JP2006009756A - Compression system and refrigerating device using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve following nature of a second vane and avoid generation of strike noise of the second vane in a second operation mode in a compression system provided with a multi cylinder rotary compressor used with changing over an operation mode to a first operation mode in which both rotary compression elements perform compression work and the second operation mode in which substantially only a first rotary compression element performs compression work. <P>SOLUTION: Refrigerant is made flow in a second cylinder 40 of a rotary compressor 10 in the first operation mode and middle pressure between suction side pressure and delivery side pressure of the both rotary compression elements 32, 34 is applied as back pressure of a second vane 52. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a compression system including a multi-cylinder rotary compressor and a refrigeration apparatus using the same.

  Conventionally, this type of compression system includes a multi-cylinder rotary compressor and a control device for controlling the operation of the multi-cylinder rotary compressor. This multi-cylinder rotary compressor, for example, a two-cylinder rotary compressor provided with first and second rotary compression elements, includes a first and a second driven by a drive element and a rotary shaft of the drive element in a sealed container. 2 rotary compression elements are housed. The first and second rotary compression elements include first and second cylinders, and first and second rollers that are fitted to eccentric portions formed on the rotation shaft and rotate eccentrically in the cylinders, respectively. The first and second vanes are in contact with the first and second cylinders and divide the inside of each cylinder into a low pressure chamber side and a high pressure chamber side, respectively. The first and second vanes are always urged by the spring members to the first and second rollers, respectively.

Then, when the drive element is driven by the control device, the low-pressure refrigerant gas is sucked into the low-pressure chamber side of each cylinder of the first and second rotary compression elements from the suction passage, and the operation of each roller and each vane Each is compressed into high-temperature and high-pressure refrigerant gas, discharged from the high-pressure chamber side of each cylinder to the discharge silencer chamber through the discharge port, then discharged into the sealed container and discharged to the outside (for example, , See Patent Document 1).
JP-A-5-99172

  In such a compression system equipped with a multi-cylinder rotary compressor, when the first and second cylinders perform compression operation in a small capacity range such as during light load or low speed rotation, the displacement volume of both cylinders Since the refrigerant gas has to be sucked in and compressed, the control device is operated with the rotational speed of the drive element lowered by that amount. However, if the rotational speed is too low, the operation efficiency of the drive element is lowered, and there is a problem that the leakage loss is increased and the compression efficiency is also lowered.

  For this reason, in view of the problem, a compression system has been developed that can switch between a one-cylinder operation and a two-cylinder operation according to the capacity. That is, one of the spring members that urge the first and second vanes of the multi-cylinder rotary compressor to the first and second rollers, for example, the second vane The spring member biased to the roller is deleted, and the refrigerant pressure on the discharge side of the rotary compression elements is applied as the back pressure of the second vane during the two-cylinder operation by the control device. As a result, the second vane is urged toward the second roller to perform compression work.

  On the other hand, in the small capacity region, the control device applies the refrigerant pressure on the suction side of the rotary compression elements as the back pressure of the second vane. Since this suction pressure is low, the second vane cannot be urged toward the second roller. For this reason, substantially no compression work is performed in the second rotary compression element, and the compression work of the refrigerant is performed only in the first rotary compression element.

  As described above, since the amount of refrigerant gas to be compressed can be reduced by performing the one-cylinder operation in the small capacity region, the number of revolutions can be increased accordingly. As a result, the operating efficiency of the drive element can be improved and the leakage loss can be reduced.

  However, in the second rotary compression element in which the spring member is not provided during the two-cylinder operation as described above, the pressure on the discharge side of both rotary compression elements that bias the second roller has a large pressure fluctuation. The followability of the vane is deteriorated due to the fluctuation, and there is a problem that a collision sound is generated between the second roller and the second vane.

  On the other hand, in the one-cylinder operation, the second rotary compression element is in a state where the second roller is idle, but at this time, the pressure in the second cylinder and the back pressure of the second vane are the same. Since the suction side pressure is applied, the second vane comes out in the second cylinder due to the fluctuation of the balance between the two spaces, and the second roller collides with the second roller to generate a collision sound. there were.

  The present invention is made to solve the problems of the related art, and only the first vane is biased to the first roller by the spring member, and the first rotary compression element performs the compression work. And a second vane in a compression system including a multi-cylinder rotary compressor that can be used by switching between the first operation mode and the second operation mode in which only the first rotary compression element performs compression work. It is an object of the present invention to improve the followability of the second vane and to avoid the occurrence of the collision sound of the second vane.

  In the compression system of the first aspect of the present invention, a drive element and first and second rotary compression elements driven by a rotary shaft of the drive element are housed in a sealed container, and the first and second rotary compressions are carried out. The elements include first and second cylinders, first and second rollers that are fitted into eccentric portions formed on the rotation shaft and eccentrically rotate in each cylinder, and the first and second rollers. And the first and second vanes that divide each cylinder into a low-pressure chamber side and a high-pressure chamber side, respectively, and urge only the first vane to the first roller by a spring member, Multi-cylinder rotary compressor that can be used by switching between a first operation mode in which both rotary compression elements perform compression work and a second operation mode in which only the first rotary compression element performs compression work In the first operation mode, the first As the back pressure of the vane, it is to apply an intermediate pressure between the suction side pressure and the discharge-side pressure of both rotary compression elements.

  A compression system according to a second aspect of the present invention houses a drive element and first and second rotary compression elements driven by a rotary shaft of the drive element in a sealed container, and the first and second rotary compressions. The elements include first and second cylinders, first and second rollers that are fitted into eccentric portions formed on the rotation shaft and eccentrically rotate in each cylinder, and the first and second rollers. And the first and second vanes that divide each cylinder into a low-pressure chamber side and a high-pressure chamber side, respectively, and urge only the first vane to the first roller by a spring member, Multi-cylinder rotary compressor that can be used by switching between a first operation mode in which both rotary compression elements perform compression work and a second operation mode in which only the first rotary compression element performs compression work The refrigerant flow to the second cylinder In the second operation mode, the valve device prevents the refrigerant from flowing into the second cylinder, and the back pressure of the second vane serves as the back pressure of the second rotary compression element in the second operation mode. A pressure is applied.

  According to a third aspect of the present invention, there is provided a compression system in which a drive element and first and second rotary compression elements driven by a rotary shaft of the drive element are housed in a sealed container, and the first and second rotary compressions are carried out. The elements include first and second cylinders, first and second rollers that are fitted into eccentric portions formed on the rotation shaft and eccentrically rotate in each cylinder, and the first and second rollers. And the first and second vanes that divide each cylinder into a low-pressure chamber side and a high-pressure chamber side, respectively, and urge only the first vane to the first roller by a spring member, Multi-cylinder rotary compressor that can be used by switching between a first operation mode in which both rotary compression elements perform compression work and a second operation mode in which only the first rotary compression element performs compression work The refrigerant flow to the second cylinder In the first operation mode, the refrigerant is caused to flow into the second cylinder by the valve device, and the suction side pressure and discharge of both rotary compression elements are used as the back pressure of the second vane. In the second operation mode, the refrigerant is prevented from flowing into the second cylinder by the valve device, and the back pressure of the second vane is used as the back pressure of the second vane. The suction side pressure of the rotary compression element is applied.

  In the refrigeration apparatus according to the fourth aspect of the present invention, a refrigerant circuit is configured by using the compression system of each of the above inventions.

  According to the first and third aspects of the invention, in the first operation mode, an intermediate pressure between the suction side pressure and the discharge side pressure of the rotary compression elements is applied as the back pressure of the second vane. Therefore, the pressure fluctuation becomes significantly smaller than when the discharge side pressure of the rotary compression element is applied to the back pressure of the second vane. Thereby, in the first operation mode, the followability of the second vane of the multi-cylinder rotary compressor is improved, the compression efficiency of the second rotary compression element is improved, and the second roller and the second Generation of collision noise with the vane can be avoided in advance.

  According to the second and third aspects of the invention, in the second operation mode, the valve device prevents the refrigerant from flowing into the second cylinder, and the back pressure of the second vane is By applying the suction side pressure of the rotary compression element, the pressure in the second cylinder can be made higher than the back pressure of the second vane. As a result, in the second operation mode, the second vane of the multi-cylinder rotary compressor does not come out into the second cylinder due to the pressure in the second cylinder, so that it collides with the second roller. It is possible to avoid inconvenience that causes a collision sound.

  As described above, the first and second rotary compression elements are switched between the first operation mode in which compression work is performed and the second operation mode in which only the first rotation compression element is in compression work is used. The performance and reliability of the multi-cylinder rotary compressor that can be improved can be improved, and the performance of the compression system can be significantly improved.

  Further, by configuring the refrigerant circuit of the refrigeration apparatus using the compression system of each of the inventions as in claim 4, it is possible to improve the operation efficiency of the entire refrigeration apparatus.

  Embodiments of the present invention will be described below in detail with reference to the drawings.

    FIG. 1 is a longitudinal side view of an internal high-pressure rotary compressor 10 having first and second rotary compression elements as an embodiment of a multi-cylinder rotary compressor of the compression system CS of the present invention. FIG. The longitudinal side view (the cross section different from FIG. 1 is shown) of the rotary compressor 10 is shown, respectively. In addition, the compression system CS of a present Example comprises a part of refrigerant circuit of the air conditioner as a refrigeration apparatus which air-conditions a room | chamber interior.

  In each figure, the rotary compressor 10 of the embodiment is an internal high-pressure type rotary compressor, and is used as a drive element disposed in the upper side of the internal space of the sealed container 12 in a vertical cylindrical sealed container 12 made of a steel plate. An electric element 14 and a rotary compression mechanism portion 18 which is disposed below the electric element 14 and is driven by the rotary shaft 16 of the electric element 14 and which includes the first and second rotary compression elements 32 and 34 are accommodated. Yes.

  The sealed container 12 has an oil reservoir at the bottom, a container body 12A that houses the electric element 14 and the rotary compression mechanism 18, and a generally bowl-shaped end cap (lid body) 12B that closes the upper opening of the container body 12A. A circular mounting hole 12D is formed on the upper surface of the end cap 12B, and a terminal (wiring is omitted) 20 for supplying power to the electric element 14 is mounted in the mounting hole 12D. ing.

  Further, a refrigerant discharge pipe 96 described later is attached to the end cap 12B, and one end of the refrigerant introduction pipe 96 communicates with the inside of the sealed container 12. A mounting base 11 is provided at the bottom of the sealed container 12.

  The electric element 14 includes a stator 22 that is welded and fixed in an annular shape along the inner peripheral surface of the upper space of the sealed container 12, and a rotor 24 that is inserted and installed inside the stator 22 with a slight gap. The rotor 24 is fixed to a rotary shaft 16 that extends in the vertical direction through the center.

  The stator 22 has a laminated body 26 in which donut-shaped electromagnetic steel plates are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method. Similarly to the stator 22, the rotor 24 is also formed of a laminated body 30 of electromagnetic steel plates.

  An intermediate partition plate 36 is sandwiched between the first rotary compression element 32 and the second rotary compression element 34. That is, the first rotary compression element 32 and the second rotary compression element 34 include an intermediate partition plate 36, first and second cylinders 38 and 40 disposed above and below the intermediate partition plate 36, and the first rotary compression element 32 and the second rotary compression element 34. The first and second cylinders 38 and 40 are fitted to upper and lower eccentric portions 42 and 44 provided on the rotary shaft 16 with a phase difference of 180 degrees, and the first and second cylinders 38 and 40 rotate eccentrically in the cylinders 38 and 40, respectively. A second roller 46, 48, and first and second vanes 50 that abut against the first and second rollers 46, 48 and partition the cylinders 38, 40 into a low pressure chamber side and a high pressure chamber side, respectively 52 and an upper support member 54 and a lower support member 56 as support members that also serve as bearings for the rotary shaft 16 by closing the upper opening surface of the first cylinder 38 and the lower opening surface of the second cylinder 40. Consists of.

  The first and second cylinders 38, 40 are provided with suction passages 58, 60 communicating with the insides of the first and second cylinders 38, 40, respectively. The suction passages 58, 60 will be described later. Refrigerant introduction pipes 92 and 94 are connected in communication.

  A discharge muffler chamber 62 is provided above the upper support member 54, and the refrigerant gas compressed by the first rotary compression element 32 is discharged into the discharge muffler chamber 62. The discharge silencing chamber 62 has a hole through which the upper support member 54 that also serves as a bearing of the rotary shaft 16 and the rotary shaft 16 passes in the center, and covers the electric element 14 side (upper side) of the upper support member 54. It is formed in a bowl-shaped cup member 63. The electric element 14 is provided above the cup member 63 at a predetermined interval from the cup member 63.

  The lower support member 56 is provided with a discharge silencing chamber 64 formed by closing a recessed portion formed on the lower side of the lower support member 56 with a cover as a wall. That is, the discharge silencer chamber 64 is closed by the lower cover 68 that defines the discharge silencer chamber 64.

  The first cylinder 38 is formed with a guide groove 70 for accommodating the first vane 50 described above, and a spring member is provided outside the guide groove 70, that is, on the back side of the first vane 50. A storage portion 70A for storing the spring 74 is formed. The spring 74 abuts against the rear side end of the first vane 50 and constantly urges the first vane 50 toward the first roller 46. Further, for example, a discharge side pressure (high pressure) described later in the sealed container 12 is also introduced into the storage portion 70 </ b> A and applied as a back pressure of the first vane 50. The storage portion 70A is open to the guide groove 70 side and the closed container 12 (container body 12A) side, and a metal plug 137 is provided on the closed container 12 side of the spring 74 stored in the storage portion 70A. Thus, it serves to prevent the spring 74 from coming off.

  The second cylinder 40 is formed with a guide groove 72 for accommodating the second vane 52, and a back pressure chamber is formed outside the guide groove 72, that is, on the back side of the second vane 52. 72A is formed. The back pressure chamber 72A is open to the guide groove 72 side and the closed container 12 side, and a pipe 75 described later is connected to the opening of the closed container 12 side to be sealed from the inside of the closed container 12.

  Sleeves 141 and 142 are welded and fixed to the side surfaces of the container body 12A of the sealed container 12 at positions corresponding to the suction passages 58 and 60 of the first cylinder 38 and the second cylinder 40, respectively. These sleeves 141 and 142 are adjacent to each other in the vertical direction.

  One end of a refrigerant introduction pipe 92 for introducing refrigerant gas into the first cylinder 38 is inserted and connected into the sleeve 141, and one end of the refrigerant introduction pipe 92 communicates with the suction passage 58 of the upper cylinder 38. The other end of the refrigerant introduction pipe 92 is opened in the accumulator 146.

  One end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the second cylinder 40 is inserted into and connected to the sleeve 142, and one end of the refrigerant introduction pipe 94 communicates with the suction passage 60 of the second cylinder 40. The other end of the refrigerant introduction pipe 94 is opened in the accumulator 146 in the same manner as the refrigerant introduction pipe 92.

  The accumulator 146 is a tank that performs gas-liquid separation of the suction refrigerant, and is attached to the upper side surface of the container body 12 </ b> A of the sealed container 12 via a bracket 147. A refrigerant introduction pipe 92 and a refrigerant introduction pipe 94 are inserted into the accumulator 146 from the bottom, and openings at the other ends are positioned above the accumulator 146, respectively. Further, one end of the refrigerant pipe 100 is inserted into the upper part of the accumulator 146.

  The discharge silencer chamber 64 and the discharge silencer chamber 62 communicate with the upper and lower support members 54 and 56, the first and second cylinders 38 and 40, and the intermediate partition plate 36 in the axial direction (vertical direction). It is communicated through. Then, the high-temperature and high-pressure refrigerant gas compressed by the second rotary compression element 34 and discharged to the discharge muffler chamber 64 is discharged to the discharge muffler chamber 62 via the communication path 120, and Merges with compressed high-temperature and high-pressure refrigerant gas.

  Further, the discharge silencer chamber 62 and the inside of the sealed container 12 are communicated with each other through a hole (not shown) penetrating the cup member 63, and the first rotary compression element 32 and the second rotary compression element 34 are compressed through this hole. The high-pressure refrigerant gas discharged into the discharge silencer chamber 62 is discharged into the sealed container 12.

  Here, a refrigerant pipe 101 is connected to the middle of the refrigerant pipe 100, and the pipe is connected to the pipe 75 described above via an electromagnetic valve 105. Further, a refrigerant pipe 102 is also connected to the middle portion of the refrigerant discharge pipe 96 described above, and is connected to the pipe 75 via an electromagnetic valve 106 in the same manner as the refrigerant pipe 101. The opening and closing of the solenoid valves 105 and 106 are controlled by a controller 210 described later. That is, when the valve device 105 is opened by the controller 210 and the valve device 106 is closed, the refrigerant pipe 101 and the pipe 75 are communicated. As a result, a part of the suction side refrigerant of the rotary compression elements 32 and 34 that flows through the refrigerant pipe 100 and flows into the accumulator 146 enters the refrigerant pipe 101 and flows from the pipe 75 into the back pressure chamber 72A. Thereby, the suction side pressure of the rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52.

  Further, when the valve device 105 is closed by the controller 210 and the valve device 106 is opened, the refrigerant discharge pipe 96 and the pipe 75 are communicated. As a result, a part of the discharge-side refrigerant of the rotary compression elements 32 and 34 discharged from the sealed container 12 and passing through the refrigerant discharge pipe 96 flows from the pipe 75 into the back pressure chamber 72A via the refrigerant pipe 102. As a result, the discharge-side pressure of the rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52.

  Here, the controller 210 described above constitutes a part of the compression system CS of the present invention, and controls the rotational speed of the electric element 14 of the rotary compressor 10. Further, as described above, the opening and closing of the electromagnetic valve 105 of the refrigerant pipe 101 and the electromagnetic valve 106 of the refrigerant pipe 102 are controlled.

  Next, FIG. 3 shows a refrigerant circuit diagram of the air conditioner configured using the compression system CS. That is, the compression system CS of the embodiment constitutes a part of the refrigerant circuit of the air conditioner shown in FIG. 3, and is composed of the rotary compressor 10 and the controller 210 described above. The refrigerant discharge pipe 96 of the rotary compressor 10 is connected to the inlet of the outdoor heat exchanger 152. The controller 210, the rotary compressor 10, and the outdoor heat exchanger 152 are provided in an outdoor unit (not shown) of the air conditioner. A pipe connected to the outlet of the outdoor heat exchanger 152 is connected to an expansion valve 154 as decompression means, and a pipe exiting the expansion valve 154 is connected to an indoor heat exchanger 156. The expansion valve 154 and the indoor side heat exchanger 156 are provided in an indoor unit (not shown) of the air conditioner. The refrigerant pipe 100 of the rotary compressor 10 is connected to the outlet side of the indoor heat exchanger 156.

  Note that HFC or HC refrigerants are used as refrigerants, and existing oils such as mineral oils (mineral oils), alkylbenzene oils, ether oils and ester oils are used as the lubricating oils.

  Next, the operation of the rotary compressor 10 with the above configuration will be described. Based on the operation command input of the controller on the indoor unit (not shown) provided in the indoor unit described above, the controller 210 controls the rotation speed of the electric element 14 of the rotary compressor 10 and the room is in a normal load or high load state. If so, the controller 210 executes the first operation mode. In this first operation mode, the controller 210 closes the electromagnetic valve 105 of the refrigerant pipe 101 and the electromagnetic valve 106 of the refrigerant pipe 102 (FIG. 4).

  When the stator coil 28 of the electric element 14 is energized through the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the first and second rollers 46 and 48 are eccentrically rotated in the first and second cylinders 38 and 40 by being fitted to upper and lower eccentric portions 42 and 44 provided integrally with the rotary shaft 16.

  Thereby, the low-pressure refrigerant flows from the refrigerant pipe 100 of the rotary compressor 10 into the accumulator 146. Since the solenoid valve 105 of the refrigerant pipe 101 is closed as described above, all of the refrigerant passing through the refrigerant pipe 100 flows into the accumulator 146 without flowing into the pipe 75.

  The low-pressure refrigerant that has flowed into the accumulator 146 is gas-liquid separated there, and then only the refrigerant gas enters the refrigerant discharge pipes 92 and 94 opened in the accumulator 146. The low-pressure refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58.

  The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the operation of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas, and the high-pressure chamber side of the first cylinder 38. Then, the liquid is discharged into the discharge silencer chamber 62 through a discharge port (not shown).

  On the other hand, the low-pressure refrigerant gas that has entered the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34. The refrigerant gas sucked into the low pressure chamber side of the second cylinder 40 is compressed by the operations of the second roller 48 and the second vane 52.

  At this time, since the electromagnetic valve 105 and the electromagnetic valve 106 are closed as described above, the inside of the pipe 75 connected to the back pressure chamber 72A of the second vane 52 is a closed space. Furthermore, since the refrigerant in the second cylinder 40 flows into the back pressure chamber 72A not less than between the second vane 52 and the storage portion 70A, the pressure in the back pressure chamber 72A of the second vane 52 is It becomes an intermediate pressure between the suction side pressure and the discharge side pressure of the rotary compression elements 32, 34, and this intermediate pressure is applied as the back pressure of the second vane 52. Due to this intermediate pressure, the second vane 52 can be sufficiently urged against the second roller 48 without using a spring member.

  Conventionally, as shown in FIG. 9, a high pressure, which is the discharge side pressure of the rotary compression elements 32, 34, is applied as the back pressure of the second vane 52. In this case, the discharge side pressure has a large pulsation. In addition, since there is no spring member, the followability of the second vane 52 is deteriorated by this pulsation, the compression efficiency is lowered, and a collision sound is generated between the second vane 52 and the second roller 48. There was a problem that occurred.

  However, in the present invention, since the intermediate pressure between the suction side pressure and the discharge side pressure of the rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52, the discharge side pressure is applied as described above. Compared to the case, the pressure pulsation is remarkably reduced. In particular, in this embodiment, the solenoid valves 105 and 106 are closed to block the inflow of the suction side refrigerant and the discharge side refrigerant of the rotary compression elements 32 and 34 from the pipe 75. The back pressure pulsation can be further suppressed. Thereby, the followability of the second vane 52 in the first operation mode is improved, and the compression efficiency of the second rotary compression element 34 is also improved.

  The refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 and having become high temperature and high pressure passes through the discharge port (not shown) from the high pressure chamber side of the second cylinder 40 to the discharge silencer chamber 64. Discharged. The refrigerant gas discharged to the discharge muffler chamber 64 is discharged to the discharge muffler chamber 62 via the communication path 120 and merges with the refrigerant gas compressed by the first rotary compression element 32. The merged refrigerant gas is discharged into the sealed container 12 through a hole (not shown) that penetrates the cup member 63.

  Thereafter, the refrigerant in the sealed container 12 is discharged to the outside from a refrigerant discharge pipe 96 formed in the end cap 12B of the sealed container 12, and flows into the outdoor heat exchanger 152. Therefore, the refrigerant gas dissipates heat and is depressurized by the expansion valve 154 and then flows into the indoor heat exchanger 156. The refrigerant evaporates in the indoor heat exchanger 156 and absorbs heat from the air circulated in the room, thereby exerting a cooling action to cool the room. Then, the refrigerant repeats a cycle in which the refrigerant leaves the indoor heat exchanger 156 and is sucked into the rotary compressor 10.

  Next, another embodiment of the compression system CS of the present invention will be described. FIG. 5 shows a vertical side view of an internal high-pressure rotary compressor 110 having first and second rotary compression elements as a multi-cylinder rotary compressor of the compression system CS in this case. In FIG. 5, the same reference numerals as those in FIGS. 1 to 4 have the same effects.

  In FIG. 5, reference numeral 200 denotes a valve device, which is provided on the outlet side of the accumulator 146 and in the middle of the refrigerant introduction pipe 94 on the inlet side of the sealed container 12. The electromagnetic valve 200 is a valve device for controlling the inflow of the refrigerant into the second cylinder 40, and is controlled by the controller 210 described above as a control device.

  In this embodiment, HFC or HC refrigerant is used as the refrigerant in the present embodiment, and the oil as the lubricating oil is, for example, existing oil such as mineral oil (mineral oil), alkylbenzene oil, ether oil, ester oil, etc. Oil is used.

  Next, the operation of the rotary compressor 110 with the above configuration will be described.

(1) First operation mode (normal load or high load operation)
First, a first operation mode in which both rotary compression elements 32 and 34 perform compression work will be described with reference to FIG. Based on the operation command input of a controller on the indoor unit side (not shown) provided in the indoor unit described above, the controller 210 controls the rotation speed of the electric element 14 of the rotary compressor 110 and the room is in a normal load or a high load state. If so, the controller 210 executes the first operation mode. In this first operation mode, the controller 210 opens the electromagnetic valve 200 of the refrigerant introduction pipe 94 and closes the electromagnetic valve 105 of the refrigerant pipe 101 and the electromagnetic valve 106 of the refrigerant pipe 102.

  When the stator coil 28 of the electric element 14 is energized through the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the first and second rollers 46 and 48 are eccentrically rotated in the first and second cylinders 38 and 40 by being fitted to upper and lower eccentric portions 42 and 44 provided integrally with the rotary shaft 16.

  Thereby, the low-pressure refrigerant flows into the accumulator 146 from the refrigerant pipe 100 of the rotary compressor 110. Since the solenoid valve 105 of the refrigerant pipe 101 is closed as described above, all of the refrigerant passing through the refrigerant pipe 100 flows into the accumulator 146 without flowing into the pipe 75.

  The low-pressure refrigerant that has flowed into the accumulator 146 is gas-liquid separated there, and then only the refrigerant gas enters the refrigerant discharge pipes 92 and 94 opened in the accumulator 146. The low-pressure refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58.

  The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the operation of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas, and the high-pressure chamber side of the first cylinder 38. Then, the liquid is discharged into the discharge silencer chamber 62 through a discharge port (not shown).

  On the other hand, the low-pressure refrigerant gas that has entered the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34. The refrigerant gas sucked into the low pressure chamber side of the second cylinder 40 is compressed by the operations of the second roller 48 and the second vane 52.

  At this time, since the electromagnetic valve 105 and the electromagnetic valve 106 are closed as described above, the inside of the pipe 75 connected to the back pressure chamber 72A of the second vane 52 is a closed space. Furthermore, since the refrigerant in the second cylinder 40 flows into the back pressure chamber 72A not less than between the second vane 52 and the storage portion 70A, the pressure in the back pressure chamber 72A of the second vane 52 is It becomes an intermediate pressure between the suction side pressure and the discharge side pressure of the rotary compression elements 32, 34, and this intermediate pressure is applied as the back pressure of the second vane 52. Due to this intermediate pressure, the second vane 52 can be sufficiently urged against the second roller 48 without using a spring member.

  As a result, like the above embodiment, the followability of the second vane 52 in the first operation mode can be improved, and the compression efficiency of the second rotary compression element 34 can be improved.

  The refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 and having become high temperature and high pressure passes through the discharge port (not shown) from the high pressure chamber side of the second cylinder 40 to the discharge silencer chamber 64. Discharged. The refrigerant gas discharged to the discharge muffler chamber 64 is discharged to the discharge muffler chamber 62 via the communication path 120 and merges with the refrigerant gas compressed by the first rotary compression element 32. The merged refrigerant gas is discharged into the sealed container 12 through a hole (not shown) that penetrates the cup member 63.

  Thereafter, the refrigerant in the sealed container 12 is discharged to the outside from a refrigerant discharge pipe 96 formed in the end cap 12B of the sealed container 12, and flows into the outdoor heat exchanger 152. Therefore, the refrigerant gas dissipates heat and is depressurized by the expansion valve 154 and then flows into the indoor heat exchanger 156. The refrigerant evaporates in the indoor heat exchanger 156 and absorbs heat from the air circulated in the room, thereby exerting a cooling action to cool the room. Then, the refrigerant repeats a cycle in which the refrigerant leaves the indoor heat exchanger 156 and is sucked into the rotary compressor 110.

(2) Second operation mode (operation at light load)
Next, the second operation mode will be described with reference to FIG. When the room is in a light load state, the controller 210 shifts to the second operation mode. The second operation mode is a mode in which only the first rotary compression element 32 substantially performs the compression work, and the electric element 14 is rotated at a low speed in the first operation mode due to a light load in the room. This is an operation mode performed when In the small capacity region of the compression system CS, the refrigerant that compresses by making only the first rotary compression element 32 perform the compression work, compared with the case where the first and second cylinders 38 and 40 perform the compression work. Since the amount of gas can be reduced, it is possible to increase the rotational speed of the electric element 14 even at a light load, improve the operating efficiency of the electric element 14, and reduce the leakage loss of the refrigerant. Because it becomes.

  In this case, the controller 210 closes the above-described electromagnetic valve 200 and prevents the refrigerant from flowing into the second cylinder 40. As a result, the second rotary compression element 34 does not perform compression work. When the refrigerant flow into the second cylinder 40 is blocked, the pressure in the second cylinder 40 is slightly higher than the suction side pressure of the rotary compression elements 32 and 34 (the second roller 48 rotates). In addition, since the high pressure in the sealed container 12 slightly flows from the gap of the second cylinder 40, the pressure in the second cylinder 40 is slightly higher than the suction side pressure).

  The controller 210 opens the electromagnetic valve 105 of the refrigerant pipe 101 and closes the electromagnetic valve 106 of the refrigerant pipe 102. As a result, the refrigerant pipe 101 and the pipe 75 communicate with each other, the refrigerant on the suction side of the first rotary compression element 32 flows into the back pressure chamber 72A, and the first rotary compression element is used as the back pressure of the second vane 52. 32 suction side pressure is applied.

  On the other hand, the controller 210 energizes the stator coil 28 of the electric element 14 via the terminal 20 and the wiring (not shown) as described above, and rotates the rotor 24 of the electric element 14. By this rotation, the first and second rollers 46 and 48 are eccentrically rotated in the first and second cylinders 38 and 40 by being fitted to upper and lower eccentric portions 42 and 44 provided integrally with the rotary shaft 16.

  Thereby, the low-pressure refrigerant flows into the accumulator 146 from the refrigerant pipe 100 of the rotary compressor 110. At this time, since the solenoid valve 105 of the refrigerant pipe 101 is opened as described above, a part of the refrigerant on the suction side of the first rotary compression element 32 passing through the refrigerant pipe 100 passes through the pipe 75 from the refrigerant pipe 101. Then, it flows into the back pressure chamber 72A. Thereby, the back pressure chamber 72A becomes the suction side pressure of the first rotary compression element 32, and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52. .

  Here, when the refrigerant is caused to flow into the second cylinder 40 as shown in FIG. 10, the back pressure chamber 72 </ b> A and the second cylinder 40 have the same suction side pressure of the first rotary compression element 32, There was a risk that the second vane 52 would come out into the second cylinder 40 and collide with the second roller 48.

  However, if the solenoid valve 200 is closed as in the present invention to prevent the refrigerant from flowing into the second cylinder 40 and the pressure in the second cylinder 40 is higher than the suction side pressure of the first rotary compression element 32. By applying the suction side pressure of the first rotary compression element 32 as the back pressure of the second vane 52, the pressure in the second cylinder 40 becomes higher than the back pressure of the second vane 52. For this reason, the second vane 52 is pushed by the pressure in the second cylinder 40 toward the back pressure chamber 72 </ b> A, which is opposite to the second roller 48, and does not come out into the second cylinder 40. . As a result, the inconvenience that the second vane 52 comes out into the second cylinder 40 and collides with the second roller 48 to generate a collision sound can be avoided.

  On the other hand, the low-pressure refrigerant flowing into the accumulator 146 is gas-liquid separated there, and then only the refrigerant gas enters the refrigerant discharge pipe 92 opened in the accumulator 146. The low-pressure refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58.

  The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the operation of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas, and the high-pressure chamber side of the first cylinder 38. Then, the liquid is discharged into the discharge silencer chamber 62 through a discharge port (not shown). At this time, in the second operation mode, the discharge silencer chamber 62 functions as an expansion-type silencer chamber, and the discharge silencer chamber 64 functions as a resonance-type silencer chamber. The pressure pulsation of the refrigerant can be further reduced. Thereby, the silencing effect can be further improved in the second operation mode in which the compression work is performed substantially only by the first rotary compression element 32.

  The refrigerant gas discharged into the discharge silencer chamber 62 is discharged into the sealed container 12 through a hole (not shown) that penetrates the cup member 63. Thereafter, the refrigerant in the sealed container 12 is discharged to the outside from a refrigerant discharge pipe 96 formed in the end cap 12B of the sealed container 12, and flows into the outdoor heat exchanger 152. Therefore, the refrigerant gas dissipates heat and is depressurized by the expansion valve 154 and then flows into the indoor heat exchanger 156. The refrigerant evaporates in the indoor heat exchanger 156 and absorbs heat from the air circulated in the room, thereby exerting a cooling action to cool the room. Then, the refrigerant repeats a cycle in which the refrigerant leaves the indoor heat exchanger 156 and is sucked into the rotary compressor 110.

  As described above in detail, according to the present invention, the first and second rotary compression elements 32 and 34 perform the compression work, and the first operation mode in which only the first rotary compression element 32 performs the compression work. The performance and reliability of the compression system CS including the rotary compressor 110 that can be used by switching between the two operation modes can be improved.

  Thus, by configuring the refrigerant circuit of the air conditioner using the compression system CS, it is possible to improve the operation efficiency and performance of the air conditioner and to reduce power consumption.

  In each of the above embodiments, an HFC or HC refrigerant is used as the refrigerant. However, a refrigerant having a large difference in high and low pressures such as carbon dioxide, for example, a combination of carbon dioxide and PAG (polyalkyl glycol) is used as the refrigerant. It does n’t matter what you do. In this case, since the refrigerant compressed by the rotary compression elements 32 and 34 has a very high pressure, the discharge silencer chamber 62 has a shape in which the upper side of the upper support member 54 is covered by the cup member 63 as in the above embodiments. Then, the cup member 63 may be damaged by the high pressure.

  For this reason, if the shape of the discharge muffler chamber on the upper side of the upper support member 54 where the refrigerant compressed by the rotary compression elements 32 and 34 joins is as shown in FIG. 8, pressure resistance can be secured. become able to. That is, the discharge silencing chamber 162 in FIG. 8 is configured by forming a recessed portion on the upper side of the upper support member 54 and closing the recessed portion with an upper cover 66 as a cover. Thereby, even if it is a case where a refrigerant | coolant with a large high-low pressure difference is contained like carbon dioxide, this invention becomes applicable.

  In each of the above-described embodiments, the rotary compressor 16 has been described as a vertical type, but it goes without saying that the present invention can also be applied to the case where a rotary compressor having a horizontal type as the rotary shaft is used.

  Furthermore, although the two-cylinder rotary compressor is used in each of the above-described embodiments, the present invention may be applied to a compression system including a multi-cylinder rotary compressor including three or more rotary compression elements.

It is a vertical side view of the multi-cylinder rotary compressor of the compression system of Example 1 of this invention. It is a vertical side view of the multi-cylinder rotary compressor of FIG. It is a refrigerant circuit diagram of the air conditioner using the compression system of the Example of this invention. It is a figure which shows the flow of the refrigerant | coolant in the 1st operation mode of the multicylinder rotary compressor of FIG. It is a vertical side view of the multi-cylinder rotary compressor of the compression system of Example 2 of this invention. It is a figure which shows the flow of the refrigerant | coolant in the 1st operation mode of the multicylinder rotary compressor of FIG. It is a figure which shows the flow of the refrigerant | coolant in the 2nd operation mode of the multicylinder rotary compressor of FIG. It is a vertical side view of the multi-cylinder rotary compressor of the compression system of Example 3 of this invention. It is a figure which shows the flow of the refrigerant | coolant at the time of 2 cylinder operation | movement of the conventional multi-cylinder rotary compressor. It is a figure which shows the flow of the refrigerant | coolant at the time of 1 cylinder operation | movement of the conventional multi-cylinder rotary compressor.

Explanation of symbols

CS compression system 10, 110 Rotary compressor 12 Sealed container 14 Electric element 16 Rotating shaft 18 Rotational compression mechanism 20 Terminal 22 Stator 24 Rotor 26 Laminated body 28 Stator coil 30 Laminated body 32 First rotational compression element 34 Second rotational compression Element 36 Intermediate divider 38 First cylinder 40 Second cylinder 42, 44 Eccentric portion 46 First roller 48 Second roller 50 First vane 52 Second vane 58, 60 Suction passages 62, 64, 162 Discharge silencer chamber 63 Cup member 66 Upper cover 68 Lower cover 70, 72 Guide groove 70A Storage portion 72A Back pressure chamber 74 Spring 75 Pipe 92, 94 Refrigerant inlet pipe 96 Refrigerant discharge pipe 100, 101, 102 Refrigerant pipe 105, 106, 200 Solenoid valve 152 Outdoor heat exchanger 154 Expansion valve 156 indoor heat exchanger 210 Controller

Claims (4)

A drive element and first and second rotary compression elements driven by a rotation shaft of the drive element are housed in a sealed container, and the first and second rotary compression elements are arranged as first and second cylinders. A first roller and a second roller which are fitted into an eccentric portion formed on the rotating shaft and rotate eccentrically in the cylinders, and abutting the first and second rollers, and in the cylinders Are composed of first and second vanes that are divided into a low-pressure chamber side and a high-pressure chamber side, respectively, and only the first vane is urged to the first roller by a spring member, and the rotary compression element Has a multi-cylinder rotary compressor that can be used by switching between a first operation mode in which compression work is performed and a second operation mode in which only the first rotary compression element performs compression work. In the compression system,
In the first operation mode, an intermediate pressure between the suction side pressure and the discharge side pressure of the rotary compression elements is applied as the back pressure of the second vane. A drive element and first and second rotary compression elements driven by a rotation shaft of the drive element are housed in a sealed container, and the first and second rotary compression elements are arranged as first and second cylinders. A first roller and a second roller which are fitted into an eccentric portion formed on the rotating shaft and rotate eccentrically in the cylinders, and abutting the first and second rollers, and in the cylinders Are composed of first and second vanes that are divided into a low-pressure chamber side and a high-pressure chamber side, respectively, and only the first vane is urged to the first roller by a spring member, and the rotary compression element Has a multi-cylinder rotary compressor that can be used by switching between a first operation mode in which compression work is performed and a second operation mode in which only the first rotary compression element performs compression work. In the compression system,
Providing a valve device for controlling refrigerant flow to the second cylinder;
In the second operation mode, the valve device prevents the refrigerant from flowing into the second cylinder, and applies the suction side pressure of the first rotary compression element as the back pressure of the second vane. A compression system characterized by that. A drive element and first and second rotary compression elements driven by a rotation shaft of the drive element are housed in a sealed container, and the first and second rotary compression elements are arranged as first and second cylinders. A first roller and a second roller which are fitted into an eccentric portion formed on the rotating shaft and rotate eccentrically in the cylinders, and abutting the first and second rollers, and in the cylinders Are composed of first and second vanes that are divided into a low-pressure chamber side and a high-pressure chamber side, respectively, and only the first vane is urged to the first roller by a spring member, thereby Has a multi-cylinder rotary compressor that can be used by switching between a first operation mode in which compression work is performed and a second operation mode in which only the first rotary compression element performs compression work. In the compression system,
Providing a valve device for controlling refrigerant flow to the second cylinder;
In the first operation mode, the valve device causes the refrigerant to flow into the second cylinder, and the back pressure of the second vane is the suction side pressure and the discharge side pressure of the rotary compression elements. While applying an intermediate pressure between
In the second operation mode, the valve device prevents the refrigerant from flowing into the second cylinder, and uses the suction side pressure of the first rotary compression element as the back pressure of the second vane. A compression system characterized by applying.   A refrigeration apparatus comprising a refrigerant circuit using the compression system according to claim 1.

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