KR100677522B1 - Modulation apparatus for rotary compressor - Google Patents

Abstract

The present invention relates to a variable capacity apparatus of a rotary compressor, wherein a plurality of compression spaces are independently formed in a casing, and either of them is separated from the inside of the casing, so that a suction pressure and a discharge pressure are supplied crosswise. A plurality of cylinders provided with a plurality of vanes contacting each rolling piston while radially reciprocating in each cylinder, one of which is installed to be supported by the pressure of the back pressure space, and a pressure of the back pressure space. In this case, the compressor includes a vane-bound spring installed in the back pressure space such that the vane is spaced apart from the rolling piston to idle, and a back pressure switching unit for selectively supplying the suction pressure and the discharge pressure to the back pressure space. Not only facilitates variable capacity control and simplifies piping, but also When it is applied to, the mode can be easily changed to improve the comfort and energy saving and to prevent the interference with other pipes in advance to improve the assembly of the air conditioner and to reduce the number of valves to reduce the production cost.

Description

Capacity variable device of rotary compressor {MODULATION APPARATUS FOR ROTARY COMPRESSOR}

1 is a system diagram showing an example of a conventional variable displacement rotary compressor,

2A and 2B are schematic views showing a compression chamber area for normal operation and saving operation of a conventional variable displacement rotary compressor;

3 is a schematic diagram showing an example of the present invention of a variable displacement double type rotary compressor;

Figure 4 is a longitudinal sectional view showing a variable displacement double rotary compressor of the present invention;

Figures 5a and 5b is a cross-sectional view showing a variable capacity state during normal operation and saving operation of the variable displacement double rotary compressor of the present invention.

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

10: casing 20: electric mechanism part

30: first compression mechanism portion 40: second compression mechanism portion

41: 2nd cylinder 41a: 2nd vaneslit

41b: back pressure space 42: lower bearing

43: second rolling piston 44: the second vane

46: vane-bound spring 46: second discharge valve

47: second muffler 50: vane control unit

51: low pressure side connector 52: high pressure side connector

53: common side connecting pipe 54: back pressure switching valve

SP1, SP2: First and second gas suction pipes V1, V2: First and second compression space

The present invention relates to a variable capacity device of a rotary compressor and an air conditioner using the same. Particularly, the capacity of a rotary compressor using a tension spring to restrain the reciprocating motion of the vane by using a tension spring is used. It relates to a variable device and an air conditioner using the same.

In general, a rotary compressor is mainly applied to an air conditioner such as an air conditioner. Recently, as the function of the air conditioner is diversified, the rotary compressor also requires a product that can vary in capacity. 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 variable technology by appropriate ring for exclusion" which changes the volume of the compression chamber by bypassing a part of the refrigerant gas compressed in the cylinder to the outside of the cylinder (hereinafter, excluded volume). Abbreviated as switching technology).

1 is a system diagram showing an example of a conventional variable displacement rotary compressor, Figures 2a and 2b is a schematic diagram showing the compression chamber area for the normal operation and the saving operation of the conventional variable displacement rotary compressor.

As shown in the drawing, the conventional variable displacement rotary compressor forms a bypass hole 1a of the cylinder so that a part of the refrigerant compressed in the middle of the compression space of the cylinder 1 can be bypassed according to the operation state of the compressor. The bypass pipe P1 is connected to the bypass hole 1a to the outside of the casing 2, and is piped from the end of the bypass pipe P1, and one end thereof is discharged from the casing 2 and the condenser ( 3) connecting to the discharge side connecting pipe (P3) in the middle of the gas discharge pipe (P2) for connecting while the other end is the suction side connecting pipe in the middle of the gas suction pipe (P4) connecting the evaporator (4) and the accumulator (5) It is connected to (P5). In addition, a discharge side valve V1 and a suction side valve V2 are respectively provided in the middle of the discharge side connecting pipe P3 and the suction side connecting pipe P5, and at the inlet side end of the bypass pipe P1. The bypass valve V3 is provided to open and close the bypass hole 1a of the cylinder 1 in accordance with the opening and closing of the discharge side valve V1 and the suction side valve V2.

In the drawings, reference numeral 6 denotes a rotating shaft, 7 a rolling piston, and 8 a vane.

When the compressor operates normally in the conventional variable displacement rotary compressor as described above, a part of the refrigerant discharged to the gas discharge pipe P2 is discharged as the discharge valve V1 of FIG. 1 is opened and the suction valve V2 is closed. The high pressure refrigerant is introduced into the bypass pipe P1 along the solid arrow, and the high pressure refrigerant pushes the bypass valve V3 to block the bypass hole 1a of the cylinder 1 as shown in FIG. 2A. ) A series of processes that are discharged to the gas discharge pipe (P2) is discharged while all the refrigerant sucked into the compression space is compressed.

On the other hand, when the compressor performs the saving operation, as the discharge valve V1 of FIG. 1 is closed and the suction valve V2 is opened, the pressure back side of the bypass valve V3 becomes the suction pressure environment, as shown in FIG. 2B. The bypass valve V3 is pushed to open the bypass hole 1a, and a part of the refrigerant compressed in the compression space through the open bypass hole 1a is connected to the suction side connection pipe P5 along the dotted arrow of FIG. 1. By bypassing to the accumulator 5 through only a portion of the refrigerant sucked into the compression space of the cylinder 1 was compressed and discharged.

However, the variable capacity device of the conventional rotary compressor as described above has a problem in that the refrigeration capacity decrease rate is small and the efficiency decreases as the resistance is increased when gas is bypassed during the saving operation by separately installing the bypass circuit on the side of the cylinder. .

In addition, as the bypass pipe P2, the discharge side connecting pipe P3, and the suction side connecting pipe P5 are installed outside the compressor casing 2 and connected to the air conditioning pipe, it is difficult to assemble the air conditioning pipe. In addition, since the discharge side valve (V1) and the suction side valve (V2) must be separately installed in the pipe, there is a problem in that the number of parts increases and the cost increases.

The present invention has been made in view of the problems of the conventional variable capacity of the rotary compressor as described above, to provide a variable capacity device of a rotary compressor that can increase the efficiency by increasing the rate of refrigeration capacity reduction during saving operation. There is this.

Another object of the present invention is to provide a variable capacity device of a rotary compressor that can easily and simply configure a variable capacity device of a compressor, as well as reduce production costs by reducing the number of parts.

In order to achieve the object of the present invention, a plurality of compression spaces are formed independently of the inside of the casing, one of which is separated from the inside of the casing is provided with a plurality of back pressure space so that the suction pressure and the discharge pressure cross-supplied cylinder; A plurality of vanes disposed in contact with each rolling piston while radially reciprocating in each cylinder, one of which is installed to be supported by the pressure of the back pressure space; A vane confinement spring installed in the back pressure space so that the vane is idle when the pressure in the back pressure space is a suction pressure; And a low pressure side connecting tube communicating at the suction side of the cylinder, a high pressure side connecting tube communicating at the discharge side of the cylinder, and a low pressure side connecting tube and a high pressure side connecting tube alternately connected to communicate with the back pressure space of the cylinder. A back pressure switching unit composed of a common pressure connector, a low pressure side connector and a high pressure side connector, and a back pressure switching valve configured to alternately connect the common side connector to both side connectors by installing at a connection point of the common side connector; It provides a variable capacity device of a rotary compressor including.

EMBODIMENT OF THE INVENTION Hereinafter, the variable capacity apparatus of the rotary compressor by this invention is demonstrated in detail based on one Example shown in an accompanying drawing.

Figure 3 is a schematic diagram showing an example of the present invention variable displacement double type rotary compressor, Figure 4 is a longitudinal sectional view showing a variable displacement double type rotary compressor of the present invention, Figures 5a and 5b is a normal operation of the variable displacement double rotary compressor of the present invention. This is a cross sectional view showing a variable capacity state for saving operation.

As shown in the drawing, the double rotary compressor according to the present invention includes a casing 10 for communicating a plurality of gas suction pipes SP1 and SP2 and one gas discharge pipe DP and an upper side of the casing 10. And a first compression mechanism 30 and a second compression mechanism 40 installed under the casing 10 to compress the refrigerant by the rotational force generated by the transmission mechanism 20. And the second compression while connecting the plurality of gas suction pipes SP1 to SP2 and the gas discharge pipe DP to switch the back surface of the second vane 44 to a high pressure atmosphere or a low pressure atmosphere. The mechanism part 40 is comprised by the back pressure switching unit 50 which makes a normal operation or saving operation.

The electric drive unit 20 has a stator 21 fixed to the inside of the casing 10 by applying constant speed driving or inverter driving to apply power from the outside, and has a predetermined gap inside the stator 21. Rotor 22 that rotates while interacting with the stator 21, and the rotating shaft coupled to the rotor 22 to transmit the rotational force to the first compression mechanism 30 and the second compression mechanism 40 It consists of 23.

The first compression mechanism 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 compression space V1. While rotating the upper bearing plate (hereinafter, the upper bearing) 32 and the intermediate bearing plate (hereinafter, the middle bearing) 33 for supporting the rotating shaft 23 in the radial direction, and the upper eccentric portion of the rotating shaft 23 The first cylinder (34) and the first rolling piston (34) for compressing the refrigerant while pivoting in the first compression space (V1) of the first cylinder (31) and the outer circumferential surface of the first rolling piston (34). A first vane 35 and a first vane, each of which is radially movable to 31 to partition the first internal space V1 of the first cylinder 31 into a first suction chamber and a first compression chamber, respectively; It is provided near the center of the vane branch spring 36 made of the compression spring and the upper bearing 32 so as to elastically support the rear side of the 35). A first discharge valve 37 and a first discharge valve 37 which are coupled to the front end of the first discharge port 32a so as to be opened and closed to regulate the discharge of the refrigerant gas discharged from the compression chamber of the first internal space V1. It is composed of a first muffler 38 having an inner volume to accommodate the upper bearing 32.

The second compression mechanism 40 is formed in an annular shape to cover the second cylinder 41 installed below the first cylinder 31 in the casing 10, and both the upper and lower sides of the second cylinder 41. 2 to form a compression space (V2) rotatably coupled to the intermediate bearing 33 and the lower bearing 42 and the lower eccentric portion of the rotating shaft 23 to support the rotating shaft 23 in the radial and axial directions The second cylinder 41 to be pressed or spaced apart from the second rolling piston 43 that compresses the refrigerant while turning in the second compression space V2 of the second cylinder 41 and the outer circumferential surface of the second rolling piston 43. A second vane 44 and a second vane configured to radially move to the second vane 44 to partition or communicate the second compression space V2 of the second cylinder 41 to the second suction chamber and the second compression chamber, respectively. A vane-bound spring 45 made of a tensioning coil spring so as to rest on the second vane 44 at the rear side of the back 44; A second discharge valve 46 coupled to the front end of the second discharge port 42a provided near the center of the 42 to control the discharge of the refrigerant gas discharged from the second compression chamber, and a second discharge valve ( It is composed of a second muffler 47 having a predetermined internal volume to accommodate the 46 and coupled to the lower bearing 42.

As shown in FIG. 4, the second cylinder 41 forms a second vane slit 41a on one side of the inner circumferential surface of the second compression space V2 such that the second vanes 44 reciprocate in the radial direction. In addition, a second suction port (not shown) for guiding the refrigerant into the second compression space V2 is radially formed at one side of the second vane slit 41a, and the refrigerant is formed at the other side of the second vane slit 41a. A second discharge guide groove (not shown) discharged into the casing 10 is formed to be inclined in the axial direction. In addition, the radially back side of the second vane slit 41a communicates with the common side connecting pipe 53 of the vane control unit 50, which will be described later, so as to achieve a suction pressure or a discharge pressure atmosphere on the rear side of the second vane 44. A back pressure space 41b having a predetermined internal volume is formed.

The back pressure space 41b communicates with the common side connecting pipe 53 of the vane control unit 50, which will be described later, even if the second vane 44 is completely retracted and stored in the second vane slit 41a. The rear surface of the 44 is formed to have a predetermined internal volume so as to form a pressure surface with respect to the pressure supplied through the common side connecting pipe 53 described above.

Here, the second cylinder 41 may be formed to have the same volume as or different from the volume of the first cylinder 31 and the compression space V1 as necessary. For example, in the case where the two cylinders 31 and 41 have the same volume, if one cylinder is saved, the compressor performs only 50% of the volume of the other cylinder. In the case where the volume of 41 is formed differently, the compressor performance is varied by the ratio of the volume of the remaining cylinders in normal operation.

The vane constrained spring 45 is formed of a tension coil spring as described above, the front end of which is fixed to the spring groove 44a provided at the rear of the second vane 44 while the rear end thereof is the second cylinder. It hangs on the spring groove 41c provided in the back pressure space 41b of 41, and is fixed. In addition, the vane constrained spring 45 may be formed smaller than the diameter of the back pressure space 41b, but in some cases, may be larger than the diameter of the back pressure space 41b. In this case, the spring escape grooves 33a and 42b that can accommodate the vane constraining springs 45 are respectively formed on the corresponding surfaces of the intermediate bearing 33 and the lower bearing 42 constituting the back pressure space 41b. It is preferable to form a forge.

The back pressure switching unit 50 communicates with the low pressure side connecting pipe 51 communicating with the suction side of the second cylinder 41, the discharge side of the second cylinder 41, more precisely with the internal space of the casing 10. The common side connection which connects to the high pressure side connection pipe 52, the low pressure side connection pipe 51, and the high pressure side connection pipe 52, respectively, and communicates with the back pressure space 41b of the said 2nd cylinder 41 mentioned above. It is installed at the connection point of the pipe 53, the low-pressure side connecting pipe 51, the high-pressure side connecting pipe 52 and the common side connecting pipe 53, the above-mentioned common side connecting pipe 53 is connected to both side connecting pipe 51 It consists of a back pressure switching valve 54, which is a three-way valve or a pilot valve connected alternately to the (52).

The low pressure side connecting pipe 51 is connected between the suction side of the second cylinder 41 and the inlet side gas suction tube or outlet side gas suction tube (second gas suction tube) SP2 of the accumulator 5.

The high pressure side connecting pipe 52 may communicate with the lower half of the casing 10 so that the oil inside the casing 10 may directly flow into the back pressure space 41b, but in some cases, the gas discharge pipe DP You can also connect in the middle of the branch.

In the drawings, the same reference numerals are given to the same parts as in the prior art.

In the drawings, reference numeral 3 denotes a condenser and 4 denotes an evaporator.

Effects of the variable capacity device of the rotary compressor of the present invention as described above are as follows.

That is, when the rotor 22 is rotated by applying power to the stator 21 of the power mechanism unit 20, the rotating shaft 23 rotates together with the rotor 22 to increase the rotational force of the power mechanism unit 20 first. It is transmitted to the compression mechanism unit 30 and the second compression mechanism unit 40, and the first compression mechanism unit 30 and the second compression mechanism unit 40 are normally operated together according to the required capacity of the air conditioner to generate a large amount of cooling force. Alternatively, only the first compression mechanism unit 30 performs normal operation, and the second compression mechanism unit 40 performs the saving operation to generate a small capacity cooling power.

In this case, when the compressor or the air conditioner applying the same operates in normal operation, as shown in FIG. 5A, the back pressure switching valve 54 operates to discharge the high pressure side connecting pipe 52 and the common side connecting pipe 53. A portion of the high pressure refrigerant gas is introduced into the back pressure space 41b of the second cylinder 41 so that the second vane 44 is pressed against the second rolling piston 43 by being pushed by the pressure of the back pressure space 41b. While maintaining, the refrigerant gas flowing into the second compression space V2 is normally compressed and discharged. In this case, the force due to the pressure of the back pressure space 41b of the second cylinder 41 is greater than the sum of the force of the restoring force of the vane constraining spring 45 and the force of the pressure of the compression space of the second cylinder 41. The second vane 44 is maintained in a pressed state to the outer circumferential surface of the second rolling piston 43. In this way, the first vane 35 and the second vane 44 are press-contacted to the respective rolling pistons 34 and 43 to transfer the first compression space V1 and the second compression space V2 into the suction chamber and the compression chamber. By compressing and discharging the entire refrigerant sucked into each suction chamber while partitioning, the compressor or the air conditioner applying the same is operated 100%.

On the other hand, in the case of saving operation such as when the compressor or the air conditioner to which the air is applied, the three-way valve 54 operates as opposed to the normal operation as shown in FIG. Part of the low-pressure refrigerant gas drawn into the second cylinder 41 by communicating with the connection pipe 53 is introduced into the back pressure space 41b of the second cylinder 41 so that the second vane 44 has a second compression space. The suction chamber and the compression chamber of the second compression space V2 communicate with each other by being pushed by the pressure of V2 to be inward of the second vane slit 41a so that the refrigerant gas sucked into the second compression space V2 cannot be compressed. do. At this time, the force due to the pressure in the back pressure space (41b) is less than the combined force of the restoring force of the vane constraining spring (45) and the pressure of the compression space of the second cylinder (41) linear movement of the second vane (44) Will be bound. In this way, as the compression chamber and the suction chamber of the second cylinder 41 communicate with each other, the entire refrigerant sucked into the suction chamber of the second cylinder 41 is not compressed and moves back to the suction chamber along the trajectory of the rolling piston 43. 2, the compression mechanism 40 does not work, so the compressor or the air conditioner applying the same operates only as much as the capacity of the first compression mechanism 30.

The variable capacity apparatus of the rotary compressor according to the present invention forms a back pressure space in which a suction pressure or a discharge pressure atmosphere is formed at a rear side of the second vane and restrains the second vane when the suction pressure atmosphere is formed in the back pressure space. By installing the tension coil spring to idle, not only can the capacity change control of the compressor be simplified and the piping can be simplified, but also the mode can be easily changed when the compressor is applied to the air conditioner, improving the comfort and energy saving and other piping. By preventing interference with the air conditioner can improve the assembly of the air conditioner and reduce the number of valves can reduce the production cost.

Claims (5)

delete A plurality of cylinders independently forming a plurality of compression spaces in the casing, one of which has a back pressure space separated from the inside of the casing so as to cross-feed the suction pressure and the discharge pressure; A plurality of vanes disposed in contact with each rolling piston while radially reciprocating in each cylinder, one of which is installed to be supported by the pressure of the back pressure space; A vane confinement spring installed in the back pressure space so that the vane is idle when the pressure in the back pressure space is a suction pressure; And The low pressure side connecting tube communicating at the suction side of the cylinder, the high pressure side connecting tube communicating at the discharge side of the cylinder, and the low pressure side connecting tube and the high pressure side connecting tube are alternately connected to communicate with the back pressure space of the cylinder. A back pressure switching unit comprising a back pressure switching valve configured to alternately connect the common side connecting pipe to both side connecting pipes by installing at a connection point of the side connection pipe, the low pressure side connector, the high pressure side connector, and the common side connector; Variable capacity device of the rotary compressor, including. The method of claim 2, The low pressure side connecting pipe is installed between the suction side and the gas suction pipe of the cylinder to connect to the inlet side or the outlet side of the accumulator separating liquid refrigerant and gas refrigerant, and the high pressure side connecting pipe is connected in the middle of the gas discharge pipe. A variable capacity device of a rotary compressor, characterized in that connected in communication with the inner space of the casing. The method of claim 2, A vane constraining spring is fixedly coupled to both ends of the vane and the bearing plate or cylinder corresponding to the back of the vane, respectively. The method of claim 4, wherein A variable capacity device of a rotary compressor, characterized in that the bearing plate to cover the back pressure space to form a spring escape groove negatively to accommodate the vane-bound spring.

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