KR20060117112A - Modulation type twin rotary compressor and airconditioner using this - Google Patents

Abstract

A twin rotary compressor and an air conditioner using the compressor are provided to convert the operation mode of the compressor by restricting and releasing a vane using the pressure difference of the vane. A twin rotary compressor includes a casing(10), a drive unit(20), a plurality of compression units(30,40), a guide unit(50), and a control unit(60). The guide unit guides a refrigerant to the compression units and selectively guides the refrigerant discharged from one of the compression units to the plurality of compression units. The control unit allows the plurality of compression units to perform compression strokes or guides or interrupts a refrigerant discharged from the compression unit. The control unit idles or normally operates the compression unit by restricting or releasing a vane of the compression unit.

Description

Multi-stage Rotary Compressor and Air Conditioner Applying It {MODULATION TYPE TWIN ROTARY COMPRESSOR AND AIRCONDITIONER USING THIS}

1 is a longitudinal sectional view showing an example of the double rotary compressor of the present invention;

Figure 2 is a longitudinal cross-sectional view showing a power mode operating state in the double rotary compressor of the present invention,

3 is a cross-sectional view taken along line "I-I" of FIG.

Figure 4 is a longitudinal cross-sectional view showing a saving mode operating state of the first compression unit in the double rotary compressor of the present invention,

5 is a cross-sectional view taken along line "II-II" of FIG. 4;

Figure 6 is a longitudinal cross-sectional view showing a saving mode operating state of the second compression unit in the double rotary compressor of the present invention,

FIG. 7 is a sectional view taken along the line "III-III" of FIG. 6;

8 and 9 are longitudinal cross-sectional views each showing a modified example of the double rotary compressor of the present invention.

** Description of the symbols for the main parts of the drawings **

10: casing 20: drive unit

23: rotating shaft 30: the first compression unit

31: first cylinder 32: upper bearing

33: intermediate bearing 34: first rolling piston

35: first vane 36: vanes spring

37: first discharge valve 38: first muffler

40: second compression unit 41: second cylinder

42: lower bearing 43: second rolling piston

44: second vane 45: vanes spring

46: second discharge valve 47: second muffler

50: guide unit 51: first suction pipe

52: second suction pipe 53: first branch pipe

54: second branch pipe 60: control unit

61a, 61b: first control valve (check valve) 62a, 62b: second control valve (2-way valve)

62: 2nd control valve (3-way, 4-way valve)

 BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multistage rotary compressor, and more particularly, to a multistage rotary compressor and an air conditioner using the same, to switch the operation mode of the compressor while restraining or releasing the vane by using the pressure difference between the front and rear of the vane.

In general, a compressor receives power from a power generating device such as an electric motor and compresses working gas to increase pressure by applying compression work to air, refrigerant, or other special gases, and is widely used throughout the industry. Compressors can be classified into volumetric and turbo type, depending on how the compression is achieved. A positive displacement compressor is a method of increasing pressure through volume reduction, and a turbo compressor is a method of converting kinetic energy of gas into pressure energy to achieve compression. Rotary compressors among volumetric compressors are mainly applied to air conditioners such as air conditioners, and in recent years, rotary compressors also require products that can vary in capacity in response to a trend of varying functions of air conditioners.

As a technique for varying the capacity of a rotary compressor, a so-called inverter method that controls the number of revolutions of the compressor by using an inverter motor is mainly known, but this technique is expensive because the inverter motor itself is expensive, and most of the air conditioners are statistically Considering that it is used as a cooler, it is difficult to increase the refrigerating capacity under heating conditions, which is more difficult in the cooling conditions, which is more important in the air conditioner compressor.

Accordingly, in recent years, the so-called "refrigeration capacity change technology" by changing the volume of the compression chamber by bypassing part of the refrigerant gas compressed in the cylinder to the outside of the cylinder (hereinafter referred to as "exchange volume switching"). Abbreviated as technology) is widely known.

As an example of the exclusion volume variable technology, a plurality of compression units having the same or different internal volume are connected to each other to connect the plurality of compression units to each other, and a valve is installed at a proper position of the pipe to change the flow path of the refrigerant while changing the capacity of the compressor. However, in this case, if the number of valves is not properly adjusted, excessive costs are incurred, as well as complicated operation, and if any one valve malfunctions, there is a concern that the variable capacity of the compressor may not be made smoothly.

 The present invention has been made in view of the above problems of the prior art, a multi-stage rotary compressor capable of smoothly varying the capacity of the compressor while reducing cost and simplifying operation by minimizing the number of valves installed in the middle of the pipe as much as possible; It is an object of the present invention to provide an air conditioner applying this.

In order to achieve the object of the present invention, a casing for forming a sealed space therein;

A driving unit built in the casing to generate a driving force; A plurality of compression units connected to the drive unit and installed in the casing and receiving the driving force from the drive unit to independently compress the refrigerant while pressing the rolling pistons to the vanes for linear movement; A guide unit connecting the plurality of compression units to guide the refrigerant to each of the compression units, and selectively guide the refrigerant discharged from one of the compression units to the plurality of compression units; Mounted on the guide unit to allow a plurality of compression units to perform a compression stroke, respectively, or to guide or block the refrigerant discharged from one of the compression unit discharged to the plurality of compression units to restrain or release the vanes of the compression unit, the compression It provides a multi-stage rotary compressor comprising a; control unit for idling or normal operation of the unit.

In addition, when a refrigerant having a plurality of compression units and a refrigerant compressed in one of the compression units is supplied to the compression chamber of either compression unit, the vane is restrained according to the pressure difference between the front and rear ends, and the idler is idle. Provided is an air conditioner having the multi-stage rotary compressor of claim 1 for normal operation when the refrigerant compressed in the compression unit is blocked from being supplied to the compression chamber of either compression unit.

Hereinafter, a multi-stage rotary compressor and an air conditioner to which the present invention is applied will be described in detail with reference to the accompanying drawings.

1 is a longitudinal cross-sectional view showing an example of the double rotary compressor of the present invention, Figures 2 and 3 is a longitudinal cross-sectional view showing a power mode operation state in the double rotary compressor of the present invention, and "I-I" front cross-sectional view of FIG. 4 and 5 are longitudinal cross-sectional views showing a saving mode operating state of the first compression unit in the double rotary compressor of the present invention and "II-II" cross-sectional view of FIG. 4, and FIGS. 6 and 7 are views of the double rotary compressor of the present invention. 2 is a longitudinal cross-sectional view showing a saving mode operation state of the compression unit, and a "III-III" cross-sectional view of FIG.

As shown therein, the multi-stage rotary compressor according to the present invention includes a casing 10 for forming a closed space therein, a driving unit 20 for generating a driving force by installing in the casing 10, and a driving unit ( A guide unit for guiding the flow of the refrigerant by connecting the first compression unit 30 and the second compression unit 40 connected to the compressor 20 to the compressor 20 and the evaporator outlet of the refrigeration cycle and the respective compression units, respectively; 50 and a control unit 60 mounted on the guide unit 50 to control the flow of the refrigerant according to the operation mode of the compressor.

The casing 10 is connected to a plurality of suction pipes 51 and 52 to be described later to communicate with each of the compression units 30 and 40 at the evaporator outlet of the refrigeration cycle, and the casing 10 to the condenser inlet of the refrigeration cycle. One discharge pipe (DP) is installed to pass through the sealed space of the.

The driving unit 20 is rotated while interacting with the stator 21 by arranging a stator 21 fixed to the inside of the casing 10 to apply power from the outside, and having a predetermined gap inside the stator 21. Rotor 22 and the rotating shaft 23 is provided with a plurality of eccentric portion to integrally coupled with the rotor 22 to transfer the driving force to the compression unit (30) (40). Here, the drive unit 20 is preferably configured as a constant speed motor because it is cheaper than an inverter motor having a control drive, but may be configured as an inverter motor in some cases.

The first compression unit 30 is formed in an annular shape to cover the first cylinder 31 installed in the casing 10 and the upper and lower sides of the first cylinder 31 to cover the first inner space V1 together. At the same time, the upper bearing 32 and the intermediate bearing 33 supporting the rotating shaft 23 in the radial direction and the upper eccentric portion of the rotating shaft 23 are inserted in the first inner space V1 of the first cylinder 31. The first rolling piston 34 which rotates and compresses the refrigerant, and is radially movably coupled to the first cylinder 31 so as to be press-contacted with the outer circumferential surface of the first rolling piston 34, A first vane 35 for dividing the first internal space V1 into a first suction chamber and a first compression chamber, a first vane spring 36 for elastically supporting a rear end of the first vane 35, and an upper portion thereof; Discharge of the refrigerant discharged from the first compression chamber by coupling the bearing 32 with the first discharge hole 32a formed to communicate with the first compression chamber so as to be openable and closeable. It is a first discharge valve 37 and the first discharging the first muffler (38) to accommodate a valve (37) provided on the upper bearing 32, which is controlled luer.

The upper bearing 32 is formed such that its outer circumferential surface has the same diameter as the inner circumferential surface of the casing 10 and welded to the casing 10, and the intermediate bearing 33 has a first vane 35 having a casing 10. In order to be influenced by the internal pressure, the rear side of the first vane slit 31a of the first cylinder 31 (more precisely, the rear end of the first vane) is exposed to the inner space of the casing 10. It is preferable to form.

The second compression unit 40 is formed in an annular shape and is positioned below the first cylinder 31 and coupled to the second cylinder 41 contacting the intermediate bearing 35 and the upper surface of the second cylinder 41. And the second cylinder by rotatably coupling the lower bearing 42 supporting the rotating shaft 23 in the radial and axial directions while forming the second inner space V2 together with the lower eccentric part of the rotating shaft 23. The second rolling piston (43) located in the second inner space (V2) of the (41) and the second cylinder 41 to be movable in the radial direction so as to be in pressure contact with the outer peripheral surface of the second rolling piston (43) Coupled to the second vane 44 which partitions the second internal space V2 of the second cylinder 41 into the second suction chamber and the second compression chamber, and the second vane 44 elastically supports the second vane 44. The second vane spring 45 made of the compression coil spring and the second pressure on one side of the lower bearing 42 so that the vanes 44 are pressed against the second rolling piston 43. A second discharge valve 46 and a second discharge valve 46 for controlling the discharge of the refrigerant discharged from the second compression chamber by coupling the second discharge hole 42a which is formed in communication with the shaft chamber to be opened and closed. The second muffler 47 is installed on the lower bearing 42.

Here, the first cylinder 31 and the second cylinder 41 form a first vane slit 31a and a second vane slit 41a on each side, and the first vane slit 31a and the second vane. One side of the slit 41a forms a first suction port 31b and a second suction port 41b to connect the first suction pipe and the second suction pipe, and the first vane slit 31a and the second vane slit ( On the other side of 41a, a first gas guide groove 31c and a second gas guide groove (not shown) are formed to communicate with the first discharge hole 32a and the second discharge hole 42a.

In addition, although the volume of the first internal space V1 of the first cylinder 31 and the volume of the second internal space V2 of the second cylinder 41 may be the same, they may be different from each other for more careful capacity variation. It is desirable to.

The guide unit 50 includes a first suction pipe 51 and a second suction pipe 52 connecting the accumulator A and the cylinders 31 and 41 of the respective compression units 30 and 40, respectively, and the second compression. The first branch pipe 53 and the second branch connecting the second muffler (or chamber) 47 of the unit 30, 40 to the middle of the first suction pipe 51 or the second suction pipe 52. It consists of an organ 54.

The control unit 60 includes a middle of each of the first suction pipe 51 and the second suction pipe 52, that is, the point where the first suction pipe 51 contacts the first branch pipe 53 and the second suction pipe 52 are formed. A plurality of check valves are provided upstream from the point of contact with the second branch pipe 54 to prevent the refrigerant sucked from the evaporator through the first suction pipe 51 and the second suction pipe 52 from flowing back to the evaporator again. A plurality of second control valves 62a disposed between the first control valves 61a and 61b and the branch pipes 53 and 54 so as to be opened and closed according to the operation mode of the compressor; 62b).

Effects of the present invention, the double rotary compressor as described above are as follows.

That is, when the rotor 22 is rotated by applying power to the stator 21 of the drive unit 20, the rotation shaft 23 rotates together with the rotor 22 to increase the rotational force of the drive unit 20. It delivers to the compression unit 30 and the second compression unit 40, and adjusts the plurality of second control valves 62a and 62b appropriately according to the required capacity in the air conditioner, while operating in a power mode, thereby allowing a large amount of cooling power. It generates a small amount of cold power while generating or performing a saving operation.

For example, when operating in a power mode, as shown in FIGS. 2 and 3, the plurality of second control valves 62a and 62b are all switched to OFF to thereby switch the first compression unit 30 and the second compression. Each of the refrigerants compressed in the unit 40 is discharged into the inner space of the casing 10. Here, as both of the second control valves 62a and 62b are closed, the refrigerant of the accumulator A passes through the plurality of first control valves 61a and 61b to allow the first suction pipe 51 and the second suction pipe to pass through. Through 52, the cylinders 31 and 41 of the first compression unit 30 and the second compression unit 40 are sucked. At this time, while the pressure Pb of the refrigerant filled in the inner space of the casing 10 maintains a high pressure state, the pressure Ps of the refrigerant sucked into the first cylinder 31 and the second cylinder 41 maintains a low pressure state. As a result, the first vane 35 and the second vane 44 are ultimately supported by the high-pressure refrigerant pressurizing the rear side while being pressed against the first rolling piston 34 and the second rolling piston 43. It generates 100% of cold power.

On the other hand, in the case of operating the first compression unit in the saving mode, as shown in FIGS. 4 and 5, the second control valve 62a mounted on the first branch pipe 53 is switched to the ON state so that the second compression valve 62a is turned on. A part of the refrigerant discharged from the compression unit 40 flows into the first suction pipe 51 through the second control valve 62a and the first branch pipe 53, and flows into the first suction pipe 51. The refrigerant is again filled the internal space of the cylinder 31 of the first compression unit (30). At this time, the pressure Pb1 of the refrigerant filling the internal space of the first cylinder 31 becomes relatively higher than the internal pressure Pb of the casing 10 as it becomes the pressure of the second muffler 47, that is, an ultrahigh pressure state. The first vane 35 is pushed out to restrain it. Accordingly, by maintaining the first vane 35 and the first rolling piston 34 spaced apart from each other, the first compression unit 30 is idling, resulting in only the capacity of the second compression unit 40. Generates cold power.

On the other hand, when the second compression unit is operated in the saving mode, as shown in FIGS. 6 and 7, the second control valve 62b mounted on the second branch pipe 54 is switched to the ON state to switch the first state. A part of the refrigerant discharged from the compression unit 40 flows into the second suction pipe 52 through the second control valve 62b and the second branch pipe 54 and flows into the second suction pipe 52. The refrigerant to be filled again fills the inner space of the cylinder 41 of the second compression unit 40 so that the second vane 44 and the second rolling piston 43 are kept spaced apart from each other so that the second compression unit 40 Is idling and thus generates only the cooling force as much as the capacity of the first compression unit 30. At this time, the pressure Pb1 of the refrigerant filling the internal space of the second cylinder 41 becomes relatively higher than the internal pressure Pb of the casing 10 as the pressure of the first muffler 38, that is, the ultra high pressure state. The second vane 44 is pushed out to restrain it.

Meanwhile, only one second control valve 63 may be installed at a point where two branch pipes 53 and 54 branch as shown in FIG. 8. In this case, the second control valve 63 is preferably constituted by a three-way valve or a four-way valve. Further, the first branch pipe and the second branch pipe may be independently connected to the discharge sides of the different compression units, respectively. That is, as shown in FIG. 9, the first branch pipe 53 is connected to the second muffler 47 of the second compression unit 40 while the second branch pipe 54 is formed of the first compression unit 30. 1 muffler 38 can be connected to simplify the piping.

Here, even in the above two cases, the operation sequence of each of the guide unit and the control unit according to the operation mode of the compressor is the same as the above-described example, and thus the detailed description of the compressor is omitted.

When the double rotary compressor according to the present invention is applied to an air conditioner, first control valves 61a and 61b serving as check valves are respectively installed in the first suction pipe 51 and the second suction pipe 52 connecting the evaporator and the compressor. The compression units 30 and 40 are branched to the first suction pipe 51 and the second suction pipe 52 to control the flow direction of the refrigerant compressed in the middle of each of the branch pipes 53 and 54. By installing the second control valve (62a) (62b) that can be opened and closed valve to change the capacity of the compressor to simplify the piping for the variable capacity of the compressor can not only expand the effective space inside the air conditioner The production cost can be reduced by reducing the number of valves used. In addition, it is possible to simplify the control program during operation of the air conditioner, thereby preventing the reliability of the air conditioner from malfunctioning.

In the multi-stage rotary compressor and the air conditioner to which the present invention is applied, check valves for preventing backflow of refrigerant are respectively provided in respective suction pipes connected to the respective compression units for varying the capacity, and the discharge sides of the other compression units are respectively checked valves. Each of the downstream suction pipes is connected to the branch pipe, and at the same time, an on / off valve for controlling the flow of the refrigerant is installed in the middle of the branch pipe to restrain or release the vanes of the compression unit to change the capacity of the compressor with high pressure refrigerant. By varying the configuration, it is possible to reduce the production cost by reducing the number of valves used to control the flow of the refrigerant, as well as to minimize the malfunction that may occur when the valve is used excessively, thereby increasing the reliability of the compressor and the air conditioner applied thereto.

Claims (17)

A casing which forms a sealed space therein; A driving unit built in the casing to generate a driving force; A plurality of compression units connected to the drive unit and installed in the casing and receiving the driving force from the drive unit to independently compress the refrigerant while pressing the rolling pistons to the vanes for linear movement; A guide unit connecting the plurality of compression units to guide the refrigerant to each of the compression units, and selectively guide the refrigerant discharged from one of the compression units to the plurality of compression units; Mounted on the guide unit to allow a plurality of compression units to perform a compression stroke, respectively, or to guide or block the refrigerant discharged from one of the compression unit discharged to the plurality of compression units to restrain or release the vanes of the compression unit, the compression A multistage rotary compressor, comprising a control unit for idling or normal operation of the unit. The method of claim 1, The guide unit comprises a plurality of suction pipes connecting the outlet of the evaporator and the cylinder inlet of each compression unit to guide the refrigerant to each compression unit; The rotary stage comprising a plurality of branch pipes connecting the discharge side of one compression unit and the suction side of each compression unit in parallel to guide the refrigerant discharged from one compression unit to the cylinder inlet of each compression unit. compressor. The method of claim 1, The guide unit comprises a plurality of suction pipes connecting the outlet of the evaporator and the cylinder inlet of each compression unit to guide the refrigerant to each compression unit; A multistage rotary system comprising a plurality of branch pipes connecting the discharge side of one of the compression units and the suction side of the other compression unit, respectively, to guide the refrigerant compressed and discharged from one compression unit to the cylinder inlet of the other compression unit; compressor. The method according to claim 2 or 3, The control unit includes a plurality of first control valves installed in both suction pipes to control the flow of the refrigerant; A multi-stage rotary compressor, comprising: at least one second control valve installed at each branch pipe independently to control the flow of refrigerant. The method of claim 4, wherein The branch pipe is a multi-stage rotary compressor, characterized in that for connecting the discharge side of one compression unit to the first control valve downstream side suction pipe. The method of claim 5, Multi-stage rotary compressor, characterized in that the first control valve is a check valve. The method of claim 5, The second control valve is a multi-stage rotary compressor, characterized in that the two-way valve (2-way valve). The method of claim 2, The control unit includes a plurality of first control valves installed in both suction pipes to control the flow of the refrigerant; And a second control valve installed at a branch point of each branch pipe to control the flow of the refrigerant. The method of claim 8, The branch pipe is a multi-stage rotary compressor, characterized in that for connecting the discharge side of one compression unit to the first control valve downstream side suction pipe. The method of claim 9, Multi-stage rotary compressor, characterized in that the first control valve is a check valve. The method of claim 9, The second control valve is a three-way valve (3-way valve) or a multi-stage rotary compressor, characterized in that the four-way valve (4-way valve). The method of claim 1, The vane of the compression unit is characterized in that the rear end is supported by the pressure in the sealed space of the casing so that the vane is pressed or spaced in the rolling piston according to the pressure difference in the sealed space of the compression chamber and the casing of the compression unit. Multistage rotary compressor. The method of claim 12, The vane of the compression unit further comprises a vane spring made of a compression spring to elastically support the rear end thereof. The method of claim 1, The plurality of compression units is a multi-stage rotary compressor, characterized in that to form different volumes of the inner space for sucking and compressing the compressed refrigerant. The method of claim 1, The drive unit is a multi-stage rotary compressor, characterized in that composed of a constant speed motor. The method of claim 1, The drive unit is a multi-stage rotary compressor, characterized in that composed of an inverter motor. When the refrigerant compressed in one of the two compression units is supplied to the compression chamber of one of the two compression units, the vane is constrained and idling according to the pressure difference between the front and rear ends, while the one of the two compression units is provided. Air conditioner with the multi-stage rotary compressor of claim 1 for normal operation when the refrigerant compressed in the block to be supplied to the compression chamber of either of the compression unit.

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