JP2013007358A - Multi-cylinder rotary compressor and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high-performance, multi-cylinder rotary compressor that has two compression mechanisms, each on both sides of an electric motor.SOLUTION: The multi-cylinder rotary compressor 2 includes: a sealed case 9; one electric motor 13 housed in the sealed case 9; two compression mechanisms 14 and 15 housed in the sealed case 9, each disposed on the both sides of the electric motor 13, and coupled to the electric motor 13 to compress working fluid; two accumulators 7 and 8, each disposed near each of the compression mechanisms 14 and 15 on the outer periphery of the sealed case 9, and connected through a suction pipe 12, respectively, to the compression mechanisms 14 and 15 adjacent to each of the accumulators.

Description

  Embodiments described herein relate generally to a multi-cylinder rotary compressor and a refrigeration cycle apparatus using the multi-cylinder rotary compressor.

  In a multi-cylinder rotary compressor that compresses a gas refrigerant circulating in the refrigeration cycle apparatus, the multi-cylinder rotary compressor has an electric motor part and two compression mechanism parts arranged on both sides of the electric motor part, and the electric motor part and the compression mechanism part, Is known in a sealed case (see Patent Document 1 below). In the multi-cylinder rotary compressor described in Patent Document 1, a low-pressure gas refrigerant is sucked into a compression mechanism and compressed, and the compressed high-pressure gas refrigerant is discharged into a sealed case. And the high-pressure gas refrigerant discharged in the sealed case is discharged to the condenser.

Japanese Utility Model Publication No. 48-105105

  Although not shown and not mentioned in Patent Document 1, in the multi-cylinder rotary compressor of the type described in Patent Document 1, a low-pressure gas refrigerant is sucked into the compression mechanism. The accumulator is used to remove the liquid refrigerant contained in the gas refrigerant.

  If an accumulator is provided in the multi-cylinder rotary compressor disclosed in Patent Document 1, it is conceivable to arrange one accumulator on the outer peripheral side of the sealed case and at an intermediate position between the two compression mechanisms. The accumulator and the two compression mechanisms are connected by a suction pipe through which a gas refrigerant flows.

  In that case, the suction pipe connecting the accumulator and the compression mechanism is lengthened, the flow resistance when refrigerant flows through the suction pipe is increased, and the generated pressure loss is increased, resulting in the performance of the multi-cylinder rotary compressor. Decreases.

  Regarding the length dimension of the suction pipe connecting the accumulator and the compression mechanism section, there is a length dimension that allows the multi-cylinder rotary compressor to operate most efficiently in relation to the intake frequency of the compression mechanism section. However, as the length dimension of the suction pipe becomes longer, it becomes difficult to adjust the length dimension of the suction pipe so that the multi-cylinder rotary compressor can be operated most efficiently.

  An object of an embodiment of the present invention is to provide a high-performance multi-cylinder rotary compressor having two compression mechanisms on both sides of an electric motor unit, and a refrigeration cycle apparatus using the multi-cylinder rotary compressor. It is.

  According to the multi-cylinder rotary compressor of the embodiment, the hermetic case, one electric motor unit accommodated in the hermetic case, the inner case accommodated in both sides of the electric motor unit, and connected to the electric motor unit Two compression mechanism parts for compressing the working fluid, and arranged on the outer peripheral side of the sealed case in close proximity to each compression mechanism part, and individually connected to the compression mechanism part on the side located in close proximity via the suction pipe Two accumulators.

It is a schematic diagram which shows the refrigerating cycle of the air conditioner which is the refrigerating cycle apparatus of 1st Embodiment. 1 is a side view of a multi-cylinder rotary compressor according to a first embodiment. 1 is a front view of a multi-cylinder rotary compressor according to a first embodiment. It is a longitudinal front view of the multi-cylinder rotary compressor of the first embodiment. It is a vertical front view of the multi-cylinder rotary compressor of 2nd Embodiment. It is a vertical front view of the multi-cylinder rotary compressor of 3rd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. As shown in the refrigeration cycle diagram of FIG. 1, an air conditioner 1 that is a refrigeration cycle device functions as a condenser during a cooling operation and a multi-cylinder rotary compressor 2, a four-way valve 3, and evaporates during a heating operation. Outdoor heat exchanger 4 that is a heat source side heat exchanger that functions as a heat exchanger, expansion device 5, and indoor heat exchange that is a utilization side heat exchanger that functions as an evaporator during cooling operation and as a condenser during heating operation It is formed by communicating with the vessel 6 in a cycle. The multi-cylinder rotary compressor 2 is provided with two accumulators 7 and 8, and these accumulators 7 and 8 are formed in the same structure.

  In this air conditioner 1, during cooling operation, high-pressure gas refrigerant, which is a working fluid, is discharged from the multi-cylinder rotary compressor 2 and flows as indicated by solid arrows, and outdoor heat exchange is performed via the four-way valve 3. Flows into the condenser (condenser) 4 and is condensed by exchanging heat with the outside air in the outdoor heat exchanger 4. The condensed refrigerant (liquid refrigerant) flows into the indoor heat exchanger (evaporator) 6 via the expansion device 5 and evaporates by exchanging heat with indoor air in the indoor heat exchanger 6. Cool the room air. The evaporated refrigerant (gas refrigerant) is sucked into the multi-cylinder rotary compressor 2 via the four-way valve 3.

  On the other hand, at the time of heating operation, high-pressure gas refrigerant is discharged from the multi-cylinder rotary compressor 2 and flows as indicated by the broken arrow, and flows into the indoor heat exchanger (condenser) 6 via the four-way valve 3. Then, heat is exchanged with room air in the indoor heat exchanger 6 to condense and heat the room air. The condensed refrigerant flows into the outdoor heat exchanger (evaporator) 4 via the expansion device 5 and evaporates by exchanging heat with outdoor air in the outdoor heat exchanger 4. The evaporated gas refrigerant is sucked into the multi-cylinder rotary compressor 2 via the four-way valve 3.

  As described above, the cooling operation or the heating operation of the air conditioner 1 is continued by continuing the circulation of the refrigerant.

  As shown in FIGS. 2 and 3, the multi-cylinder rotary compressor 2 includes a cylindrical sealing case 9 installed in a landscape orientation, and a cylindrical configuration installed in a portrait orientation on the outer peripheral side of the sealing case 9. The two accumulators 7 and 8 are provided. As will be described later, the sealed case 9 accommodates a compression mechanism that compresses the gas refrigerant and an electric motor that drives the compression mechanism. In the sealed case 9, lubricating oil for lubricating the sliding portion of the compression mechanism is stored.

As shown in FIG. 2, the accumulators 7 and 8 are fixed by welding to the outer peripheral side of the sealed case 9 using a connecting piece 10. As shown in FIGS. 2 and 3, an inflow path 11 through which heat-exchanged gas refrigerant flows is provided at the upper part of the accumulators 7 and 8. From the lower part of the accumulators 7 and 8, suction pipes 12 for supplying the gas refrigerant flowing into the accumulators 7 and 8 to the compression mechanism portion in the sealed case 9 extend. The one end side located in the accumulators 7 and 8 in the suction pipe 12 extends and opens to the upper end side in the accumulators 7 and 8 as shown by the broken line in FIG. The refrigerant is stored in the accumulators 7 and 8, and only the gas refrigerant from which the liquid refrigerant has been removed is supplied to the compression mechanism. The other end of the suction pipe 12 is connected to the suction side of the compression mechanism.

  The structure inside the sealed case 9 will be described with reference to FIG. In the sealed case 9, there is housed one electric motor part 13 arranged at the center part in the longitudinal direction and two compression mechanism parts 14, 15 arranged on both sides of the electric motor part 13. The motor unit 13 is provided with two drive shafts 16 and 17 that rotate about the center line. The motor unit 13 and one compression mechanism unit 14 are connected via the drive shaft 16, and the motor unit 13 and the other compression unit are compressed. The mechanism unit 15 is connected via a drive shaft 17. The basic configuration of the two compression mechanisms 14 and 15 is the same, and the low-pressure gas refrigerant sucked from the accumulators 7 and 8 via the suction pipe 12 is compressed to obtain high-pressure and high-temperature gas refrigerant. Of the accumulators 7, 8 welded to the outer peripheral side of the sealed case 9, one accumulator 7 is disposed close to one compression mechanism 14, and the other accumulator 8 is connected to the other compression mechanism 15. They are placed close together.

  The electric motor unit 13 includes a stator 18 and a rotor 19. The stator 18 is fixed to the inner peripheral portion of the hermetic case 9 by adhesion, press fitting, or the like, so that the rotor 19 can rotate inside the stator 18. Has been inserted. Drive shafts 16 and 17 are fixed to the center of the rotor 19. The drive shafts 16 and 17 are each provided with two eccentric portions 20 and 21, and these eccentric portions 20 and 21 are arranged with a phase of 180 ° along the rotation direction of the drive shafts 16 and 17.

  One compression mechanism portion 14 is fixed in the sealed case 9 by a fixing member (not shown) and has two compression portions 22 and 23. The two compression parts 22 and 23 are respectively a cylinder 25 having a cylinder chamber 24, and a roller accommodated in the cylinder chamber 24 so as to be eccentrically rotatable while a part of the outer peripheral surface is brought into contact with the inner peripheral surface of the cylinder chamber 24. 26, and a slidable blade 27 that is provided in the cylinder 25 and bisects the inside of the cylinder chamber 24 along the rotation direction of the roller 26 by bringing the tip portion into contact with the outer peripheral surface of the roller 26. A spring 28 is disposed on the rear end side of the blade 27, and this spring 28 urges the blade 27 in a direction in which a tip portion thereof abuts on the outer peripheral surface of the roller 26. Eccentric portions 20 and 21 of the drive shaft 16 are located in the cylinder chamber 24, and a roller 26 is fitted to the outer peripheral portions of these eccentric portions 20 and 21. Accordingly, the two rollers 26 are arranged with a phase of 180 ° along the rotation direction of the drive shaft 16.

  A portion between the two compression portions 22 and 23 on one end face of the cylinder 25 is closed by a partition plate 29. The other end face of the cylinder 25 is closed by a bearing 30 that rotatably supports the drive shaft 16.

  A discharge muffler 31 for discharging the gas refrigerant compressed by the compression mechanism unit 14 is provided on the outer peripheral side of the compression mechanism unit 14, and the gas in the discharge muffler 31 is disposed between the discharge muffler 31 and the bearing 30. A discharge gap 32 is formed as a discharge portion for discharging the refrigerant into the sealed case 9. Further, the compression mechanism section 14 is provided with an oil supply section 33 that supplies the lubricating oil stored in the sealed case 9 to the inside of the compression mechanism section 14. The supply of the lubricating oil by the oil supply unit 33 is performed, for example, by sucking the lubricating oil from a minute gap portion using a differential pressure between the cylinder chamber 24 and the sealed case 9. A discharge pipe 34 that discharges the gas refrigerant in the sealed case 9 to the outside of the sealed case 9 is connected to a position above the compression mechanism portion 14 in the sealed case 9.

The other structure of the other compression mechanism unit 15 is the same as that of the compression mechanism unit 14, and parts having the same configuration are denoted by the same reference numerals and description thereof is omitted. Here, a different part from the compression mechanism part 14 is demonstrated. The cylinders 25 of the two compression parts 22, 23 in the compression mechanism part 15 accommodate the rear end side of the blade 27 so as to be slidable and are airtight with respect to the space in the sealed case 9. A chamber 35 is formed. The partition plate 29 located between the two compression portions 22 and 23 is formed with a communication path 36 that communicates the blade back chamber 35 of one compression portion 22 with the blade back chamber 35 of the other compression portion 23. Yes. Further, in each blade back chamber 35, when the blade 27 is in a cylinder resting state in which the tip portion is separated from the outer peripheral surface of the roller 26 and the gas refrigerant is not compressed, the blade 27 is adsorbed. A permanent magnet 37 for holding is provided. The permanent magnet 37 may be integrally formed across the two blade back chambers 35.

  Further, the compression mechanism unit 15 is provided with a working pressure switching unit 38 that switches the magnitude of the pressure of the gas refrigerant acting on the blade back chamber 35. The working pressure switching unit 38 includes a three-way valve 39, a high-pressure introduction pipe 40 having one end connected to the bottom of the sealed case 9 and the other end connected to the three-way valve 39, and one end connected to the suction pipe 12 of the accumulator 7. The other end is constituted by a low pressure introduction pipe 41 connected to the three-way valve 39 and a pressure introduction pipe 42 having one end connected to the three-way valve 39 and the other end connected to the blade back chamber 35. When the three-way valve 39 is switched and the pressure of the gas refrigerant compressed in the compression mechanism 14 that is the discharge-side working fluid and discharged into the sealed case 9 is applied to the blade back chamber 35 via the lubricating oil, The blade 27 is energized, the tip of the energized blade 27 is brought into contact with the outer peripheral surface of the roller 26, and the compression mechanism unit 15 enters an operation state in which the gas refrigerant is compressed. On the other hand, when the three-way valve 39 is switched and the pressure of the gas refrigerant in the accumulator 7 before being compressed by the compression mechanism 14 that is the suction side working fluid is applied to the blade back chamber 35, the tip of the blade 27 is moved to the roller 26. The force that urges the blade 27 in the direction of contact with the outer peripheral surface of the roller 26 is lost, the tip portion of the blade 27 is separated from the outer peripheral surface of the roller 26, and the compression mechanism unit 15 is in a cylinder resting state in which the gas refrigerant is not compressed. Become. The blade 27 having the tip portion separated from the outer peripheral surface of the roller 26 is held by the permanent magnet 37 so as to be fixed at a position where the tip portion is separated from the roller 26.

  In the sealed case 9, two baffle bodies 43 that divide the sealed case 9 into three spaces are provided. These baffle bodies 43 are formed in a ring shape and are fitted to the outer peripheral portion of the bearing 30 positioned between the motor portion 13 and the compression mechanism portions 14 and 15, and the motor portion 13 is accommodated in the sealed case 9. It is divided into one electric motor unit accommodating space 44 and two compression mechanism unit accommodating spaces 45 and 46 in which the compression mechanism units 14 and 15 are accommodated. The discharge gap 32 of the discharge muffler 31 opens into the motor unit accommodation space 44. In the baffle body 43, the gas refrigerant and the lubricating oil move between the electric motor unit accommodation space 44 and the compression mechanism unit accommodation spaces 45, 46, and between the electric motor unit accommodation space 44 and the compression mechanism unit accommodation spaces 45, 46. The electric motor unit accommodating space 44 is partitioned so as to generate a differential pressure that is higher than the compression mechanism unit accommodating spaces 45 and 46.

  Returning to FIG. 3, a communication path 47 is connected between the bottoms of the two accumulators 7 and 8. Further, a communication path 48 is connected between the suction pipes 12 of the two accumulators 7 and 8 and located below the cylinder chamber 24. By connecting the communication passage 47 between the bottoms of the accumulators 7 and 8, the liquid refrigerant accumulated in the accumulators 7 and 8 can move between the accumulators 7 and 8 through the communication passage 47. . Further, when the communication passage 48 is connected between the suction pipes 12 of the accumulators 7 and 8, the compression mechanism portion 15 is in a cylinder resting state, and lubricating oil is accumulated in the cylinder chamber 24 of the compression mechanism portion 15. Then, the lubricating oil passes through the communication passage 48 and is sucked into the compression mechanism portion 14 in the operating state.

In such a configuration, when the air conditioner 1 is operated, the electric motor unit 13 is driven to rotate the drive shafts 16 and 17, and the rollers 26 fitted to the eccentric portions 20 and 21 of the drive shafts 16 and 17 are provided. The compression mechanism portions 14 and 15 are eccentrically rotated in the cylinder chamber 24. As the roller 26 rotates eccentrically in the cylinder chamber 24, the low-pressure gas refrigerant is sucked into the cylinder chamber 24 from the accumulators 7 and 8 via the suction pipe 12 and compressed.

  The gas refrigerant that has become high pressure by being compressed in the cylinder chamber 24 is discharged from the cylinder chamber 24 into the discharge muffler 31, and further discharged into the motor unit accommodation space 44 from the discharge gap 32 of the discharge muffler 31. . The high-pressure gas refrigerant discharged into the electric motor unit accommodation space 44 passes through a partition portion formed by the baffle body 43, moves into the compression mechanism unit accommodation spaces 45, 46, and moves into the compression mechanism unit accommodation spaces 45, 46. The high-pressure gas refrigerant thus discharged is discharged out of the sealed case 9 from the discharge pipe 34.

  Here, in the multi-cylinder rotary compressor 2, the motor unit 13 and the two compression mechanism units 14 and 15 located on both sides of the motor unit 13 are accommodated in the sealed case 9, The two accumulators 7 and 8 which are located are arranged close to the compression mechanism parts 14 and 15, and the accumulator 7 and the compression mechanism part 14 which are located close to each other, and the accumulator 8 and the compression mechanism part 15 are respectively suction pipes. 12 is connected. For this reason, the length dimension of the suction pipe 12 can be shortened, whereby the flow resistance when the gas refrigerant flows through the suction pipe 12 can be reduced, and the generated pressure loss can be reduced to reduce the number of cylinders. The performance of the rotary compressor 2 can be improved.

  Further, regarding the length dimension of the suction pipe 12 that connects the accumulators 7 and 8 and the compression mechanism parts 14 and 15, the multi-cylinder rotary compressor 2 is most affected by the intake frequency of the compression mechanism parts 14 and 15. There are length dimensions that can be operated efficiently. In the multi-cylinder rotary compressor 2, the length of the suction pipe 12 can be shortened. Therefore, the length of the suction pipe 12 is adjusted so that the multi-cylinder rotary compressor 2 can be operated most efficiently. It becomes possible.

  Furthermore, when an accumulator is used in the compressor, the required volume in the accumulator is determined by the cylinder volume of the compressor. In this multi-cylinder rotary compressor 2, since the two accumulators 7 and 8 are used, the volume of each accumulator 7 and 8 can be halved compared to the case where one accumulator is used. , 8 can be reduced in size. When the two accumulators 7 and 8 that are reduced in size are arranged on the side of the sealed case 9, the multi-cylinder rotary type is used as compared with the case where one large accumulator is arranged on the side of the sealed case 9. The width dimension in the direction orthogonal to the longitudinal direction of the sealed case 9 in the compressor 2 can be reduced. Thereby, the multi-cylinder rotary compressor 2 can be reduced in size, and the installation area of the multi-cylinder rotary compressor 2 can be reduced.

  Next, as shown in FIG. 4, two baffle bodies 43 are provided in the sealed case 9 to divide the sealed case 9 into three parts, that is, an electric motor unit storage space 44 and compression mechanism unit storage spaces 45 and 46. Then, the gas refrigerant compressed in the compression mechanism portions 14 and 15 is discharged into the electric motor unit accommodation space 44. The baffle body 43 moves the gas refrigerant and the lubricating oil between the motor unit housing space 44 and the compression mechanism unit housing spaces 45 and 46, and between the motor unit housing space 44 and the compression mechanism unit housing spaces 45 and 46. The motor unit housing space 44 is partitioned so as to generate a differential pressure that is higher than the compression mechanism housing spaces 45 and 46. For this reason, when the multi-cylinder rotary compressor 2 is operated, the pressure in the motor unit housing space 44 becomes higher than the pressure in the compression mechanism unit housing spaces 45 and 46, and the lubricating oil in the sealed case 9 is retained in the motor unit housing space. The amount of lubricating oil that moves from 44 into the compression mechanism housing spaces 45 and 46 and is stored in the motor housing space 44 is reduced. As a result, the rotor 19 rotating in the motor unit accommodating space 44 can be prevented from being immersed in the lubricating oil, and the rotational resistance of the rotor 19 immersed in the lubricating oil is increased, resulting in a multi-cylinder rotary type. It can prevent that the performance of the compressor 2 falls. On the other hand, since the amount of the lubricating oil stored in the compression mechanism housing spaces 45 and 46 is increased, the lubricating oil can be smoothly supplied to the compression mechanism 14 and 15 performed by the oil supply section 33.

  The rollers 26 of the two compression units 22 and 23 of the compression mechanism unit 14 are arranged with a phase of 180 ° along the rotation direction of the drive shaft 16. For this reason, when only the two compression parts 22 and 23 of the compression mechanism part 14 are drive | operated by switching the compression mechanism part 15 to a cylinder resting state, the driving | operation of low vibration with few torque fluctuations can be performed.

  In the compression mechanism portion 15 that can be switched between the operating state and the cylinder resting state, the blade back chambers 35 of the two compression portions 22 and 23 are communicated with each other by the communication path 36, and the two compression portions 22, Twenty-three rollers 26 are arranged with a phase of 180 °. For this reason, in the operation state in which high pressure is applied to these blade back chambers 35 via the high pressure introduction pipe 40 and the pressure introduction pipe 42, the inside of one blade back chamber 35 is associated with the sliding of the blade 27. When the pressure increases, the pressure in the other blade back chamber 35 decreases, so that the fluctuations in pressure in the two blade back chambers 35 cancel each other, and the blade 27 slides in the pressure introduction pipe 42 and the high pressure introduction pipe 40. Therefore, the reciprocating flow of the lubricating oil does not occur, the occurrence of the lubricating oil piping vibration in the pressure introducing pipe 42 and the high pressure introducing pipe 40 can be prevented, and the performance and durability of the multi-cylinder rotary compressor 2 are improved. be able to.

  As shown in FIG. 3, a communication path 47 is connected between the two accumulators 7 and 8, and the refrigerant in the liquid state accumulated in the accumulators 7 and 8 can move through the communication path 47. For this reason, when the multi-cylinder rotary compressor 2 is in operation, it is possible to prevent a large amount of liquid refrigerant from accumulating in one of the accumulators 7 and 8, and to accumulate in the two accumulators 7 and 8. The amount of the refrigerant in the liquid state can be made the same. Thereby, the volume in the accumulators 7 and 8 can be effectively used to store the refrigerant in the liquid state, the volume of the accumulators 7 and 8 can be reduced, and the accumulators 7 and 8 on one side can be achieved. In addition, it is possible to increase the reliability of the multi-cylinder rotary compressor 2 by preventing the occurrence of inconvenience that a large amount of liquid refrigerant accumulates.

  Further, a communication path 48 is connected between the suction pipes 12 of the two accumulators 7 and 8 and below the cylinder chamber 24 as shown in FIG. Lubricating oil accumulated in the cylinder chamber 24 of the compression mechanism section 15 can be sucked toward the compression mechanism section 14 in the operating state. Thereby, it is possible to prevent the lubricating oil that has entered the cylinder chamber 24 of the cylinder mechanism 24 in the cylinder resting state from being sucked into the compression mechanism section 14 and accumulated in the accumulator 8 connected to the compression mechanism section 15. it can. Thereby, when the compression mechanism part 15 becomes a cylinder resting state, it can prevent that lubricating oil accumulates in the accumulator 8, and can prevent the liquid level fall of the lubricating oil in the airtight case 9. FIG.

In the present embodiment, it is assumed that the volume of the cylinder chamber 24 in the compression mechanism portions 14 and 15 is the same, but the volume of the cylinder chamber 24 of the compression mechanism portion 14 and the cylinder chamber of the compression mechanism portion 15 are assumed. The volume of 24 may be different. For example, the multi-cylinder rotary type in the case where the compression mechanism unit 15 is cylinder-rested by making the volume of the cylinder chamber 24 of the compression mechanism unit 15 in the cylinder-cylinder state larger than the volume of the cylinder chamber 24 of the compression mechanism unit 14. The output of the compressor 2 can be made smaller than 1/2 of the output in the normal operation state.
(Second Embodiment)
A second embodiment of the present invention will be described with reference to FIG. In the present embodiment and other embodiments described below, the same components as those of the previously described embodiments are denoted by the same reference numerals, and redundant descriptions are omitted.

The basic configuration of the multi-cylinder rotary compressor 2A of the second embodiment is the same as that of the multi-cylinder rotary compressor 2 of the first embodiment, and the multi-cylinder rotary compressor 2A of the second embodiment. And the multi-cylinder rotary compressor 2 of the first embodiment is that one compression unit 22 in the compression mechanism unit 14 can be switched between an operating state and a cylinder resting state.

  A blade back chamber 35 in which the rear end side of the blade 27 is slidably accommodated in the cylinder 25 of one compression portion 22 in the compression mechanism portion 14 and is airtight with respect to the space in the sealed case 9. Is formed. The compression mechanism unit 14 is provided with a working pressure switching unit 51 that switches the magnitude of the pressure of the gas refrigerant acting on the blade back chamber 35. The working pressure switching unit 51 includes a three-way valve 52, a high-pressure introduction pipe 53 having one end connected to the bottom of the sealed case 9 and the other end connected to the three-way valve 52, and one end connected to the suction pipe 12 of the accumulator 7. The other end is constituted by a low-pressure introduction pipe 54 whose other end is connected to the three-way valve 52, and a pressure introduction pipe 55 whose one end is connected to the three-way valve 52 and the other end is connected to the blade back chamber 35. When the three-way valve 52 is switched and the pressure of the gas refrigerant compressed in the compression mechanism 14 and discharged into the sealed case 9 is applied to the blade back chamber 35 via the lubricating oil, the blade 27 is biased by the pressure. The tip of the urged blade 27 is brought into contact with the outer peripheral surface of the roller 26, and the compression unit 22 of the compression mechanism unit 14 is in an operating state. On the other hand, when the three-way valve 52 is switched and the pressure of the gas refrigerant in the accumulator 7 before being compressed by the compression mechanism 14 is applied to the blade back chamber 35, the tip of the blade 27 comes into contact with the outer peripheral surface of the roller 26. The force that urges the blade 27 in the direction to be removed disappears, the tip end portion of the blade 27 moves away from the outer peripheral surface of the roller 26, and the compression portion 22 of the compression mechanism portion 14 enters a cylinder resting state in which the gas refrigerant is not compressed. The blade 27 having the tip portion separated from the outer peripheral surface of the roller 26 is held by the permanent magnet 37 so as to be fixed at a position where the tip portion is separated from the roller 26.

  In such a configuration, according to the second embodiment, since all the configurations described in the first embodiment are provided, all the operations and effects described in the first embodiment are exhibited.

  Furthermore, by switching the working pressure switching unit 51 in conjunction with the switching of the working pressure switching unit 38, the operating state of the multi-cylinder rotary compressor 2A can be switched to four stages. The four-stage switching of the operating state is as follows.

  First, in the compression mechanism unit 14, the two compression units 22 and 23 are set in an operating state, and in the compression mechanism unit 15, the two compression units 22 and 23 are set in an operating state. As a result, the multi-cylinder rotary compressor 2A has a four-cylinder operation state in which compression is performed by the two compression units 22 and 23 of the compression mechanism unit 14 and the two compression units 22 and 23 of the compression mechanism unit 15. Become.

  Next, in the compression mechanism unit 14, the compression unit 22 is placed in a cylinder resting state, the compression unit 23 is set in an operation state, and in the compression mechanism unit 15, the two compression units 22 and 23 are set in an operation state. As a result, the multi-cylinder rotary compressor 2 </ b> A enters a three-cylinder operation state in which compression is performed by one compression unit 23 of the compression mechanism unit 14 and the two compression units 22 and 23 of the compression mechanism unit 15.

  Next, two compression parts 22 and 23 are made into an operation state in compression mechanism part 14, and two compression parts 22 and 23 are made into a cylinder rest state in compression mechanism part 15. Thus, the multi-cylinder rotary compressor 2A is in a two-cylinder operation state in which compression is performed by the two compression units 22 and 23 of the compression mechanism unit 14.

Next, in the compression mechanism unit 14, the compression unit 22 is brought into a cylinder resting state, the compression unit 23 is brought into an operating state, and in the compression mechanism unit 15, the two compression units 22 and 23 are brought into a cylinder resting state. Thus, the multi-cylinder rotary compressor 2A is in a one-cylinder operation state in which compression is performed only by one compression unit 23 of the compression mechanism unit 14.
(Third embodiment)
A third embodiment of the present invention will be described with reference to FIG. The basic configuration of the multi-cylinder rotary compressor 2B of the third embodiment is the same as that of the multi-cylinder rotary compressor 2 of the first embodiment, and the multi-cylinder rotary compressor 2B of the third embodiment. The difference between the multi-cylinder rotary compressor 2 of the first embodiment and the multi-cylinder rotary compressor 2 is the configuration of the electric motor unit 71 accommodated in the sealed case 9.

  In the sealed case 9, an electric motor part 71 arranged at the center part in the longitudinal direction and two compression mechanism parts 14 and 15 arranged on both sides of the electric motor part 71 are accommodated.

  The electric motor unit 71 includes a stator 72 and a rotor 73, and the stator 72 is fixed to the inner peripheral portion of the hermetic case 9 by adhesion, press fitting, or the like, so that the rotor 73 can rotate inside the stator 72. Has been inserted. The rotor 73 includes two divided rotors 73a and 73b divided in the axial direction of the rotor 73.

  A rotor lumen 74 is formed at the center of one split rotor 73a, and a drive shaft 75 is inserted and fixed in the rotor lumen 74. The drive shaft 75 is adjacent to the split rotor 73a. Are connected to one of the compression mechanisms 14 located at the same position. A rotor lumen 76 is formed at the center of the other divided rotor 73b, and a drive shaft 77 is inserted and fixed in the rotor lumen 76. The drive shaft 77 is adjacent to the divided rotor 73b. Are connected to the other compression mechanism portion 15 located at the same position.

  One drive shaft 75 is inserted into the rotor lumen 74 of one split rotor 73a, and the tip is inserted into the rotor lumen 76 of the other split rotor 73b.

  A half-moon-shaped notch portion 78 is formed as a detent mechanism portion for preventing the drive shafts 75 and 77 from rotating around each other at a portion where one end of the drive shaft 75 and one end of the drive shaft 77 are opposed to each other. Are fitted to each other.

  A plurality of detent pins 79 are inserted into the split rotor 73a and the split rotor 73b in a direction parallel to the drive shafts 75 and 77 as a detent mechanism for preventing the split rotors 73a and 73b from rotating. . These detent pins 79 are inserted into shaft insertion holes 80 formed in the divided rotor 73a and shaft insertion holes 81 formed in the divided rotor 73b.

  The total axial length “L1” of the divided rotor 73a and the divided rotor 73b is set larger than the axial length “L2” of the stator 72.

  In such a configuration, according to the third embodiment, since all the configurations described in the first embodiment are provided, all the operations and effects described in the first embodiment are exhibited.

  Furthermore, since the rotor 73 of the electric motor unit 71 is composed of divided rotors 73a and 73b divided into two, in this multi-cylinder rotary compressor 2B, the electric motor unit 71 and the compression mechanism units 14 and 15 The split rotor 73a is fixed to the drive shaft 75 to which the compression mechanism unit 14 is connected, and the split rotor 73b is fixed to the drive shaft 77 to which the compression mechanism unit 15 is connected. This can be done by inserting the children 73a and 73b into the stator 72 from both sides. For this reason, compared with the case where a compression mechanism part is connected with the drive shaft fixed to the rotor inserted in the stator, the motor part 71 and the compression mechanism parts 14 and 15 can be connected easily. .

  The tip of one drive shaft 75 inserted into the rotor lumen 74 of one split rotor 73a is also inserted into the rotor lumen 76 of the other split rotor 73b. For this reason, the centers of the two divided rotors 73a and 73b can be easily matched, and the gap between the stator 72 and the divided rotors 73a and 73b can be ensured equally.

Moreover, the half-moon-shaped notch part 78 is each formed in the edge part of the drive shafts 75 and 77, and these notch parts 78 are fitted. For this reason, even if torque fluctuation occurs on the compression mechanism portions 14 and 15 side, the drive shaft 75 and the drive shaft 77 always rotate integrally, and the divided rotor 73a and the divided rotor 73b are positioned in the rotation direction. It is possible to prevent the displacement, and it is possible to prevent the performance degradation of the electric motor unit 71 caused by the displacement of the divided rotor 73a and the divided rotor 73b in the rotational direction.

  Further, the divided rotor 73 a and the divided rotor 73 b are prevented from being rotated by a rotation-preventing pin 79 inserted into the shaft insertion holes 80 and 81. For this reason, it is possible to more reliably prevent the positional deviation in the rotational direction between the divided rotor 73a and the divided rotor 73b.

  The total axial length “L1” of the split rotor 73a and split rotor 73b is set to be larger than the axial length “L2” of the stator 72. For this reason, between the stator 72 and the rotor 73, the force of the direction which draws | separates the split rotors 73a and 73b acts, and the split rotor 73a and the split rotor 73b contact | abutted the end surface Rotate with. As a result, it is possible to prevent the split rotors 73a and 73b from moving in the axial direction during rotation, and the split rotors 73a and 73b from contacting and separating to generate abnormal noise.

  In the present embodiment, the case where the axial lengths of the split rotor 73a and the split rotor 73b are the same is shown as an example, but when the load torques of the compression mechanism portions 14 and 15 are different. The axial dimension of the split rotors 73a and 73b may be changed according to the difference in the load torque. For example, when the load torque of the compression mechanism unit 14 during operation is larger than the compression mechanism unit 15, the axial dimension of the divided rotor 73a connected to the compression mechanism unit 14 is set in the axial direction of the divided rotor 73b. Make it larger than the length dimension. Thereby, even if a large load torque acts on the compression mechanism unit 14 side, it is possible to prevent the positional deviation between the drive shaft 75 and the split rotor 73a.

  According to each embodiment described above, the motor unit 13 and the two compression mechanism units 14 and 15 located on both sides of the motor unit 13 are accommodated in the sealed case 9 and are located on the outer peripheral side of the sealed case 9. The two accumulators 7 and 8 are arranged close to the compression mechanism parts 14 and 15, and the accumulator 7 and the compression mechanism part 14, which are located close to each other, and the accumulator 8 and the compression mechanism part 15 are respectively connected via the suction pipe 12. Connected. For this reason, the length dimension of the suction pipe 12 can be shortened, whereby the flow resistance when the gas refrigerant flows through the suction pipe 12 can be reduced, and the generated pressure loss can be reduced to reduce the number of cylinders. The performance of the rotary compressors 2, 2A, 2B can be improved.

  As mentioned above, although several embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 1 ... Air conditioner (refrigeration cycle apparatus), 2 ... Multi-cylinder rotary compressor, 2A ... Multi-cylinder rotary compressor, 2B ... Multi-cylinder rotary compressor, 4 ... Outdoor heat exchanger (condenser, evaporator) ), 5 ... expansion device, 6 ... indoor heat exchanger (evaporator, condenser), 7, 8 ... accumulator, 12 ... suction pipe, 13 ... motor part, 14, 15 ... compression mechanism part, 22, 23 ... compression part 24 ... Cylinder chamber, 25 ... Cylinder, 26 ... Roller, 27 ... Blade, 32 ... Discharge gap (discharge portion), 33 ... Oil supply portion, 34 ... Discharge pipe, 35 ... Blade back chamber, 38 ... Working pressure switching portion, 43 ... Baffle body, 44 ... Motor unit storage space, 45, 46 ... Compression mechanism storage space, 47 ... Communication path, 72 ... Stator, 73 ... Rotor, 73a, 73b ... Split rotor, 75, 77 ... Drive axis

Claims (6)

A sealed case;
One electric motor unit housed in the sealed case;
Two compression mechanism parts housed in the sealed case and disposed on both sides of the electric motor part, connected to the electric motor part and compressing the working fluid;
Two accumulators arranged close to each compression mechanism on the outer peripheral side of the sealed case and individually connected to the compression mechanism on the side located close to each other via a suction pipe;
A multi-cylinder rotary compressor.   2. The multi-cylinder rotary compressor according to claim 1, wherein a communication passage is connected between the two accumulators so that the working fluid stored in the accumulators can move. Two baffle bodies that divide the inside of the sealed case into a motor unit housing space in which the motor unit is housed and a compression mechanism unit housing space in which the compression mechanism units are housed;
A discharge part for discharging the working fluid compressed by each compression mechanism part into the electric motor unit accommodation space;
A discharge pipe that is communicated with each of the compression mechanism housing spaces and discharges the working fluid in the compression mechanism housing space to the outside of the sealed case;
An oil supply section that is provided in each compression mechanism section accommodating space, and supplies lubricating oil stored in the compression mechanism section accommodation space to the compression mechanism section;
Have
Each baffle body is configured such that the working fluid and the lubricating oil can move between the motor unit storage space and the compression mechanism unit storage space between the motor unit storage space and the compression mechanism unit storage space, and 3. The multi-cylinder rotary compressor according to claim 1, wherein the multi-cylinder rotary compressor is partitioned so as to generate a differential pressure between the motor unit housing space and each compression mechanism unit housing space. Each compression mechanism section includes a roller, a cylinder having a cylinder chamber in which the roller is housed so as to be eccentrically rotatable, and a slidable provided in the cylinder so that the tip end abuts against the outer peripheral surface of the roller. Two compression parts provided with a blade that bisects the cylinder chamber along the rotation direction of the rollers by
The roller of one compression part of one compression mechanism part and the roller of the other compression part are arranged at a position that rotates with a phase of 180 °,
In each cylinder of the two compression parts in the one compression mechanism part, the rear end side of the blade is slidably accommodated and airtight with respect to the space in the hermetic case, and the blade backs communicated with each other. A room was established,
An operating state in which the tip of the blade is brought into contact with the outer peripheral surface of the roller by applying the pressure of the discharge-side working fluid to the blade back chamber of the one compression mechanism, and the suction-side working fluid in the blade back chamber A working pressure switching unit is provided for switching to a closed cylinder state in which the tip of the blade is separated from the outer peripheral surface of the roller by applying the pressure of
The multi-cylinder rotary compressor according to any one of claims 1 to 3.   The electric motor unit has a stator and a rotor provided rotatably in the stator, and the rotor includes two divided rotors divided in the axial direction of the rotor, The multi-cylinder according to any one of claims 1 to 4, wherein the divided rotor and the compression mechanism portion positioned adjacent to the divided rotor are connected by different drive shafts. Rotary compressor. The multi-cylinder rotary compressor according to any one of claims 1 to 5, a condenser connected to the multi-cylinder rotary compressor, an expansion device connected to the condenser, and the expansion device And an evaporator connected between the multi-cylinder rotary compressor.

Images