KR100677515B1 - Modulation type multi-stage rotary compressor and airconditioner using this - Google Patents

Abstract

Multi-stage rotary compressor according to the present invention and an air conditioner using the same, the casing for forming a sealed space therein; A driving unit built in the casing to generate a driving force; It is connected to the drive unit, installed inside the casing, and receives the driving force from the drive unit, each rolling piston turning in the inner space of each cylinder presses with each vane in a linear motion to compress the refrigerant independently and compress A plurality of compression units for discharging the refrigerant to the sealed space of the casing through respective mufflers; A guide unit which connects a plurality of compression units to guide the refrigerant to each compression unit and selectively guides the refrigerant discharged from the muffler of either compression unit to a cylinder of the other compression unit; Attached to the guide unit so that a plurality of compression units perform compression strokes respectively, or guide or block refrigerant discharged from one compression unit to another compression unit to restrain or release the vanes of the other compression unit By including a control unit for idling or normal operation of the compression unit; by reducing the number of use of the valve to control the flow of the refrigerant to reduce the production cost, as well as to minimize the malfunction that can occur when the valve overuse the compressor and applying it You can increase the reliability of the air conditioner.

Description

Multi-stage rotary compressor and air conditioner using it {MODULATION TYPE MULTI-STAGE 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 sectional view showing a saving mode operating state in the double rotary compressor of the present invention,

FIG. 5 is a sectional view taken along the line “II-II” of FIG. 4; FIG.

** 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: first discharge valve

37: first muffler 40: second compression unit

41: 2nd cylinder 42: lower bearing

43: second rolling piston 44: the second vane

45: vane spring 46: second discharge valve

47: second muffler 50: guide unit

51: first suction pipe 52: second suction pipe

53: branch pipe 60: control unit

61: first control valve (check valve) 62: second control valve (2-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, not only excessive costs are generated, but also complicated operation and there is a concern that the variable capacity of the compressor can not be made smoothly if any one valve malfunctions.

The present invention has been made in view of the above-described 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. And 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; It is connected to the drive unit, installed inside the casing, and receives the driving force from the drive unit, each rolling piston turning in the inner space of each cylinder presses with each vane in a linear motion to compress the refrigerant independently and compress A plurality of compression units for discharging the refrigerant to the sealed space of the casing through respective mufflers; A guide unit which connects a plurality of compression units to guide the refrigerant to each compression unit and selectively guides the refrigerant discharged from the muffler of either compression unit to a cylinder of the other compression unit; Attached to the guide unit so that a plurality of compression units perform compression strokes respectively, or guide or block refrigerant discharged from one compression unit to another compression unit to restrain or release the vanes of the other compression unit It provides a multi-stage rotary compressor comprising a; control unit for idling or normal operation of the compression unit.

In addition, when a refrigerant having a plurality of compression units and compressed and discharged from one of the compression units is supplied to the compression chamber of one of the compression units, the vanes are 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 and discharged from one 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, Figure 2 is a longitudinal cross-sectional view showing a power mode operating state in the double rotary compressor of the present invention, Figure 3 is a "I-I" front cross-sectional view of FIG. Figure 4 is a longitudinal sectional view showing a saving mode operation state in the double rotary compressor of the present invention, Figure 5 is a "II-II" front sectional view of FIG.

As shown in the drawing, the double rotary compressor according to the present invention includes a casing 10 for forming a closed space therein, a drive unit 20 for generating a driving force in the casing 10, and a drive unit ( A first compression unit 30 and a second compression unit 40 connected to each other to compress the refrigerant, and a guide unit 50 connecting the evaporator outlet of the refrigeration cycle with each compression unit to guide the flow of the refrigerant. And a control unit 60 mounted to 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 which will be described later so as to communicate the respective compression units 30 and 40 to 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). In this case, the driving unit 20 is preferably composed of 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, Opening and closing the first vane 35 which partitions the first internal space V1 into the first suction chamber and the first compression chamber, and the first discharge hole 32a which is formed in the upper bearing 32 so as to communicate with the first compression chamber. And a first discharge valve 36 and a first discharge valve 36 for controlling the discharge of the refrigerant discharged from the first compression chamber to be coupled to each other. It comprises a first muffler 37 provided on the bearing portion (32).

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.

In addition, the first vane 35 may not include a separate vane spring to be supported by the pressure of the gas filled in the inner space of the casing 10, but in some cases, the vane 35 may be restrained and released. By installing a vane spring (not shown) having a modulus of elasticity within a smooth range, it is possible to facilitate the initial startup during power operation.

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 vane spring 45 for allowing the vanes 44 to be pressed against the second rolling piston 43 and the second compression chamber communicated with one side of the lower bearing 42. 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 to be opened and closed, and a lower bearing 42 for accommodating the second discharge valve 46. It consists of the 2nd muffler 47 installed in ().

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 thereof, 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 41c 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. You may.

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. It consists of a branch pipe 53 which connects the 2nd muffler (or chamber) 47 of the unit 30 and 40 to the middle of the said 1st suction pipe 51.

The control unit 60 is installed in the middle of the first suction pipe 51, that is, upstream from the point where the first suction pipe 51 is in contact with the branch pipe 53, and is sucked by the evaporator through the first suction pipe 51. The first control valve 61 as a check valve to prevent the refrigerant from flowing back to the evaporator again, and the second control valve as a two-way valve installed in the middle of the branch pipe 53 to open and close according to the operation mode of the compressor. It consists of 62.

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 second control valve 62 appropriately according to the required capacity in the air conditioner to generate a large amount of cooling force or to operate the saving mode while operating in the power mode. Generates a small amount of cold power while performing.

For example, when driving in the power mode, as shown in FIGS. 2 and 3, the second control valve 62 is switched to an OFF state, so that the first compression unit 30 and the second compression unit 40 are turned off. Each compressed refrigerant is to be discharged to the inner space of the casing (10). Here, as the second control valve 62 is closed, the refrigerant of the accumulator (A) passes through the first control valve (61), and the cylinder (31) of the first compression unit (30) through the first suction pipe (51). Inhaled). 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 maintains a low pressure state, thereby eventually causing the first vane. 35 is maintained by the first rolling piston 34 while being supported by a high pressure refrigerant pressurizing the rear side. At the same time, the refrigerant sucked into the cylinder 41 of the second compression unit 40 through the second suction pipe 52 is compressed in the second compression unit 40 and compressed in the first compression unit 30. It is discharged together to generate 100% cold power.

On the other hand, when operating in the saving mode, as shown in FIGS. 4 and 5, the second control valve 62 is turned on, and a part of the refrigerant discharged from the second compression unit 40 is removed. 2 is introduced into the first suction pipe 51 through the control valve 62 and the branch pipe 53, the refrigerant flowing into the first suction pipe 51 is again the cylinder 31 of the first compression unit (30) Fill the interior space. 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. It is to generate cold power.

Meanwhile, when the double rotary compressor according to the present invention is applied to an air conditioner, a first control valve 61, which is a check valve, is installed in the first suction pipe 51 connecting the evaporator and the compressor, and the second compression unit 40 is first installed. It is possible to vary the capacity of the compressor by installing a second control valve 62, which is an on-off valve for branching to the suction pipe 51 and controlling the flow direction of the compressed refrigerant in the middle of the branch pipe 53. By simplifying the piping for varying the capacity of the compressor to increase the effective space inside the air conditioner, as well as reducing the number of valves used for this can reduce the production cost. 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.

The multi-stage rotary compressor according to the present invention and the air conditioner using the same include a check valve for preventing a suction pipe suction pipe backflow connected to the compression unit for changing the capacity, and the discharge side of the other compression unit to the refrigerant in the check valve downstream refrigerant guide tube. By connecting the circulation pipe and at the same time by installing an on-off valve for controlling the flow of the refrigerant in the middle of the refrigerant circulation pipe to configure the variable capacity of the compressor while constraining or releasing the vane of the compression unit for changing the capacity to a high-pressure refrigerant, By reducing the number of valves used to control the flow of refrigerant, not only can the production cost be lowered, but also the reliability of the compressor and the air conditioner applied to it can be improved by minimizing the malfunctions that may occur when the valve is overused.

Claims (11)

A casing which forms a sealed space therein; A driving unit built in the casing to generate a driving force; It is connected to the drive unit, installed inside the casing, and receives the driving force from the drive unit, each rolling piston turning in the inner space of each cylinder presses with each vane in a linear motion to compress the refrigerant independently and compress A plurality of compression units for discharging the refrigerant to the sealed space of the casing through respective mufflers; A guide unit which connects a plurality of compression units to guide the refrigerant to each compression unit and selectively guides the refrigerant discharged from the muffler of either compression unit to a cylinder of the other compression unit; Attached to the guide unit so that a plurality of compression units perform compression strokes respectively, or guide or block refrigerant discharged from one compression unit to another compression unit to restrain or release the vanes of the other compression unit Multi-stage rotary compressor comprising a; control unit for idling or normal operation of the compression 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; A multistage rotary compressor, comprising: a branch pipe connecting a discharge side of one compression unit and a suction side of another compression unit to guide the refrigerant compressed and discharged in one compression unit to a cylinder inlet of the other compression unit. The method of claim 2, The control unit is installed on one suction pipe to control the flow of the refrigerant and the first control valve, And a second control valve installed in the branch pipe to control the flow of the refrigerant. The method of claim 3, 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 4, wherein The first control valve is a multi-stage rotary compressor, characterized in that the check valve. The method of claim 4, wherein The second control valve is a multi-stage rotary compressor, characterized in that the two-way valve (2-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 7, wherein 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 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 a refrigerant having a plurality of compression units and compressed and discharged from one of the compression units is supplied to the compression chamber of one of the compression units, the vane is restrained according to the pressure difference between the front and rear ends, while the idler An air conditioner having the multi-stage rotary compressor of claim 1, wherein the refrigerant is compressed and discharged from the compression unit to block the supply of the refrigerant to the compression chamber of either of the compression units.

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