the cylinder and each shutting the upper part and lower part of the compression chamber of the cylinder; and an opening and shutting unit selectively opening and shutting the bypass port according to an operation mode. Compression spaces of different volume are formed in the compression chamber according to the opening and shutting of the bypass port.

Description

Rotary Compressor {Rotary Type Compressor}

The present invention relates to a rotary compressor, and more particularly, to a rotary compressor capable of compressing and discharging fluid with two compression capacities depending on a mode while rotating in one direction.

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 compressor is provided with one suction port and one discharge port communicating with the cylinder to which compression is performed, and a roller moves inside the cylinder from the suction port side to the discharge port side along the inner circumferential surface of the cylinder. While it is intended to compress the working fluid, the conventional rotary compressor has a problem that it is impossible to vary the compression capacity.

Recently, compressors capable of varying the compression capacity have been developed to cope with various operating conditions such as air conditioners. Since the conventional rotary compressor has only one compression capacity, its application range may be quite narrow. There was only.

Accordingly, the present invention has been made in order to solve the above problems, it is possible to vary the compression capacity to low capacity and large capacity according to the mode while rotating the roller of the rotary compressor in one direction, even when the compression of the conventional rotary compressor It is an object to provide a rotary compressor having a compression capacity corresponding to the compression capacity.

1 is a sectional view showing the main parts of a rotary compressor according to an embodiment of the present invention;

2 is an exploded perspective view of the rotary compressor of FIG.

3 is a plan view showing a compression unit of the rotary compressor of FIG.

4 is a bottom view of the upper bearing member of the rotary compressor of FIG.

5A to 5C are plan views illustrating a compression process sequentially explaining a compression process performed in a power mode in the rotary compressor of FIG. 1.

6A through 6C are plan views illustrating compression processes sequentially performed in a saving mode in the rotary compressor of FIG. 1.

7A and 7B are principal part sectional views showing the first embodiment of the solenoid valve of the rotary compressor of FIG.

8A and 8B are principal part sectional views showing the second embodiment of the solenoid valve of the rotary compressor of FIG.

9A and 9B are cross-sectional views illustrating main parts of a solenoid valve of the rotary compressor of FIG. 1.

10 is an exploded perspective view showing another embodiment of a rotary compressor according to the present invention;

FIG. 11 is a sectional view of principal parts of the rotary compressor of FIG. 10; FIG.

12 is a plan view of the compression unit of the rotary compressor of FIG.

13 is an exploded perspective view showing another embodiment of a rotary compressor according to the present invention

14 is a plan view of the compression unit of the rotary compressor of FIG.

15 is a cross-sectional view taken along the line I-I of FIG.

Explanation of Reference Symbols in Main Parts of Drawings

20: Stator 30: Rotor

40: crankshaft 41: eccentric cam portion

50: cylinder 51: suction port

57: bypass port 58: connection euro

60: upper bearing portion 61: discharge port

66: corresponding connection flow path 70: lower bearing part

76, 77: suction port 78: discharge port

80: roller 90: vane

200: compression chamber 300: suction plenum

500, 510, 520, 530, 550: Solenoid Valve

The present invention for achieving the above object, the drive shaft rotated by a drive motor rotated by a motor; A cylinder in which a compression chamber of a predetermined volume is formed; A suction port communicating with the compression chamber so that fluid is sucked into the compression chamber from the outside; A bypass port formed at a position spaced apart from the suction port by a predetermined distance; A discharge port through which the fluid compressed in the compression chamber is discharged; A roller eccentrically coupled to the drive shaft, the roller eccentrically rotating in the compression chamber and rolling along the inner wall of the compression chamber and partitioning a space for suction and compression of fluid together with the compression chamber inner wall; A vane disposed between the suction port and the discharge port to maintain elastic contact with the rolling member at all times and divide the compression chamber into a suction space and a discharge space; An upper bearing part and a lower bearing part installed on the upper and lower parts of the cylinder to rotatably support the driving shaft, and closing the upper and lower parts of the compression chamber of the cylinder, respectively; And an opening and closing unit for selectively opening and closing the bypass port according to the operation mode; Provided is a rotary compressor in which different volumes of compression space are formed in the compression chamber according to opening and closing of the bypass port.

Hereinafter, preferred embodiments of the rotary compressor according to the present invention will be described in detail with reference to the accompanying drawings.

1 to 4 show the structure of an embodiment of a rotary compressor according to the present invention, Figures 5a to 5c and 6a to 6d are operating modes of the rotary compressor according to the present invention for implementing different compression capacity, respectively It is a figure explaining a different action.

First, as shown in Figures 1 and 2, the rotary compressor according to the present invention is largely the case 1, the transmission unit located on the upper portion of the case 1, the compression located below the transmission unit It consists of wealth.

The case 1 is composed of an upper cap 3 disposed on the upper portion and a lower cap 5 coupled to the lower portion of the upper cap 3 to form a sealed inner space. A suction pipe 7 through which gas is sucked from the outside is installed at one side of the case 1, and a discharge pipe 9 through which compressed gas is discharged is installed at the center of the upper cap 3.

The transmission part includes a stator 20 fixed to the case 1, a rotor 30 rotatably installed inside the stator 20, and a crankshaft 40 press-fitted into the rotor 30. do. The rotor 30 is rotated by the electromagnetic force, the crankshaft 40 transmits the rotational force of the rotor 30 to the compression unit. At this time, in order to supply external power to the stator 20, the upper cap (3) is provided with a hermetic terminal (4).

The compression unit rotatably supports the cylinder 50 fixed to the case 1, the roller 80 compressing the gas while rolling along the inner circumferential surface of the cylinder 50, and the crankshaft 40. The upper bearing portion 60 and the lower bearing portion 70 is composed of. At this time, the upper bearing portion 60 and the lower bearing portion 70 together with the cylinder 50 forms a compression chamber 200.

The configuration of the compression unit will be described in more detail as follows. As shown in FIG. 2, the crankshaft 40 has an eccentric cam portion 41 integrally formed at a lower portion thereof. The eccentric cam portion 41 has a center spaced apart from the rotation center of the crankshaft 40 by a predetermined distance. Here, the eccentric cam portion 41 may be formed integrally with the crankshaft 40, but may be implemented as an eccentric pin inserted into the crankshaft 40.

The cylinder 50 has a cylindrical shape in which upper and lower surfaces are open, and a compression chamber 200 having a predetermined volume in which the eccentric cam portion 41 is accommodated is formed. One side of the cylinder 50 is formed with a suction port 51 which communicates with the outside, the suction port 51 is a flow path for guiding the outside gas into the compression chamber 200.

In this embodiment, the suction port 51 is formed in a direction orthogonal to the crankshaft 40, and is connected to the suction pipe 7 through a connection pipe 52.

The sidewalls of the cylinder 50 adjacent to the suction port 51 are provided with installation grooves 53 which are recessed by a predetermined depth from the inner circumferential surface. The installation groove 53 is a space in which the vanes 90 to be described later are installed, and the installation groove 53 has a sufficient depth to completely accommodate the vanes 90.

The roller 80 has a ring shape having an outer diameter smaller than the inner diameter of the cylinder 50 and is coupled to the eccentric cam portion 41. Here, the roller 80 is to be rolled along the inner circumferential surface of the cylinder 50, for this purpose, the roller 80 is rotatably installed with respect to the eccentric cam portion 41. Alternatively, when the eccentric cam portion 41 is rotatably installed with respect to the crankshaft 40, the roller 80 may be fixed to the eccentric cam portion 41.

As described above, the vane 90 is installed in the installation groove 53 of the cylinder 50. The vane 90 is a member that divides the compression chamber 200 into a suction space in which gas is sucked and a discharge space in which compressed gas is compressed and discharged. To this end, the vanes 90 should always be in contact with the outer circumferential surface of the roller 80.

However, when the crankshaft 40 rotates, the roller 80 revolves around the center of the compression chamber 200 as the rotation center. Therefore, in order to maintain close contact between the vanes 90 and the rollers 80, the vanes 90 need to be elastically installed. To this end, a spring 95 for elastically supporting the vane 90 is installed in the installation groove 53 of the cylinder 50. That is, the spring 95 is one end is fixed to the cylinder 50 and the other end is coupled to the vane 90, by pushing the vane 90 to the roller 80 side, the vane 80 is the front end roller Continuous contact with the outer circumferential surface of (80).

The upper bearing portion 60 and the lower bearing portion 70 pass through the crankshaft 40 and are coupled to the upper and lower surfaces of the cylinder 50, respectively. Here, a plurality of fastening holes 65, 75, and 55 are formed at positions corresponding to each other of the upper bearing portion 60, the lower bearing portion 70, and the cylinder 50. Therefore, the cylinder 50 and the upper and lower bearing parts 60 and 70 are coupled to each other through separate fastening screws, wherein the cylinder 50 and the upper and lower bearing parts 60 and 70 are formed of gas. Closely coupled to each other so that there is no leakage.

In the upper bearing part 60, one discharge port 61 is formed in communication with the compression chamber 200 to form a discharge flow path of the compressed gas, wherein the discharge port 61 connects the vane 90. It is preferably located approximately opposite the suction port 51 as a center.

The upper bearing part 60 is provided with a discharge valve 110 for controlling the discharge of the gas through the discharge port 61. The discharge valve 110 serves to open the discharge port 61 only when the pressure in the compression chamber 200 is greater than or equal to a predetermined pressure. For this purpose, the discharge valve 110 has one end discharge port 61. It is preferable that the other end is configured in the form of a leaf spring which is supported near the other end while maintaining the free state.

On the other hand, as shown in Figure 1, a retainer (130) is installed on the upper portion of the discharge valve 110, the retainer 130 is to ensure a stable operation of the discharge valve 110, It is installed to be in contact with the discharge valve 110, to limit the opening degree of the discharge valve (110). When the retainer 130 is not present, the discharge valve 110 may be excessively bent due to high pressure. When this occurs, reliability of the discharge valve 110 may be degraded.

The muffler 140 is installed above the upper bearing part 60. The muffler 140 reduces noise generated when the compressed gas is discharged. To this end, the muffler 140 surrounds the upper space of the discharge port 61, a separate discharge hole 141 is formed on one side.

A certain amount of refrigeration oil (O) is filled in the bottom surface of the case (1) for lubrication and cooling of the frictional member. At this time, the end of the crankshaft 40 is locked to the refrigerator oil (O).

On the other hand, the rotary compressor of the present invention can realize a double compression capacity by varying the point where the actual compression starts when the roller 80 rotates in the compression chamber 200, the configuration of the compression unit for this Referring to 3 and 4 in more detail as follows.

As shown in FIGS. 3 and 4, the suction port 51 of the cylinder 50 is disposed on one side of the vane 90 and is opposite to the suction port 51 about the vane 90. The discharge port 61 is arranged.

In addition, a bypass port 57 is formed in the cylinder 50, one end of which is communicated with the inside of the compression chamber 200 at a position separated by a predetermined angle from the suction port 51. The suction port 51 and the bypass port 57 are connected to each other by a connecting flow path 58 formed along the circumferential direction on the upper surface of the cylinder 50.

The connecting flow path 58 has a substantially semi-circular groove shape, and the connection flow path 58 has a shape corresponding to that of the connection flow path 58 on the lower surface of the upper bearing part 60 in order to have a sealed structure. The corresponding connection flow path 66 is formed. Thus, when the upper bearing portion 60 is coupled to the cylinder 50, the connection flow path 58 and the corresponding connection flow path 66 is in the form of a groove of approximately circular cross section.

A solenoid valve 500 for communicating and closing the bypass port 57 and the connection passage 58 is installed at a portion where the bypass port 57 and the connection passage 58 cross each other.

The solenoid valve 500 is electrically connected to the transmission unit of the compressor to operate in conjunction with the electrical signal applied to the transmission unit, it is configured to communicate and close the bypass port 57 and the connection flow path (58). Embodiments of the specific structure and operation of the solenoid valve 500 will be described later in detail with reference to FIGS. 7A to 9B.

On the other hand, the position in which the bypass port 57 is installed is a position spaced at an angle from the suction port 51 according to the compression capacity to be changed, for example, 100 ° ~ 200 ° spaced from the suction port 51 Can be set to the specified position.

Referring to the mode-specific operation of the rotary compressor configured as described above are as follows.

5A to 5C show a compression process in a power mode to realize a large compression capacity. In this mode, the solenoid valve 500 is compressed while the bypass port 57 is closed. This is done, the roller 80 is revolved counterclockwise in the compression chamber 200 by the rotation of the crankshaft 40 and its outer peripheral surface is in constant contact with the inner wall surface of the compression chamber 200.

Therefore, the gas sucked through the suction pipe 7 (see FIG. 1) and the connection pipe 52 flows into the compression chamber 200 only through the suction port 51.

Then, since the suction port 51 is open until the roller 80 passes through the vane 90 and passes through the suction port 51, compression does not occur, and the roller 80 passes through the suction port 51. From this point in time, since the compression chamber 200 is completely closed, the compression of the gas proceeds gradually from this time.

When the roller 80 advances to a certain degree and the pressure of the gas reaches a certain level or more, the discharge valve 110 is opened and the compressed gas is discharged through the discharge port 61. At this time, the space from the portion where the roller 80 passes to the vane 90 continues to be filled with gas through the suction port 51.

At the point where the roller 80 is close to the vane 90, most of the gas is discharged through the discharge port 61, and the roller 80 passes through the vane 90 and passes through the suction port 51. Repeat the same process to perform compression.

Therefore, in the power mode as described above, compression occurs by an angle from the suction port 51 to the discharge port 61.

On the other hand, Figure 6a to 6d shows a compression process in a saving mode (saving mode) state to implement a small capacity compression capacity, in this saving mode, the electric motor only needs to output the torque for the small capacity compression stroke accordingly The motor output is changed, and the solenoid valve 500 is operated by the output change of this transmission part, and the bypass port 57 and the connection flow path 58 communicate with each other.

Therefore, in this saving mode, gas is introduced not only through the suction port 51 but also through the bypass port 57.

First, as shown in FIGS. 6A and 6B, the suction roller 51 and the bypass port 57 are both rotated counterclockwise to pass through the vanes 90 to the bypass port 57. Since it is in an open state, a part of the gas pushed toward the discharge port 61 by the progress of the roller 80 is discharged toward the connection flow path 58 through the bypass port 57, and compression does not occur.

In addition, since the compression chamber 200 is completely sealed from the point where the roller 80 passes the bypass port 57, the compression of the gas proceeds gradually from this time. That is, in the saving mode, compression occurs up to an angle from the bypass port 57 to the discharge port 61.

When the roller 80 advances to a certain degree and the pressure of the gas reaches a certain level or more, the discharge valve 110 is opened and the compressed gas is discharged through the discharge port 61. At this time, the space from the portion where the roller 80 passes to the vane 90 continues to be filled with gas through the suction port 51 and the bypass port 57.

As described above, in the rotary mode of the present invention, since the bypass port 57 is in a closed state, the compression is advanced by an angle from the suction port 51 to the discharge port 61, so that the compression capacity of the large capacity is increased. In the saving mode, since the bypass port 57 is converted into an open state, the compression proceeds only as much as the angle from the bypass port 57 to the discharge port 61, so that a compression capacity of a small capacity can be obtained.

In the above-described embodiment, when the roller 80 is compressed through the suction port 51 in the power mode, if a small space is formed between the outlet of the bypass port 57 and the solenoid valve 500 in this portion, A dead volume arises where the gas expands and degrades compression efficiency.

Therefore, the solenoid valve 500 is preferably installed to be as close as possible to the inner wall of the compression chamber 200, preferably, the body of the solenoid valve 500 is in contact with the inner wall of the compression chamber 200, there is no space at all It is a good idea to avoid this.

In addition, in the above-described embodiment, the bypass port and the suction port have been described as being interconnected, but this is not necessarily the case.

In addition, in the above embodiment, the connection passage 58 connecting the suction port 51 and the bypass port 57 to each other has been described as being formed on the upper surface of the cylinder 50. It may be formed. In this case, it is preferable to form a flow path corresponding to the connection flow path on the upper surface of the lower bearing part.

7A and 7B illustrate a first embodiment of a solenoid valve for opening and closing the bypass port 57 as described above. The solenoid valve 510 of this embodiment includes a connection flow path 58 and a bypass port ( 57 is formed in a substantially cylindrical body 511 which is installed to be movable up and down at the intersection of the 57, and approximately 'a' shape in the body 511 to connect the connection flow path 58 and the bypass port 57 The guide hole 512 to interconnect with each other, and the plunger 513 is electrically connected to the electric drive on the upper end of the body 511 to operate.

The body 511 of the solenoid valve 510 is elastically supported by the lower compression spring 514.

Thus, as shown in FIG. 7A, in the power mode, the solenoid valve 510 is positioned upward by the action of the compression spring 514 so that the body 511 is connected to the connection passage 58 and the bypass port 57. Will be closed. As shown in FIG. 7B, in the saving mode, the electrical signal is applied and the plunger 513 and the body 511 are lowered so that the guide hole 512 coincides with the bypass port 57 and the connection flow path 58. Is opened.

When switching from the saving mode to the power mode, the electrical signal is cut off, and the body 511 and the plunger 513 are raised again by the elastic force of the compression spring 514 to position the guide hole 512 and the bypass port 57. Is shifted and the bypass port 57 is closed.

8A and 8B show a second embodiment of solenoid valve 520. The solenoid valve 520 of this embodiment has a linear guide hole 522 is formed in the cylindrical body 521 which is installed in the bypass port 57 to be reciprocally rotated in both directions.

Therefore, in the power mode, as shown in FIG. 8A, the guide hole 522 and the bypass port 57 of the solenoid valve 520 are shifted from each other, and the bypass port 57 is connected to the body 521 of the solenoid valve 520. Closed state.

In the saving mode, as the electrical signal is applied as shown in FIG. 8B, the body 521 of the solenoid valve 520 rotates by 90 ° while the guide hole 522 and the bypass port 57 coincide with each other. The 58, the guide hole 522, and the bypass port 57 communicate with each other to allow gas to move.

9A and 9B, the embodiment of the solenoid valve 530 is also configured to open and close the bypass port 57 while the body 531 of the solenoid valve 530 rotates in both directions or one direction. In the embodiment, the guide hole 532 for communicating the bypass port 57 and the connection passage 58 to each other is formed in a '-' shape.

FIG. 9A shows a solenoid valve state in a power mode, and FIG. 9B shows a solenoid valve state in a saving mode.

10 and 11 illustrate another embodiment of the rotary compressor according to the present invention. In the above-described embodiment, the rotary compressor has a suction port 56 of the cylinder 50 directly connected to the suction pipe 7 so that the gas In this embodiment, the structure is supplied with gas through the suction port 56 of the cylinder 50 after the gas is supplied to a separate suction plenum 300.

In more detail, the suction plenum 300 in the form of a container having an upper surface open to the lower portion of the lower bearing part 70 is fixed, and the suction plenum 300 is connected to the suction pipe 7 to supply gas. To be supplied. Therefore, the gas supplied through the suction pipe 7 is primarily stored in the space in the suction plenum 300.

In addition, a suction port 56 is installed in the cylinder 50 so as to be close to the vane 90, and the suction port 56 is sucked through the suction hole 76 formed to penetrate the lower bearing part 70. In communication with the plenum 300.

In addition, similar to the above-described embodiment, the bypass port 57 is formed at a position spaced apart from the suction port 56 at a predetermined angle in the cylinder 50, and the bypass port 57 is connected to the flow path 58. It is connected to the suction port 56 by the). The inlet side of the bypass port 57 is provided with a solenoid valve 500 for communicating and closing the bypass port 57 and the connection flow path 58, the configuration and operation of the solenoid valve 500 is described above. It will be easily understood by referring to the configuration and operation of the solenoid valves of the two solenoid valves.

Therefore, in the rotary compressor of this embodiment, the gas is first supplied to the suction plenum 300 through the suction pipe 7 and temporarily stored therein, and then the suction port through the suction hole 76 of the lower bearing part 70. 56 is supplied to the compression chamber 200 and then compressed.

This embodiment differs from the above-described embodiment in that the gas supply process to the compression unit is performed through the suction plenum 300, and the compression process performed in the compression chamber in the power mode and the saving mode is performed as described above. Same process as the example.

Meanwhile, the rotary compressor of this embodiment has a structure in which the suction plenum 300 and the suction port 56 are connected through the suction hole 76 of the lower bearing part 70, but unlike the lower bearing part 70 and the suction part. The suction port 56 and the suction plenum 300 may be connected by using a separate suction pipe outside the plenum 300.

13 and 14 are modified examples of the rotary compressor described with reference to FIGS. 10 to 11, and the suction plenum 300 in which gas is temporarily supplied and stored under the lower bearing part 70 is also stored in the rotary compressor of this embodiment. ) Is fixed, but the suction port is not formed on the side wall of the cylinder 50, and the suction port 77 is formed in the lower bearing portion 70 to directly communicate with the suction plenum 300, the suction plenum 300 The gas stored in the gas is supplied directly into the compression chamber 200 without passing through the side wall of the cylinder 50.

Here, the suction port 77 is formed at a position adjacent to the vane (90). As in the above-described embodiments, one discharge port 61 is formed on the opposite side of the suction port 51 around the vane 90 to communicate with the upper bearing part 60 on the upper side.

In addition, a bypass port 78 which is directly in communication with the suction plenum 300 is formed at a position spaced a predetermined angle from the suction port 77 of the lower bearing part 70. A solenoid valve 550 for selectively opening and closing the bypass port 78 is installed at a lower portion of the lower bearing part 70 according to an operation mode.

In the rotary compressor of the present embodiment, after the solenoid valve 550 closes the bypass port 78 in the power mode, gas is first supplied to the suction plenum 300 and then the compression chamber through the suction port 77. (200) is supplied to the inside is compressed, and in the saving mode, the solenoid valve 550 opens the bypass port 78, so the gas flows through the suction port 77 and the bypass port 78 and compressed. This is done.

As described above, according to the present invention, different compression capacities can be provided by varying the time point at which compression proceeds according to the operation mode while rotating the roller in one direction.

In the related art, various devices have been 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.

In addition, the conventional compressor 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, thereby reducing the power consumption.

In addition, the rotary compressor of the present invention uses the whole existing compression chamber designed 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.

Claims (23)

A drive shaft rotating by a motor; A cylinder in which a compression chamber of a predetermined volume is formed; A suction port communicating with the compression chamber so that fluid is sucked into the compression chamber from the outside; A bypass port formed at a position spaced apart from the suction port by a predetermined distance; A discharge port through which the fluid compressed in the compression chamber is discharged; A roller eccentrically coupled to the drive shaft, the roller eccentrically rotating in the compression chamber and rolling along the inner wall of the compression chamber and partitioning a space for suction and compression of fluid together with the compression chamber inner wall; A vane disposed between the suction port and the discharge port to maintain elastic contact with the rolling member at all times and divide the compression chamber into a suction space and a discharge space; An upper bearing part and a lower bearing part installed on the upper and lower parts of the cylinder to rotatably support the driving shaft, and closing the upper and lower parts of the compression chamber of the cylinder, respectively; And an opening and closing unit for selectively opening and closing the bypass port according to the operation mode; And a compression space of a different volume is formed in the compression chamber according to opening and closing of the bypass port. The rotary compressor of claim 1, wherein the opening / closing unit is a solenoid valve electrically connected to the motor to open and close the bypass port in conjunction with the operation of the motor. The rotary compressor of claim 1, wherein the suction port and the bypass port are formed in communication with the compression chamber on the side wall of the cylinder, and a connection flow path is formed on the side wall of the cylinder to connect the suction port and the bypass port to each other. . 4. The rotary compressor of claim 3, wherein the connection channel is formed on an upper surface of the cylinder. 5. The rotary compressor of claim 4, wherein a corresponding connection channel corresponding to the connection channel is formed on a lower surface of the upper bearing part. 4. The rotary compressor of claim 3, wherein the connection channel is formed on a lower surface of the cylinder. 7. The rotary compressor of claim 6, wherein a corresponding connection channel corresponding to the connection channel is formed on an upper surface of the lower bearing part. The solenoid valve of claim 3, wherein the opening / closing unit is installed to be electrically connected to the motor at a connection portion between the bypass port and the connection channel, and communicates and closes the bypass port and the connection channel in conjunction with the operation of the motor. Rotary compressor characterized by. 9. The rotary compressor of claim 8, wherein the solenoid valve is configured to communicate with and close the connection flow path and the bypass port while the body moves linearly up and down. 10. The rotary compressor of claim 9, wherein an elastic member for elastically supporting the solenoid valve is installed under the body of the solenoid valve. 9. The rotary compressor of claim 8, wherein the solenoid valve is configured to communicate with and close the vice pass port and the connection passage while the body rotates in one or both directions. 12. The rotary compressor of claim 9 or 11, wherein the body of the solenoid valve has a cylindrical or polygonal cylinder. 13. The rotary compressor of claim 12, wherein a fluid guide hole is formed in the body of the solenoid valve so that one end of the solenoid valve communicates with the bypass port and the other end of the solenoid valve communicates with the connection passage. The rotary compressor of claim 13, wherein the fluid guide hole is formed in a straight shape in the body. The rotary compressor of claim 13, wherein the fluid guide hole is formed in a '-' shape in the body. 2. The rotary compressor of claim 1, wherein the suction port and the discharge port are installed close to both sides of the vane with respect to the vane. 2. The apparatus of claim 1, further comprising: an intake plenum connected to an external fluid source to temporarily suck the fluid and temporarily storing the fluid; and a fluid stored in the intake plenum by connecting the intake plenum and the suction port. The rotary compressor further comprises a suction passage leading to the suction port. 18. The rotary compressor of claim 17, further comprising a bypass passage connecting the suction plenum and the bypass port. 19. The rotary compressor of claim 17 or 18, wherein the suction plenum is provided under the lower bearing portion. 20. The rotary compressor of claim 19, wherein the suction passage is connected to the suction port through the lower bearing part. 20. The rotary compressor of claim 19, wherein the suction flow passage comprises a suction pipe connecting one side of the suction plenum and the suction port to the outside of the lower bearing part. 19. The rotary compressor of claim 18, wherein the bypass passage is connected to the bypass port through the lower bearing part. 19. The rotary compressor of claim 18, wherein the bypass passage comprises a bypass tube connecting one side of the suction plenum and the bypass port to the outside of the lower bearing part.