US20140099218A1 - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- US20140099218A1 US20140099218A1 US14/124,494 US201214124494A US2014099218A1 US 20140099218 A1 US20140099218 A1 US 20140099218A1 US 201214124494 A US201214124494 A US 201214124494A US 2014099218 A1 US2014099218 A1 US 2014099218A1
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- Prior art keywords
- rotary compressor
- rotations
- valve
- operation chamber
- suction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/40—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member
- F04C18/46—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member with vanes hinged to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
- F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
Definitions
- the present invention relates to a rotary compressor.
- a motor of a compressor is usually controlled by an inverter and a microcomputer. If the number of rotations of the motor is reduced, it is possible to operate, with sufficiently lower ability than rating, a refrigeration cycle apparatus in which the compressor is used.
- Patent documents 1 and 2 provide one technique for operating the refrigeration cycle apparatus with a low ability using a method which is different from the inverter control.
- FIG. 8 is a partially cut-away sectional view showing a configuration of the compressor described in patent document 1.
- the compressor 601 includes a partition vane 615 , a partition vane spring 616 , a discharge port 617 , a discharge pipe 618 and an opening 619 .
- the partition vane 615 partitions a cylinder 608 into a low pressure chamber and a high pressure chamber.
- the opening 619 opens at an intermediate portion of the cylinder 608 , and is in communication with an opening/closing mechanism 620 provided in the opening 619 .
- the opening/closing mechanism 620 is composed of a plunger 621 and a plunger spring 622 . In a state where high pressure gas is not introduced into the plunger 621 from a high pressure-induction pipe 623 , the opening 619 and a suction port 612 are connected to each other through a bypass path 624 .
- a four-way valve 625 , a utilization-side heat exchanger 626 , a decompressor 627 , a heat source-side heat exchanger 628 , an accumulator 611 and a suction pipe 629 are connected to the compressor 601 through the discharge pipe 618 .
- the discharge pipe 618 , an intermediate portion of the four-way valve 625 and the high pressure-induction pipe 623 are connected to one another through a solenoid valve 630 .
- a piston 607 rotates in a direction of an arrow A.
- FIG. 9 is a vertical sectional view of a compressor described in patent document 2.
- a first discharge port 714 is formed in a cylinder 710
- a second discharge port 723 is formed in a main bearing 720 such that the second discharge port 723 is in communication with the first discharge port 714 so that compressed gas is discharged into a casing 701 .
- a bypass hole 722 having a bypass valve 780 between the first discharge port 714 and the second discharge port 723 is formed in the main bearing 720 .
- One technique for enhancing efficiency of a refrigeration cycle apparatus is to enhance efficiency of a compressor.
- the efficiency of the compressor largely depends on efficiency of a motor used in the compressor. Many motors exert high efficiency with the number of rotations close to the rated number of rotations (e.g., 60 Hz). Hence, if the motor is driven with low number of rotations (e.g., 30 Hz) using an inverter or the like, it can not be expected to enhance the efficiency of the compressor.
- the refrigeration cycle apparatus When the refrigeration cycle apparatus is operated with ability lower than rated ability (e.g., 30% or less of rated ability), the number of rotations of the rotary compressor is reduced and vibration caused by torque variation is increased, and the rotary compressor cannot be operated with further lower number of rotations (e.g., 20 Hz or less). As a result, the rotary compressor is intermittently operated in such a manner that operation and rest are repeated, and efficiency of the refrigeration cycle apparatus is largely deteriorated.
- ability lower than rated ability e.g. 30% or less of rated ability
- the number of rotations of the rotary compressor is reduced and vibration caused by torque variation is increased, and the rotary compressor cannot be operated with further lower number of rotations (e.g., 20 Hz or less).
- the rotary compressor is intermittently operated in such a manner that operation and rest are repeated, and efficiency of the refrigeration cycle apparatus is largely deteriorated.
- the present invention provides a rotary compressor in which a compression mechanism includes: a cylinder; a piston disposed in the cylinder; a frame which rotatably holds a shaft, which covers both upper and lower sides of the cylinder, and which forms an operation chamber between the frame and an inner peripheral surface of the cylinder; and a vane which partitions the operation chamber into a suction chamber and a compression-discharge chamber, and in which a motor operates the piston through the shaft
- the rotary compressor includes: a hermetic container in which the compression mechanism and the motor are accommodated; a suction path for guiding working fluid to be compressed to the suction chamber; a discharge port which is provided in the frame, and through which compressed working fluid flows out from the operation chamber; an interior space which is partitioned from an interior of the hermetic container and the operation chamber; a communication passage between the interior space and the suction path; a first passage between the discharge port and the interior space; a first check valve which prohibits working fluid passing through the first passage from returning from
- the present invention by making working fluid return from the operation chamber to the suction path using the communication passage, it is possible to operate the rotary compressor with relatively small suction volume. If working fluid is prohibited to return from the operation chamber to the suction path on the other hand, it is possible to operate the rotary compressor with relatively large suction volume, i.e., with normal suction volume.
- the control mechanism and the inverter are controlled such that reduction of the suction volume is compensated by increase in the number of rotations of the motor, the suction volume is reduced instead of driving the motor with the low number of rotations. Therefore, it is possible to provide a rotary compressor capable of exerting high efficiency from high ability to low ability of a refrigeration cycle apparatus.
- the present invention since there is no opening which opens toward the cylinder, it is possible to prevent the efficiency of the compressor from being deteriorated by dead volume. It is possible to secure the strength of the cylinder, and to prevent galling between parts and abnormal wearing of parts which may be caused due to deformation caused by pressure or temperature at the time of operation.
- FIG. 1 is a vertical sectional view of a rotary compressor according to a first embodiment
- FIG. 2 is a vertical sectional view of a rotary compressor according to a second embodiment
- FIG. 3A is a control flowchart of a control unit (on-off valve) and an inverter;
- FIG. 3B is another control flowchart of the control unit (on-off valve) and the inverter;
- FIG. 4 is a graph showing a relation between ability of a rotary compressor, suction volume of a compression mechanism, a state of an on-off valve and the number of rotations of a motor;
- FIG. 5 is a graph showing a relation between ability of the rotary compressor and efficiency of the rotary compressor
- FIG. 6 is a vertical sectional view of a rotary compressor according to a third embodiment
- FIG. 7 is a block diagram of a refrigeration cycle apparatus using the rotary compressor of the third embodiment.
- FIG. 8 is a partial sectional view showing a configuration of a conventional compressor.
- FIG. 9 is a vertical sectional view of another conventional compressor.
- a rotary compressor 100 of a first embodiment includes a compressor body 40 , an accumulator 12 , a discharge path 11 , a suction path 14 , a communication passage 16 , a control mechanism 30 , an inverter 42 and a control unit 44 .
- the compressor body 40 includes a hermetic container 1 , a motor 2 , a compression mechanism 3 and a shaft 4 .
- the compression mechanism 3 is disposed at a lower location in the hermetic container 1 .
- the motor is disposed above the compression mechanism 3 .
- the compression mechanism 3 and the motor 2 are connected to each other through the shaft 4 .
- An upper portion of the hermetic container 1 is provided with a terminal 21 for supplying electricity to the motor 2 .
- An oil reservoir 22 in which lubricant oil is held is formed in a bottom of the hermetic container 1 .
- the compressor body 40 has a so-called hermetic compressor structure.
- the discharge path 11 , the suction path 14 and the communication passage 16 are respectively composed of refrigerant pipes.
- the discharge path 11 penetrates an upper portion of the hermetic container 1 , and opens in the hermetic container 1 .
- the discharge path 11 guides compressed working fluid (typically, refrigerant) to outside of the compressor body 40 .
- the suction path 14 has one end connected to the compression mechanism 3 and the other end connected to the accumulator 12 .
- the suction path 14 penetrates a barrel of the hermetic container 1 .
- the suction path 14 guides refrigerant to be compressed from the accumulator 12 to an operation chamber 25 of the compression mechanism 3 .
- the communication passage 16 has one end connected to the compression mechanism 3 at a position different from that of the suction path 14 , and the other end connected to the accumulator 12 .
- the communication passage 16 penetrates the barrel of the hermetic container 1 .
- the communication passage 16 returns refrigerant which is once sucked into the operation chamber 25 of the compression mechanism 3 to the suction path 14 before the refrigerant is compressed.
- the compression mechanism 3 is a positive displacement type fluid mechanism.
- the compression mechanism 3 is driven by the motor 2 and compresses refrigerant.
- the compression mechanism 3 is composed of a cylinder 5 , a piston 8 , a vane 9 , a spring 10 , an upper frame 6 and a lower frame 7 .
- the piston 8 fitted over an eccentric portion 4 a of the shaft 4 is disposed in the cylinder 5 .
- the operation chamber 25 is formed between an outer peripheral surface of the piston 8 and an inner peripheral surface of the cylinder 5 .
- a vane groove (not shown) is formed in the cylinder 5 .
- the vane 9 has a tip end which comes into contact with the outer peripheral surface of the piston 8 , and the vane 9 is accommodated in the vane groove.
- the spring 10 is disposed in the vane groove. The vane 9 is pushed toward the piston 8 .
- the upper frame 6 and the lower frame 7 are respectively provided on an upper side and a lower side of the cylinder 5 such that the upper frame 6 and the lower frame 7 sandwich the cylinder 5 to cover the same.
- the operation chamber 25 between the cylinder 5 and the piston 8 is partitioned by the vane 9 . According to this, the operation chamber 25 (suction chamber) and the operation chamber 25 (compression-discharge chamber) are formed. Refrigerant to be compressed is guided to the operation chamber 25 (suction chamber) through the suction path 14 . Compressed refrigerant flows out from the operation chamber 25 (compression-discharge chamber) and from a discharge port 29 formed in the upper frame 6 .
- the interior space 28 which is partitioned from an interior of the hermetic container 1 and the operation chamber 25 is provided in the upper frame 6 on the opposite side from the operation chamber 25 , a first passage 34 a is formed between the discharge port 29 and the interior space 28 , and the interior space 28 and the discharge port 29 are in communication with each other.
- the first passage 34 a is provided with a first check valve 35 a to prevent refrigerant from flowing from the interior space 28 to the operation chamber 25 .
- a second passage 34 b is formed between the interior space 28 and the interior of the hermetic container 1 , and the interior space 28 and the interior of the hermetic container 1 are in communication with each other.
- the second passage 34 b is provided with a second check valve 35 b to prevent refrigerant from flowing from the interior of the hermetic container 1 to the interior space 28 .
- the vane 9 may be integral with the piston 8 . That is, the piston 8 and the vane 9 may be composed of a swing piston, or the vane 9 and the piston 8 may be joined to each other.
- the motor 2 is composed of a stator 17 and a rotor 18 .
- the stator 17 is fixed to an inner peripheral surface of the hermetic container 1 .
- the rotor 18 is fixed to the shaft 4 and rotates together with the shaft 4 .
- the piston 8 is moved in the cylinder 5 by the motor 2 .
- As the motor 2 it is possible to use a motor whose number of rotations can be changed. Examples of such a motor are an IPMSM (Interior Permanent Magnet Synchronous Motor) and an SPMSM (Surface Permanent Magnet Synchronous Motor).
- the control unit 44 controls the inverter 42 and adjusts the number of rotations of the motor 2 , i.e., the number of rotations of the rotary compressor 100 .
- the control unit 44 it is possible to use a DSP (Digital Signal Processor) including an A/D conversion circuit, an input/output circuit, a computation circuit and a storage unit.
- DSP Digital Signal Processor
- the accumulator 12 is composed of an accumulation container 12 a and an introduction pipe 12 b .
- the accumulation container 12 a includes an interior space capable of holding liquid refrigerant and gas refrigerant.
- the introduction pipe 12 b penetrates an upper portion of the accumulation container 12 a , and opens toward the interior space of the accumulation container 12 a .
- the other end of the suction path 14 and the other end of the communication passage 16 are connected to the accumulator 12 .
- the other end of the suction path 14 and the other end of the communication passage 16 penetrate a bottom of the accumulation container 12 a , upwardly extend from the bottom of the accumulation container 12 a , and open in the interior space of the accumulation container 12 a at given heights.
- the communication passage 16 is connected to the suction path 14 through the interior space of the accumulator 12 .
- other member such as a baffle may be provided in the accumulation container 12 a .
- the communication passage 16 may be connected directly to the suction path 14 or the introduction pipe 12 b.
- the control mechanism 30 is provided in the communication passage 16 at a location outside of the compressor body 40 .
- the control mechanism 30 is composed of an on-off valve 32 .
- One end of the communication passage 16 which is connected to the compression mechanism 3 is in communication with the interior space 28 .
- the control mechanism 30 changes a suction volume of the rotary compressor 100 .
- the first check valve 35 a opens and refrigerant is discharged to outside of the operation chamber 25 .
- the discharged refrigerant is returned to the suction path 14 through the communication passage 16 .
- pressure in the operation chamber 25 does not rise.
- the rotary compressor 100 is operated in a state where its suction volume is substantially zero.
- the rotary compressor 100 of this embodiment controls the inverter 42 and adjusts the number of rotations of the motor 2 , i.e., the number of rotations of the rotary compressor 100 .
- the number of rotations of the rotary compressor 100 is reduced, this reduction increases the vibration caused by torque variation, and the rotary compressor 100 can not be operated with further lower number of rotations (e.g., 20 HZ or less).
- the rotary compressor 100 is intermittently operation in such a manner that operation and rest are repeated, and efficiency of the refrigeration cycle apparatus is largely deteriorated.
- the rotary compressor 100 of this embodiment can realize a so-called digital compressor technique in which a case where the rotary compressor 100 is operated with substantially zero suction volume by opening the on-off valve 32 and a case where the rotary compressor 100 is operated with a normal suction volume by closing the on-off valve 32 are combined to control the ability.
- the on-off valve 32 is opened and closed. For example, by opening the on-off valve 32 for five seconds and closing the on-off valve 32 for five seconds, the ability of operation for total ten seconds can be made 50%. As a result, even when the refrigeration cycle apparatus is operated with ability lower than the rated ability, since the rotary compressor 100 can continuously be operated, the refrigeration cycle apparatus can be operated efficiently.
- the rotary compressor 100 of this embodiment When the rotary compressor 100 of this embodiment is operated with a normal suction volume by closing the on-off valve 32 , since there is no opening facing the cylinder 5 , it is possible to prevent the efficiency of the compressor from being deteriorated by dead volume. That is, in the normal rotary compressor 100 , the operation chamber 25 between the cylinder 5 and the piston 8 is partitioned by the vane 9 and according to this, the operation chamber 25 (suction chamber) and the operation chamber 25 (compression-discharge chamber) are formed. Refrigerant to be compressed is guided to the operation chamber 25 (suction chamber) through the suction path 14 .
- refrigerant in the operation chamber 25 is held in the opening when the opening is in communication with the operation chamber 25 (compression-discharge chamber), but if the opening is brought into communication with the operation chamber 25 (suction chamber), since pressure of refrigerant in the opening is higher than pressure of refrigerant in the operation chamber 25 (suction chamber), refrigerant in the opening reversely flows toward the operation chamber 25 (suction chamber). At this time, the refrigerant in the operation chamber 25 (suction chamber) is reduced and volume efficiency is deteriorated. Since the refrigerant in the opening is not discharged into the hermetic container 1 , compression power is lost correspondingly and input of the compressor is increased. This series of loss is called efficiency reduction of a compressor caused by dead volume.
- a height of the cylinder 5 is not limited by a configuration of the check valve.
- the first check valve 35 a and the second check valve 35 b are configured in an end surface direction. According to this configuration, since refrigerant which flows out from the discharge port 29 can smoothly flow into the interior space 29 and the hermetic container 1 , it is possible to provide a rotary compressor 100 capable of suppressing a loss caused when refrigerant is discharged from the operation chamber 25 and capable of exerting high efficiency.
- the rotary compressor 100 of this embodiment is configured such that when it is operated with the normal suction volume by closing the on-off valve 32 , a cross-sectional area of the second passage 34 b becomes greater than that of the first passage 34 a .
- a cross-sectional area of the second passage 34 b becomes greater than that of the first passage 34 a .
- the first passage 34 a opens at the cylinder 5 , if the cross-sectional area of the first passage 34 a is increased, efficiency of the compressor is deteriorated by the dead volume. If the cross-sectional area of the first passage 34 a is reduced on the other hand, pressure in the operation chamber 25 rises higher than discharge pressure by resistance of refrigerant which flows out from the operation chamber 25 through the discharge port 29 , and compression power is increased.
- the cross-sectional area of the first passage 34 a is determined such that the efficiency of the rotary compressor 100 becomes the highest.
- the second passage 34 b is provided between the interior space 29 and the interior of the hermetic container 1 , the efficiency of the compressor is not deteriorated by the dead volume. That is, by suppressing pressure rise in the interior space 29 by the resistance of refrigerant which flows out through the second passage 34 b , performance of the rotary compressor 100 is enhanced.
- the cross-sectional area of the second passage 34 b greater than that of the first passage 34 a , it is possible to provide the rotary compressor 100 capable of exerting high efficiency.
- the first check valve 35 a and the second check valve 35 b can be composed of reed valves which are composed of reed portions 36 a and 36 b and valve stoppers 37 a and 37 b , respectively.
- a check valve of another type there is a free valve (not shown) composed of a valve body, a guide and a spring.
- the check valve can be composed of a plunger and a plunger spring (not shown). If the plunger and the plunger spring are used, since the check valve can always be opened, it is possible to reduce a pressure loss generated in the check valve.
- the free valve is characterized in that a pressure loss when working fluid passes therethrough can be made smaller than that of a reed valve.
- a so-called “ability variable technique based on switching of a suction volume” is used.
- this technique a portion of refrigerant which is compressed by the cylinder 5 is made to bypass to outside of the cylinder 5 , thereby changing a suction volume of the operation chamber 25 .
- the on-off valve 32 is opened and closed. For example, by opening the on-off valve 32 for three seconds and closing the on-off valve 32 for seven seconds, the ability of operation for total ten seconds can be made 70%.
- the ability is controlled using the ability variable technique based on switching of the suction volume as described above, it is necessary that the time during which the rotary compressor 100 is operated with substantially zero suction volume is set to 30% by opening the on-off valve 32 . At this time, since the rotary compressor 100 keeps rotating, a machine loss is generated to drive the compression mechanism 3 even if power for compressing refrigerant becomes zero.
- the on-off valve 32 is opened and closed in the rotary compressor 100 of this embodiment. For example, by opening the on-off valve 32 for five seconds and closing the on-off valve 32 for five seconds, the ability of operation for total ten seconds can be made 50%.
- the ability variable technique based on the switching of the suction volume and the inverter 42 which drives the motor 2 with an arbitrary number of rotations are appropriately separately used depending upon situations.
- the ability variable technique based on the switching of the suction volume is selected when the refrigeration cycle apparatus is operated with 70% ability
- the inverter 42 which drives the motor 2 with an arbitrary number of rotations is selected when the refrigeration cycle apparatus is operated with 50% ability, but the invention is not limited to this embodiment.
- Concerning a question as to which one of the ability variable technique and the inverter should used for controlling the ability of the refrigeration cycle it is preferable to select one of them which can operate the refrigeration cycle apparatus more efficiently.
- a rotary compressor 200 of a second embodiment includes a second compression mechanism 33 in addition to the compression mechanism 3 described in the first embodiment.
- “first” is added to the elements of the compression mechanism 3 described in the first embodiment.
- the cylinder 5 is described as a first cylinder 5
- the piston 8 is described as a first piston 8
- the vane 9 is described as a first vane 9
- the operation chamber 25 is described as a first operation chamber 25
- the compression mechanism 3 is described as a first compression mechanism 3 .
- the second compression mechanism 33 is composed of a second cylinder 55 , a second piston 58 , a second vane 59 and a second spring 60 .
- the second cylinder 55 is disposed concentrically with the first cylinder 5 .
- a second piston 58 fitted over a second eccentric portion 4 b of a shaft 4 is disposed in the second cylinder 55 .
- a second operation chamber 75 is formed between an outer peripheral surface of the second piston 58 and an inner peripheral surface of the second cylinder 55 .
- a second vane groove (not shown) is formed in the second cylinder 55 .
- a second vane 59 is accommodated in the second vane groove.
- a tip end of the second vane 59 is in contact with the outer peripheral surface of the second piston 58 .
- a second spring 60 is disposed in the second vane groove.
- the second spring 60 pushes the second vane 59 toward the second piston 58 .
- a second operation chamber 75 between the second cylinder 55 and the second piston 58 is partitioned by the second vane 59 .
- a second operation chamber 75 (second suction chamber) and a second operation chamber 75 (second compression-discharge chamber) are formed.
- Refrigerant to be compressed is guided to the second operation chamber 75 (second suction chamber) through a second suction path 15 .
- a second discharge port 79 is formed in an upper frame 6 . According to this, compressed refrigerant is guided from the second operation chamber 75 (second compression-discharge chamber) into the hermetic container 1 through the second discharge port 79 .
- a discharge valve 35 c is provided in the second discharge port 79 . According to this, refrigerant does not reversely flow from the hermetic container 1 into the second operation chamber 75 .
- first compression mechanism 3 refrigerant to be compressed is guided to the first operation chamber 25 (suction chamber) through the first suction path 14 .
- Compressed refrigerant flows out from a first discharge port 29 which is formed from the first operation chamber 25 (compression-discharge chamber) to the lower frame 7 .
- the interior space 28 which is partitioned from an interior of the hermetic container 1 , the first operation chamber 25 and the second operation chamber 75 is provided in the upper frame 7 on the opposite side from the operation chamber 25 , a first passage 34 a is formed between the discharge port 29 and the interior space 28 , and the interior space 28 and the discharge port 29 are in communication with each other.
- the first passage 34 a is provided with a first check valve 35 a to prevent refrigerant from flowing from the interior space 28 to the first operation chamber 25 .
- a second passage 34 b is formed between the interior space 28 and the interior of the hermetic container 1 , and the interior space 28 and the interior of the hermetic container 1 are in communication with each other.
- the second passage 34 b is provided with a second check valve 35 b to prevent refrigerant from flowing from the interior of the hermetic container 1 to the interior space 28 .
- the first operation chamber 25 is located in the vertically downward direction with respect to the second operation chamber 75 . This is because when the refrigeration cycle apparatus operated with low ability, since only suction refrigerant passes through the first operation chamber 25 , temperature of the cylinder becomes low. Further, this is because if the low temperature cylinder is located at a low location, it is possible to restrain the suction refrigerant from receiving heat from discharged refrigerant from a standpoint of temperature stratification.
- the lower frame 7 is covered with a muffler 23 .
- the muffler 23 has a space capable of receiving refrigerant which is compressed by the first compression mechanism 3 .
- a flow path 26 penetrates the lower frame 7 , the first cylinder 5 , a middle plate 53 , the second cylinder 55 and the upper frame 6 . According to this configuration, refrigerant moves from the space of the muffler 23 into the hermetic container 1 .
- a projecting direction of the first eccentric portion 4 a is deviated from a projecting direction of the second eccentric portion 4 b by 180°. That is, a phase of the first piston 8 is deviated from a phase of the second piston 58 by a rotation angle of the shaft of 180°.
- Refrigerant is supplied to the first compression mechanism 3 through the first suction path 14 .
- Refrigerant is supplied to the second compression mechanism 33 through the second suction path 15 .
- Refrigerant is compressed by the first compression mechanism 3 or the second compression mechanism 33 and discharged into the hermetic container 1 .
- the first suction path 14 and the second suction path 15 are connected to the accumulator 12 .
- One of the suction paths 14 and 15 may branch off from the other one inside or outside of the accumulator 12 .
- the communication passage 16 since the communication passage 16 is not connected to the second compression mechanism 33 , a suction volume of the second compression mechanism 33 is always constant.
- the communication passage 16 is connected only to the first compression mechanism 3 so that only a suction volume of the first compression mechanism 3 can be changed. According to this, production costs of the rotary compressor 200 can be suppressed.
- the communication passage 16 may be connected to the first compression mechanism 3 and the second compression mechanism 33 so that suction volumes of the first compression mechanism 3 and the second compression mechanism 33 can be changed.
- the first compression mechanism 3 is disposed on a side far from the motor 2 and the second compression mechanism 33 is disposed on a side close to the motor 2 . That is, the motor 2 , the second compression mechanism 33 and the first compression mechanism 3 are arranged in this order along an axial direction of the shaft 4 . Since the second compression mechanism 33 has the constant suction volume, the second compression mechanism 33 requires greater torque than that of the first compression mechanism 3 which can be operated with substantially zero suction volume. Therefore, since the second compression mechanism 33 is disposed on the side close to the motor 2 , a load which is applied to the shaft 4 when the first compression mechanism 3 is operated with the substantially zero suction volume is reduced. According to this, it is possible to reduce machine losses of the upper frame 6 and the lower frame 7 .
- first compression mechanism 3 which can be operated with the substantially zero suction volume is disposed on a lower side, it is possible to reduce a pressure loss which is generated when compressed refrigerant flows into the interior space 28 of the hermetic container 1 through the muffler 23 .
- a positional relation between the first compression mechanism 3 and the second compression mechanism 33 is not limited to the above-described relation.
- a normal suction volume of the first compression mechanism 3 and a suction volume of the second compression mechanism 33 are the same.
- a case where the first compression mechanism 3 is operated with substantially zero suction volume is defined as a low volume mode
- a case where the first compression mechanism 3 is operated with a normal suction volume is defined as a high volume mode.
- a suction volume in the high volume mode of the rotary compressor 200 is defined as V
- a suction volume in the low volume mode is V/2.
- step 1 the number of rotations of the motor 2 is adjusted in accordance with requested ability. More specifically, the number of rotations of the motor 2 is adjusted so that a necessary flow rate of refrigerant is obtained.
- steps 2 and 6 it is determined whether the number of rotations of the motor 2 is reduced or increased. If it is determined in step 2 that the number of rotations is reduced, the procedure proceeds on to step 3, and it is determined whether the current number of rotations is 30 Hz or less. If the current number of rotations is 30 Hz or less, it is determined in step 4 whether the on-off valve 32 is closed.
- step 5 processing to open the on-off valve 32 and processing to increase the number of rotations of the motor 2 to a double value of the current number of rotations are carried out.
- the order of the processing operations in step 5 is not especially limited, it is possible to increase the number of rotations of the motor 2 substantially at the same time when the on-off valve 32 is opened.
- step 2 If it is determined in step 2 that processing to increase the number of rotations is carried out on the other hand, the processing proceeds on to step 7, and it is determined whether the current number of rotations is 70 Hz or more. If the current number of rotations is 70 Hz or more, it is determined in step 8 whether the on-off valve 32 is opened. If the on-off valve 32 is opened, processing to close the on-off valve 32 and processing to reduce the number of rotations of the motor 2 to 1 ⁇ 2 of the current number of rotations are carried out in step 9. Although the order of the processing operations in step 9 is not especially limited, it is possible to reduce the number of rotations of the motor 2 substantially at the same time when the on-off valve 32 is closed.
- a suction volume of the compression mechanism 3 is “V”.
- the control unit 44 carries out processing concerning the on-off valve 32 to reduce the suction volume and processing concerning the inverter 42 to increase the number of rotations of the motor 2 .
- the processing concerning the on-off valve 32 to reduce the suction volume is processing to open the on-off valve 32 .
- the processing concerning the inverter 42 to increase the number of rotations of the motor 2 is processing to set the target number of rotations of the motor 2 to a double value of the last number of rotations.
- the control unit 44 controls the on-off valve 32 and the inverter 42 to compensate for the increase in the suction volume by reducing the number of rotations of the motor 2 .
- the control unit 44 carries out processing concerning the on-off valve 32 to increase the suction volume and processing concerning the inverter 42 to reduce the number of rotations of the motor 2 .
- the processing concerning the on-off valve 32 to increase the suction volume is processing to close the on-off valve 32 .
- the processing concerning the inverter 42 to reduce the number of rotations of the motor 2 is processing to set the target number of rotations of the motor 2 to 1 ⁇ 2 of the last number of rotations.
- the on-off valve 32 is opened and the number of rotations of the motor 2 is increased to 60 Hz. If the number of rotations of the motor 2 is increased to 70 Hz in a state where the on-off valve 32 is opened, the on-off valve 32 is closed and the number of rotations of the motor 2 is reduced to 35 Hz.
- the number of rotations when the on-off valve 32 is opened and the number of rotations of the motor 2 is increased is defined as the third number of rotations and the number of rotations when the on-off valve 32 is closed and the number of rotations of the motor 2 is reduced is defined as the fourth number of rotations
- a relation (first number of rotations) ⁇ (fourth number of rotations) and a relation (third number of rotations) ⁇ (second number of rotations) are established.
- the first number of rotations is set to 30 Hz or less, it is possible to operate the rotary compressor 200 with wider ability.
- a lower limit value of the first number of rotations is not especially limited, but an example of the lower limit value is 20 Hz.
- the inverter 42 is controlled to compensate for reduction of the suction volume by increasing the number of rotations of the motor 2 . According to this, it becomes unnecessary to largely reduce the number of rotations of the motor 2 even when the refrigeration cycle apparatus is operated with ability lower than the rated ability. That is, even when the refrigeration cycle apparatus is operated with low ability, it is possible to drive the motor 2 with the number of rotations capable of exerting high efficiency. Therefore, efficiency of the rotary compressor 200 is also enhanced.
- the rotary compressor 200 in this embodiment can exert high efficiency even when the rotary compressor 200 is operated with low ability.
- the rated ability of the rotary compressor 200 is defined as “100%”. If the rated ability is a criterion, the efficiency of the rotary compressor 200 is lowered as the ability to be exerted is lowered, i.e., as the number of rotations of the motor 2 is reduced. As shown by broken lines, when the motor 2 is driven with the number of rotations which is 50% or less of the rated number of rotations, the efficiency is largely deteriorated. In this embodiment, when relatively low ability is required, the motor 2 is operated in the low volume mode having a suction volume V/2.
- Heights of the first cylinder 5 and the second cylinder 55 may be made different from each other in accordance with a rate of suction volumes to be changed, and a normal suction volume of the first compression mechanism 3 and a suction volume of the second compression mechanism 33 may be changed. More specifically, when a suction volume of the first compression mechanism 3 is defined as V1 and a suction volume of the second compression mechanism 33 is defined as V2, a suction volume VH in the high volume mode is V1+V2, and a suction volume VL in the low volume mode is V2. Usually, it is preferable that a ratio (VL/VH) of the suction volume VL in the low volume mode to the suction volume VH in the high volume mode is in a range of 0.2 to 0.8.
- the suction volume of the first compression mechanism 3 is defined as V1 and the suction volume of the second compression mechanism 33 is defined as V2, the suction volume in the high volume mode is V1+V2, and the suction volume in the low volume mode is V2. This situation will be discussed below.
- the number of rotations of the motor 2 can be adjusted in accordance with the ratio (VL/VH) of the suction volume VL in the low volume mode to the suction volume VH in the high volume mode.
- the number of rotations (target number of rotations) of the motor 2 is set to the number of rotations which is obtained by dividing the number of rotations of the motor 2 immediately before the switching operation between the modes by the ratio (VL/VH).
- the number of rotations of the motor 2 is set to the number of rotations which is obtained by multiplying the number of rotations of the motor 2 immediately before the switching operation between the modes by the ratio (VL/VH). According to this, it is possible to smoothly switch between the operation modes of the high volume mode and the low volume mode.
- This embodiment does not have ability in which the control mechanism 30 decompresses refrigerant. Sucked refrigerant is not substantially compressed in the compression-discharge chamber and returned into the first suction path 14 through the communication passage 16 . Therefore, deterioration in efficiency caused by a pressure loss is extremely small.
- the embodiment may have the ability in which the control mechanism 30 decompresses refrigerant only within a range not largely affecting the efficiency of the rotary compressor 200 .
- the control unit 44 may carry out the processing concerning the on-off valve 32 to reduce the suction volume and the processing concerning the inverter 42 to increase the number of rotations of the motor 2 . That is, the control unit 44 determines whether it is necessary to switch between the modes before the number of rotations of the motor 2 is actually reduced to the first number of rotations.
- control unit 44 may carry out the processing concerning the on-off valve 32 to increase the suction volume and the processing concerning the inverter 42 to reduce the number of rotations of the motor 2 . That is, the control unit 44 determines whether it is necessary to switch between the modes before the number of rotations of the motor 2 is actually increased to the second number of rotations. An example of such control will be described with reference to FIG. 3B .
- the necessary number of rotations of the motor 2 is first calculated in step 11.
- “necessary number of rotations” means the number of rotations for obtaining a necessary flow rate of refrigerant.
- the necessary number of rotations is equal to or less than the first number of rotations (e.g., 30 Hz). If the necessary number of rotations is equal to or less than the first number of rotations, it is determined in step 13 whether the on-off valve 32 is closed. If the on-off valve 32 is closed, in step 15, the on-off valve 32 is opened and the number of rotations of the motor 2 is adjusted to a value capable of obtaining a necessary flow rate of refrigerant. If the on-off valve 32 is opened, only the number of rotations of the motor 2 is adjusted in step 14.
- step 16 determines whether the necessary number of rotations is equal to or more than the second number of rotations (e.g., 70 Hz). If the necessary number of rotations is equal to or more than the second number of rotations, it is determined in step 17 whether the on-off valve 32 is opened. If the on-off valve 32 is opened, in step 18, the on-off valve 32 is closed and the number of rotations of the motor 2 is adjusted to a value capable of obtaining the necessary flow rate of refrigerant. If the on-off valve 32 closed, only the number of rotations of the motor 2 is adjusted in step 19.
- the second number of rotations e.g. 70 Hz
- the rotary compressor 100 can exert high efficiency also when low ability is required (when, is small) as shown by solid lines in FIG. 5 .
- the rated ability of the rotary compressor 100 is defined as “100%”. If the rated ability is defined as a criterion, the efficiency of the rotary compressor 100 is lowered as the as ability to be exerted is reduced, i.e., as the number of rotations of the motor 2 is reduced. As shown by the broken lines, when the motor 2 is driven with the number of rotations which is 50% or less of the rated number of rotations, the efficiency is largely lowered.
- the operation when relatively low ability is required, the operation is carried out in the low volume mode with the suction volume V/2. According to this, the motor 2 can be driven with the number of rotations which is close to the rated number of rotations as close as possible. Therefore, even in a region where necessary ability is 50% or less of the rated ability, the rotary compressor 100 can exert excellent efficiency.
- a rotary compressor 300 of a third embodiment includes a control mechanism 30 having a structure different from that of the rotary compressor 100 of the first embodiment.
- Other structures are the same as those described in the first embodiment.
- the rotary compressor 300 includes a communication passage 16 , a three-way valve 90 and a high pressure path 92 .
- the communication passage 16 is composed of an upstream portion 16 h which brings the three-way valve 90 and an interior space 28 into communication with each other, and a downstream portion which brings the three-way valve 90 and a suction path 14 into communication with each other.
- the high pressure path 92 has one end connected to the three-way valve 90 and the other end connected to an oil reservoir 22 .
- the high pressure path 92 is a path for supplying pressure which is equal to that of compressed refrigerant to an interior space 28 .
- the rotary compressor 300 of this embodiment is a so-called high pressure shell type compressor in which an interior of a hermetic container 1 is filled with compressed refrigerant. Oil having pressure which is substantially equal to that of compressed refrigerant is held in the oil reservoir 22 .
- the three-way valve 90 connects one of the suction path 14 and the high pressure path 92 to the upstream portion 16 h of the communication passage 16 . By controlling the three-way valve 90 , the rotary compressor 300 can be operated in any of a high volume mode and a low volume mode.
- the three-way valve 90 is controlled such that the suction path 14 is brought into communication with the upstream portion 16 h of the communication passage 16 .
- a first check valve 35 a opens, and refrigerant is discharged to outside of the operation chamber 25 .
- the discharged refrigerant returns to the suction path 14 through the communication passage 16 .
- pressure in the operation chamber 25 does not rise.
- the rotary compressor 300 is operated with substantially zero suction volume.
- the three-way valve 90 is controlled such that the high pressure path 92 is brought into communication with the upstream portion 16 h of the communication passage 16 .
- pressure of oil in the oil reservoir 22 is introduced into the interior space 28 .
- a suction stroke of refrigerant is completed, a compression stroke of refrigerant is immediately started.
- compressed refrigerant is discharged into the interior space 28 through a first passage 34 a .
- a second check valve 35 b opens and refrigerant is discharged into the hermetic container 1 .
- the rotary compressor 300 is operated with a normal suction volume.
- a portion between the three-way valve 90 and the high pressure path 92 is composed of a capillary tube (not shown) or the like having a relatively small cross-sectional area as compared with the communication passage 16 .
- Compressed refrigerant is discharged into the interior space 28 through the first passage 34 a , but if refrigerant-passage resistance of the high pressure path 92 is large, the second check valve 35 b smoothly opens, and refrigerant in the interior space 28 is discharged into the hermetic container 1 .
- the high pressure path 92 has one end connected to (opened toward) the oil reservoir 22 .
- the one end of the high pressure path 92 may be connected to any portion of the interior of the hermetic container 1 .
- the high pressure path 92 may be connected to a high pressure portion (e.g., a portion between the rotary compressor 300 and a radiator) of the refrigerant circuit.
- a sealing effect by oil can be obtained. This is preferable to prevent efficiency from being deteriorated by leakage of refrigerant.
- the three-way valve 90 is used as the control mechanism 30 in this embodiment, a four-way valve may be used.
- a refrigeration cycle apparatus 500 can be configured using the rotary compressor 100 .
- the refrigeration cycle apparatus 500 includes the rotary compressor 100 , a radiator 502 , an expansion mechanism 504 and an evaporator 506 . These devices are connected to one another in this order through refrigerant pipes to form a refrigerant circuit.
- the radiator 502 is composed of an air-refrigerant heat exchanger for example, and cools refrigerant which is compressed by the rotary compressor 100 .
- the expansion mechanism 504 is composed of an expansion valve, and expands refrigerant which is cooled by the radiator 502 .
- the evaporator 506 is composed of an air-refrigerant heat exchanger for example, and heats refrigerant which is expanded by the expansion mechanism 504 .
- the rotary compressors 200 and 300 of the second and third embodiments may be used instead of the rotary compressor 100 of the first embodiment.
- the present invention is effective for a compressor of a refrigeration cycle apparatus which can be utilized for a water heater, a hydronic heater and an air conditioner. Especially, the invention is effective for a compressor of the air conditioner which requires wide ability.
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Abstract
Description
- The present invention relates to a rotary compressor.
- A motor of a compressor is usually controlled by an inverter and a microcomputer. If the number of rotations of the motor is reduced, it is possible to operate, with sufficiently lower ability than rating, a refrigeration cycle apparatus in which the compressor is used.
Patent documents -
FIG. 8 is a partially cut-away sectional view showing a configuration of the compressor described inpatent document 1. The compressor 601 includes apartition vane 615, apartition vane spring 616, adischarge port 617, adischarge pipe 618 and anopening 619. The partition vane 615 partitions acylinder 608 into a low pressure chamber and a high pressure chamber. Theopening 619 opens at an intermediate portion of thecylinder 608, and is in communication with an opening/closing mechanism 620 provided in theopening 619. The opening/closing mechanism 620 is composed of aplunger 621 and aplunger spring 622. In a state where high pressure gas is not introduced into theplunger 621 from a high pressure-induction pipe 623, theopening 619 and asuction port 612 are connected to each other through abypass path 624. - A four-
way valve 625, a utilization-side heat exchanger 626, adecompressor 627, a heat source-side heat exchanger 628, anaccumulator 611 and asuction pipe 629 are connected to the compressor 601 through thedischarge pipe 618. Thedischarge pipe 618, an intermediate portion of the four-way valve 625 and the high pressure-induction pipe 623 are connected to one another through a solenoid valve 630. Apiston 607 rotates in a direction of an arrow A. - When the solenoid valve 630 opens, since high pressure gas is introduced into the high pressure-
induction pipe 623, theplunger 621 overcomes theplunger spring 622 and closes an opening 610 of thecylinder 608. At this time, most of refrigerant sucked from thesuction port 612 into thecylinder 608 is discharged into thedischarge pipe 618 through thedischarge port 617. - When the solenoid valve 630 closes on the other hand, a pressure difference in the compressor 601 is reduced, the
plunger 621 is returned to a position shown inFIG. 8 by a restoring force of theplunger spring 622. Thereafter, if the compressor 601 is operated again, high pressure gas is not introduced into the high pressure-induction pipe 623. Theopening 619 formed in an intermediate portion of thecylinder 608 is in communication with thesuction port 612 through thebypass path 624. As a result, a portion of refrigerant in thecylinder 608 is returned into thesuction port 612 through thebypass path 624 while the refrigerant is being compressed, and refrigerant discharged from thedischarge pipe 618 is largely reduced. According to this, it is possible to operate the refrigeration cycle apparatus with lower ability. -
FIG. 9 is a vertical sectional view of a compressor described inpatent document 2. Afirst discharge port 714 is formed in acylinder 710, and asecond discharge port 723 is formed in amain bearing 720 such that thesecond discharge port 723 is in communication with thefirst discharge port 714 so that compressed gas is discharged into acasing 701. A bypass hole 722 having abypass valve 780 between thefirst discharge port 714 and thesecond discharge port 723 is formed in themain bearing 720. - When the bypass hole 722 closes, most of refrigerant sucked from the
suction port 712 into thecylinder 710 is discharged into thecasing 701 through thefirst discharge port 714 and thesecond discharge port 723. - When high pressure is introduced into the
bypass valve 780 and the bypass hole 722 opens on the other hand, since refrigerant sucked from thesuction port 712 into thecylinder 710 is returned into thesuction port 712 through thefirst discharge port 714 and the bypass hole 722, refrigerant is not discharged into thecasing 701. According to this, it is possible to operate the refrigeration cycle apparatus with lower ability. -
- [Patent Document 1] Japanese Patent Application Laid-open No. S61-93285
- [Patent Document 2] Japanese Translation of PCT International Application, Publication No. 2008-509325
- One technique for enhancing efficiency of a refrigeration cycle apparatus is to enhance efficiency of a compressor. The efficiency of the compressor largely depends on efficiency of a motor used in the compressor. Many motors exert high efficiency with the number of rotations close to the rated number of rotations (e.g., 60 Hz). Hence, if the motor is driven with low number of rotations (e.g., 30 Hz) using an inverter or the like, it can not be expected to enhance the efficiency of the compressor. When the refrigeration cycle apparatus is operated with ability lower than rated ability (e.g., 30% or less of rated ability), the number of rotations of the rotary compressor is reduced and vibration caused by torque variation is increased, and the rotary compressor cannot be operated with further lower number of rotations (e.g., 20 Hz or less). As a result, the rotary compressor is intermittently operated in such a manner that operation and rest are repeated, and efficiency of the refrigeration cycle apparatus is largely deteriorated.
- In
patent document 1, when the solenoid valve 630 opens, high pressure gas is introduced into the high pressure-induction pipe 623, and theplunger 621 overcomes theplunger spring 622 and closes theopening 619 of thecylinder 608. However, a volume of theopening 619 becomes dead volume, and this deteriorates the efficiency of the compressor 601. - In
patent document 2, since thefirst discharge port 714 is formed in thecylinder 710, if attempt is made to reduce dead volume of the discharge port, strength of thecylinder 710 is lowered and this causes problems that galling between parts is caused or parts become abnormally worn due to deformation caused by pressure or temperature at the time of operation. If strength of thecylinder 710 is enhanced, dead volume of the discharge port increases, and this deteriorates efficiency of the compressor. To configure a first discharge valve for preventing back-flow of refrigerant from thefirst discharge port 714 to the compression chamber, it is necessary to secure a certain level of height of thecylinder 710. Especially when high density refrigerant such as R410 and carbon dioxide is used as refrigerant as working fluid, a load of a shaft or a vane is increased, a machine loss increases, a leakage loss while refrigerant is compressed increases and the efficiency of the compressor is deteriorated. - In view of such circumstances, it is an object of the present invention to provide a rotary compressor capable of exerting high efficiency from high ability to low ability of a refrigeration cycle apparatus.
- That is, the present invention provides a rotary compressor in which a compression mechanism includes: a cylinder; a piston disposed in the cylinder; a frame which rotatably holds a shaft, which covers both upper and lower sides of the cylinder, and which forms an operation chamber between the frame and an inner peripheral surface of the cylinder; and a vane which partitions the operation chamber into a suction chamber and a compression-discharge chamber, and in which a motor operates the piston through the shaft, wherein the rotary compressor includes: a hermetic container in which the compression mechanism and the motor are accommodated; a suction path for guiding working fluid to be compressed to the suction chamber; a discharge port which is provided in the frame, and through which compressed working fluid flows out from the operation chamber; an interior space which is partitioned from an interior of the hermetic container and the operation chamber; a communication passage between the interior space and the suction path; a first passage between the discharge port and the interior space; a first check valve which prohibits working fluid passing through the first passage from returning from the interior space to the discharge port; a second passage between the interior space and the interior of the hermetic container; a second check valve which prohibits working fluid passing through the second passage from returning from the interior of the hermetic container to the interior space; and a control mechanism which is provided in the communication passage and which controls pressure in the interior space.
- According to the present invention, by making working fluid return from the operation chamber to the suction path using the communication passage, it is possible to operate the rotary compressor with relatively small suction volume. If working fluid is prohibited to return from the operation chamber to the suction path on the other hand, it is possible to operate the rotary compressor with relatively large suction volume, i.e., with normal suction volume. When the control mechanism and the inverter are controlled such that reduction of the suction volume is compensated by increase in the number of rotations of the motor, the suction volume is reduced instead of driving the motor with the low number of rotations. Therefore, it is possible to provide a rotary compressor capable of exerting high efficiency from high ability to low ability of a refrigeration cycle apparatus.
- Further, according to the present invention, since there is no opening which opens toward the cylinder, it is possible to prevent the efficiency of the compressor from being deteriorated by dead volume. It is possible to secure the strength of the cylinder, and to prevent galling between parts and abnormal wearing of parts which may be caused due to deformation caused by pressure or temperature at the time of operation. Further, since it is possible to lower the height of the cylinder, if high density refrigerant such as R410A, carbon dioxide, R32, R407C, HFO-1234yf and R134a is used as refrigerant as the working fluid, since it is possible to prevent a machine loss from increasing by increase in a load of a shaft or a vane, and to prevent a leakage loss from increasing while refrigerant is compressed and therefore, it is possible to provide a rotary compressor capable of exerting high efficiency.
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FIG. 1 is a vertical sectional view of a rotary compressor according to a first embodiment; -
FIG. 2 is a vertical sectional view of a rotary compressor according to a second embodiment; -
FIG. 3A is a control flowchart of a control unit (on-off valve) and an inverter; -
FIG. 3B is another control flowchart of the control unit (on-off valve) and the inverter; -
FIG. 4 is a graph showing a relation between ability of a rotary compressor, suction volume of a compression mechanism, a state of an on-off valve and the number of rotations of a motor; -
FIG. 5 is a graph showing a relation between ability of the rotary compressor and efficiency of the rotary compressor; -
FIG. 6 is a vertical sectional view of a rotary compressor according to a third embodiment; -
FIG. 7 is a block diagram of a refrigeration cycle apparatus using the rotary compressor of the third embodiment; -
FIG. 8 is a partial sectional view showing a configuration of a conventional compressor; and -
FIG. 9 is a vertical sectional view of another conventional compressor. -
- 1 hermetic container
- 2 motor
- 3 compression mechanism
- 4 shaft
- 5 cylinder
- 6 upper frame
- 7 lower frame
- 8 piston
- 9 vane
- 12 accumulator
- 14 suction path
- 16 communication passage
- 22 oil reservoir
- 25 operation chamber
- 28 interior space
- 29 discharge port
- 30 control mechanism
- 32 on-off valve
- 34 a first passage
- 34 b second passage
- 35 a first check valve
- 35 b second check valve
- 40 compressor body
- 42 inverter
- 44 control unit
- 90 three-way valve
- 92 high pressure path
- 100, 200, 300 rotary compressor
- As shown in
FIG. 1 , arotary compressor 100 of a first embodiment includes acompressor body 40, anaccumulator 12, adischarge path 11, asuction path 14, acommunication passage 16, acontrol mechanism 30, aninverter 42 and acontrol unit 44. - The
compressor body 40 includes ahermetic container 1, amotor 2, acompression mechanism 3 and ashaft 4. Thecompression mechanism 3 is disposed at a lower location in thehermetic container 1. In thehermetic container 1, the motor is disposed above thecompression mechanism 3. Thecompression mechanism 3 and themotor 2 are connected to each other through theshaft 4. An upper portion of thehermetic container 1 is provided with a terminal 21 for supplying electricity to themotor 2. Anoil reservoir 22 in which lubricant oil is held is formed in a bottom of thehermetic container 1. Thecompressor body 40 has a so-called hermetic compressor structure. - The
discharge path 11, thesuction path 14 and thecommunication passage 16 are respectively composed of refrigerant pipes. - The
discharge path 11 penetrates an upper portion of thehermetic container 1, and opens in thehermetic container 1. Thedischarge path 11 guides compressed working fluid (typically, refrigerant) to outside of thecompressor body 40. Thesuction path 14 has one end connected to thecompression mechanism 3 and the other end connected to theaccumulator 12. - The
suction path 14 penetrates a barrel of thehermetic container 1. - The
suction path 14 guides refrigerant to be compressed from theaccumulator 12 to anoperation chamber 25 of thecompression mechanism 3. Thecommunication passage 16 has one end connected to thecompression mechanism 3 at a position different from that of thesuction path 14, and the other end connected to theaccumulator 12. Thecommunication passage 16 penetrates the barrel of thehermetic container 1. - The
communication passage 16 returns refrigerant which is once sucked into theoperation chamber 25 of thecompression mechanism 3 to thesuction path 14 before the refrigerant is compressed. - The
compression mechanism 3 is a positive displacement type fluid mechanism. Thecompression mechanism 3 is driven by themotor 2 and compresses refrigerant. As shown inFIG. 1 , thecompression mechanism 3 is composed of a cylinder 5, apiston 8, avane 9, aspring 10, anupper frame 6 and alower frame 7. Thepiston 8 fitted over aneccentric portion 4 a of theshaft 4 is disposed in the cylinder 5. Theoperation chamber 25 is formed between an outer peripheral surface of thepiston 8 and an inner peripheral surface of the cylinder 5. A vane groove (not shown) is formed in the cylinder 5. Thevane 9 has a tip end which comes into contact with the outer peripheral surface of thepiston 8, and thevane 9 is accommodated in the vane groove. Thespring 10 is disposed in the vane groove. Thevane 9 is pushed toward thepiston 8. - The
upper frame 6 and thelower frame 7 are respectively provided on an upper side and a lower side of the cylinder 5 such that theupper frame 6 and thelower frame 7 sandwich the cylinder 5 to cover the same. Theoperation chamber 25 between the cylinder 5 and thepiston 8 is partitioned by thevane 9. According to this, the operation chamber 25 (suction chamber) and the operation chamber 25 (compression-discharge chamber) are formed. Refrigerant to be compressed is guided to the operation chamber 25 (suction chamber) through thesuction path 14. Compressed refrigerant flows out from the operation chamber 25 (compression-discharge chamber) and from adischarge port 29 formed in theupper frame 6. Theinterior space 28 which is partitioned from an interior of thehermetic container 1 and theoperation chamber 25 is provided in theupper frame 6 on the opposite side from theoperation chamber 25, afirst passage 34 a is formed between thedischarge port 29 and theinterior space 28, and theinterior space 28 and thedischarge port 29 are in communication with each other. Thefirst passage 34 a is provided with afirst check valve 35 a to prevent refrigerant from flowing from theinterior space 28 to theoperation chamber 25. Asecond passage 34 b is formed between theinterior space 28 and the interior of thehermetic container 1, and theinterior space 28 and the interior of thehermetic container 1 are in communication with each other. Thesecond passage 34 b is provided with asecond check valve 35 b to prevent refrigerant from flowing from the interior of thehermetic container 1 to theinterior space 28. - The
vane 9 may be integral with thepiston 8. That is, thepiston 8 and thevane 9 may be composed of a swing piston, or thevane 9 and thepiston 8 may be joined to each other. - The
motor 2 is composed of astator 17 and arotor 18. Thestator 17 is fixed to an inner peripheral surface of thehermetic container 1. Therotor 18 is fixed to theshaft 4 and rotates together with theshaft 4. Thepiston 8 is moved in the cylinder 5 by themotor 2. As themotor 2, it is possible to use a motor whose number of rotations can be changed. Examples of such a motor are an IPMSM (Interior Permanent Magnet Synchronous Motor) and an SPMSM (Surface Permanent Magnet Synchronous Motor). - The
control unit 44 controls theinverter 42 and adjusts the number of rotations of themotor 2, i.e., the number of rotations of therotary compressor 100. As thecontrol unit 44, it is possible to use a DSP (Digital Signal Processor) including an A/D conversion circuit, an input/output circuit, a computation circuit and a storage unit. - The
accumulator 12 is composed of anaccumulation container 12 a and an introduction pipe 12 b. Theaccumulation container 12 a includes an interior space capable of holding liquid refrigerant and gas refrigerant. The introduction pipe 12 b penetrates an upper portion of theaccumulation container 12 a, and opens toward the interior space of theaccumulation container 12 a. The other end of thesuction path 14 and the other end of thecommunication passage 16 are connected to theaccumulator 12. The other end of thesuction path 14 and the other end of thecommunication passage 16 penetrate a bottom of theaccumulation container 12 a, upwardly extend from the bottom of theaccumulation container 12 a, and open in the interior space of theaccumulation container 12 a at given heights. That is, thecommunication passage 16 is connected to thesuction path 14 through the interior space of theaccumulator 12. To reliably prevent liquid refrigerant from directly flowing from the introduction pipe 12 b to thesuction path 14, other member such as a baffle may be provided in theaccumulation container 12 a. Thecommunication passage 16 may be connected directly to thesuction path 14 or the introduction pipe 12 b. - The
control mechanism 30 is provided in thecommunication passage 16 at a location outside of thecompressor body 40. In this embodiment, thecontrol mechanism 30 is composed of an on-offvalve 32. One end of thecommunication passage 16 which is connected to thecompression mechanism 3 is in communication with theinterior space 28. Thecontrol mechanism 30 changes a suction volume of therotary compressor 100. - When the on-off
valve 32 is opened, as a volume of theoperation chamber 25 reduces, thefirst check valve 35 a opens and refrigerant is discharged to outside of theoperation chamber 25. The discharged refrigerant is returned to thesuction path 14 through thecommunication passage 16. Hence, pressure in theoperation chamber 25 does not rise. At this time, since refrigerant is not discharged from theinterior space 28 into thehermetic container 1, therotary compressor 100 is operated in a state where its suction volume is substantially zero. - When the on-off
valve 32 is closed, refrigerant can not return from theoperation chamber 25 to thesuction path 14 through thecommunication passage 16. Hence, if a suction stroke is completed, a compression stroke starts immediately. At this time, since thefirst check valve 35 a prevents refrigerant from reversely flowing from theinterior space 28 to theoperation chamber 25, pressure in theinterior space 28 rises. Further, when pressure in theinterior space 28 rises and becomes higher than pressure in thehermetic container 1, thesecond check valve 35 b opens and refrigerant is discharged into thehermetic container 1. At this time, therotary compressor 100 is operated with a normal suction volume. - The
rotary compressor 100 of this embodiment controls theinverter 42 and adjusts the number of rotations of themotor 2, i.e., the number of rotations of therotary compressor 100. However, when the refrigeration cycle apparatus is operated with ability lower than the rated ability (e.g., 30% or less of the rated ability), the number of rotations of therotary compressor 100 is reduced, this reduction increases the vibration caused by torque variation, and therotary compressor 100 can not be operated with further lower number of rotations (e.g., 20 HZ or less). As a result, therotary compressor 100 is intermittently operation in such a manner that operation and rest are repeated, and efficiency of the refrigeration cycle apparatus is largely deteriorated. - Hence, a so-called “ability variable technique based on switching of a suction volume” is widely known. In this technique, a portion of refrigerant which is compressed by the cylinder 5 is made to bypass to outside of the cylinder 5, thereby changing a suction volume of the
operation chamber 25. As a switching operation of the suction volume, therotary compressor 100 of this embodiment can realize a so-called digital compressor technique in which a case where therotary compressor 100 is operated with substantially zero suction volume by opening the on-offvalve 32 and a case where therotary compressor 100 is operated with a normal suction volume by closing the on-offvalve 32 are combined to control the ability. - In the
rotary compressor 100 of this embodiment, the on-offvalve 32 is opened and closed. For example, by opening the on-offvalve 32 for five seconds and closing the on-offvalve 32 for five seconds, the ability of operation for total ten seconds can be made 50%. As a result, even when the refrigeration cycle apparatus is operated with ability lower than the rated ability, since therotary compressor 100 can continuously be operated, the refrigeration cycle apparatus can be operated efficiently. - When the
rotary compressor 100 of this embodiment is operated with a normal suction volume by closing the on-offvalve 32, since there is no opening facing the cylinder 5, it is possible to prevent the efficiency of the compressor from being deteriorated by dead volume. That is, in thenormal rotary compressor 100, theoperation chamber 25 between the cylinder 5 and thepiston 8 is partitioned by thevane 9 and according to this, the operation chamber 25 (suction chamber) and the operation chamber 25 (compression-discharge chamber) are formed. Refrigerant to be compressed is guided to the operation chamber 25 (suction chamber) through thesuction path 14. Here, if the opening exists in the cylinder 5, refrigerant in theoperation chamber 25 is held in the opening when the opening is in communication with the operation chamber 25 (compression-discharge chamber), but if the opening is brought into communication with the operation chamber 25 (suction chamber), since pressure of refrigerant in the opening is higher than pressure of refrigerant in the operation chamber 25 (suction chamber), refrigerant in the opening reversely flows toward the operation chamber 25 (suction chamber). At this time, the refrigerant in the operation chamber 25 (suction chamber) is reduced and volume efficiency is deteriorated. Since the refrigerant in the opening is not discharged into thehermetic container 1, compression power is lost correspondingly and input of the compressor is increased. This series of loss is called efficiency reduction of a compressor caused by dead volume. - When the
rotary compressor 100 of this embodiment is operated with a normal suction volume by closing the on-offvalve 32, thedischarge port 29 through which compressed working fluid flows out from theoperation chamber 25 is formed in theupper frame 6. According to this configuration, since it is possible to secure the strength of the cylinders, it is possible to avoid a case where galling between parts is caused or parts become abnormally worn due to deformation caused by pressure or temperature at the time of operation. Further, a height of the cylinder 5 is not limited by a configuration of the check valve. As a result, when high density refrigerant such as R410A and carbon dioxide is used as working fluid, since the height of the cylinder 5 can be lowered, it is possible to reduce the increase in a machine loss caused by increase in a load of theshaft 4 or thevane 9 and to reduce a gap formed between an inner periphery of the cylinder 5 and an outer periphery of thepiston 8, it is possible to prevent a leakage loss caused when refrigerant is being compressed from increasing. As a result, it is possible to provide therotary compressor 100 capable of exerting high efficiency. - When the
rotary compressor 100 of this embodiment is operated with a normal suction volume by closing the on-offvalve 32, thefirst check valve 35 a and thesecond check valve 35 b are configured in an end surface direction. According to this configuration, since refrigerant which flows out from thedischarge port 29 can smoothly flow into theinterior space 29 and thehermetic container 1, it is possible to provide arotary compressor 100 capable of suppressing a loss caused when refrigerant is discharged from theoperation chamber 25 and capable of exerting high efficiency. - The
rotary compressor 100 of this embodiment is configured such that when it is operated with the normal suction volume by closing the on-offvalve 32, a cross-sectional area of thesecond passage 34 b becomes greater than that of thefirst passage 34 a. According to this configuration, since thefirst passage 34 a opens at the cylinder 5, if the cross-sectional area of thefirst passage 34 a is increased, efficiency of the compressor is deteriorated by the dead volume. If the cross-sectional area of thefirst passage 34 a is reduced on the other hand, pressure in theoperation chamber 25 rises higher than discharge pressure by resistance of refrigerant which flows out from theoperation chamber 25 through thedischarge port 29, and compression power is increased. Hence, it is necessary that the cross-sectional area of thefirst passage 34 a is determined such that the efficiency of therotary compressor 100 becomes the highest. However, since thesecond passage 34 b is provided between theinterior space 29 and the interior of thehermetic container 1, the efficiency of the compressor is not deteriorated by the dead volume. That is, by suppressing pressure rise in theinterior space 29 by the resistance of refrigerant which flows out through thesecond passage 34 b, performance of therotary compressor 100 is enhanced. As a result, by setting the cross-sectional area of thesecond passage 34 b greater than that of thefirst passage 34 a, it is possible to provide therotary compressor 100 capable of exerting high efficiency. - The
first check valve 35 a and thesecond check valve 35 b can be composed of reed valves which are composed of reed portions 36 a and 36 b andvalve stoppers 37 a and 37 b, respectively. As a check valve of another type, there is a free valve (not shown) composed of a valve body, a guide and a spring. As a check valve of another type, the check valve can be composed of a plunger and a plunger spring (not shown). If the plunger and the plunger spring are used, since the check valve can always be opened, it is possible to reduce a pressure loss generated in the check valve. Here, the free valve is characterized in that a pressure loss when working fluid passes therethrough can be made smaller than that of a reed valve. However, in therotary compressor 100 of this embodiment, if the on-offvalve 32 is closed from its opened state, there is a problem that pressure in theinterior space 29 rises and the valve body collides against the guide and noise is generated until the valve body closes the passage. Hence, it is preferable that the reed valve is used in therotary compressor 100 of this embodiment. - Next, a relation between an ability variable technique carried out by switching the suction volume and the
inverter 42 which drives themotor 2 with an arbitrary number of rotations will be described. - First, a case where the refrigeration cycle apparatus is operated with 70% ability.
- A so-called “ability variable technique based on switching of a suction volume” is used. In this technique, a portion of refrigerant which is compressed by the cylinder 5 is made to bypass to outside of the cylinder 5, thereby changing a suction volume of the
operation chamber 25. In this case, in therotary compressor 100 of this embodiment, the on-offvalve 32 is opened and closed. For example, by opening the on-offvalve 32 for three seconds and closing the on-offvalve 32 for seven seconds, the ability of operation for total ten seconds can be made 70%. - By repeating the opening and closing operations of the on-off
valve 32 and by changing the ratio between the opening time and closing time in the opening and closing operations, it is possible to change the ability of the refrigeration cycle apparatus. That is, when the opening and closing operations of the on-offvalve 32 are repeated, if the ratio of the opening time is increased, the ability of the refrigeration cycle apparatus can be reduced. - When the ability is controlled using the ability variable technique based on switching of the suction volume as described above, it is necessary that the time during which the
rotary compressor 100 is operated with substantially zero suction volume is set to 30% by opening the on-offvalve 32. At this time, since therotary compressor 100 keeps rotating, a machine loss is generated to drive thecompression mechanism 3 even if power for compressing refrigerant becomes zero. - When the
motor 2 is driven by theinverter 42 with an arbitrary number of rotations on the other hand, if themotor 2 is operated with 70% number of rotations (e.g., 42 Hz) of the rated number of rotations (e.g., 60 Hz), the ability can be made 70%.Many motors 2 are designed such that the highest efficiency is exerted with the number of rotations close to the rated number of rotations (e.g., 60 Hz), but if themotor 2 is operated with about 70% number of rotations (e.g., 42 Hz), high efficiency can be maintained. As a result, if aninverter 42 which drives themotor 2 with an arbitrary number of rotations is used, it is possible to operate the refrigeration cycle apparatus efficiently. - Next, a case where the refrigeration cycle apparatus is operated with 50% ability will be described.
- When the so-called “ability variable technique based on switching of a suction volume” is used, the on-off
valve 32 is opened and closed in therotary compressor 100 of this embodiment. For example, by opening the on-offvalve 32 for five seconds and closing the on-offvalve 32 for five seconds, the ability of operation for total ten seconds can be made 50%. - When the
motor 2 is driven by theinverter 42 with an arbitrary number of rotations on the other hand, if themotor 2 is operated with 50% number of rotations (e.g., 30 Hz) of the rated number of rotations (e.g., 60 Hz), the ability can be made 50%. However,many motors 2 are designed such that the highest efficiency is exerted with the number of rotations close to the rated number of rotations (e.g., 60 Hz), if themotor 2 is operated with about 50% number of rotations (e.g., 30 Hz), the efficiency is largely deteriorated. As a result, if the ability variable technique based on the switching of the suction volume is used, it is possible to operate the refrigeration cycle apparatus efficiently. - Hence, concerning a relation between the ability variable technique based on the switching of the suction volume and the
inverter 42 which drives themotor 2 with an arbitrary number of rotations, if aninverter 42 which can operate the refrigeration cycle apparatus efficiently is selected, it is possible to operate the refrigeration cycle apparatus more efficiently. - In this embodiment, the ability variable technique based on the switching of the suction volume and the
inverter 42 which drives themotor 2 with an arbitrary number of rotations are appropriately separately used depending upon situations. The ability variable technique based on the switching of the suction volume is selected when the refrigeration cycle apparatus is operated with 70% ability, theinverter 42 which drives themotor 2 with an arbitrary number of rotations is selected when the refrigeration cycle apparatus is operated with 50% ability, but the invention is not limited to this embodiment. Concerning a question as to which one of the ability variable technique and the inverter should used for controlling the ability of the refrigeration cycle, it is preferable to select one of them which can operate the refrigeration cycle apparatus more efficiently. - As shown in
FIG. 2 , arotary compressor 200 of a second embodiment includes asecond compression mechanism 33 in addition to thecompression mechanism 3 described in the first embodiment. In the following description, “first” is added to the elements of thecompression mechanism 3 described in the first embodiment. For example, the cylinder 5 is described as a first cylinder 5, thepiston 8 is described as afirst piston 8, thevane 9 is described as afirst vane 9, theoperation chamber 25 is described as afirst operation chamber 25, and thecompression mechanism 3 is described as afirst compression mechanism 3. - The
second compression mechanism 33 is composed of asecond cylinder 55, asecond piston 58, asecond vane 59 and asecond spring 60. Thesecond cylinder 55 is disposed concentrically with the first cylinder 5. Asecond piston 58 fitted over a second eccentric portion 4 b of ashaft 4 is disposed in thesecond cylinder 55. Asecond operation chamber 75 is formed between an outer peripheral surface of thesecond piston 58 and an inner peripheral surface of thesecond cylinder 55. A second vane groove (not shown) is formed in thesecond cylinder 55. Asecond vane 59 is accommodated in the second vane groove. A tip end of thesecond vane 59 is in contact with the outer peripheral surface of thesecond piston 58. Asecond spring 60 is disposed in the second vane groove. Thesecond spring 60 pushes thesecond vane 59 toward thesecond piston 58. Asecond operation chamber 75 between thesecond cylinder 55 and thesecond piston 58 is partitioned by thesecond vane 59. According to this, a second operation chamber 75 (second suction chamber) and a second operation chamber 75 (second compression-discharge chamber) are formed. Refrigerant to be compressed is guided to the second operation chamber 75 (second suction chamber) through asecond suction path 15. Asecond discharge port 79 is formed in anupper frame 6. According to this, compressed refrigerant is guided from the second operation chamber 75 (second compression-discharge chamber) into thehermetic container 1 through thesecond discharge port 79. Adischarge valve 35 c is provided in thesecond discharge port 79. According to this, refrigerant does not reversely flow from thehermetic container 1 into thesecond operation chamber 75. - In the
first compression mechanism 3, refrigerant to be compressed is guided to the first operation chamber 25 (suction chamber) through thefirst suction path 14. Compressed refrigerant flows out from afirst discharge port 29 which is formed from the first operation chamber 25 (compression-discharge chamber) to thelower frame 7. Theinterior space 28 which is partitioned from an interior of thehermetic container 1, thefirst operation chamber 25 and thesecond operation chamber 75 is provided in theupper frame 7 on the opposite side from theoperation chamber 25, afirst passage 34 a is formed between thedischarge port 29 and theinterior space 28, and theinterior space 28 and thedischarge port 29 are in communication with each other. Thefirst passage 34 a is provided with afirst check valve 35 a to prevent refrigerant from flowing from theinterior space 28 to thefirst operation chamber 25. Asecond passage 34 b is formed between theinterior space 28 and the interior of thehermetic container 1, and theinterior space 28 and the interior of thehermetic container 1 are in communication with each other. Thesecond passage 34 b is provided with asecond check valve 35 b to prevent refrigerant from flowing from the interior of thehermetic container 1 to theinterior space 28. - It is preferable that the
first operation chamber 25 is located in the vertically downward direction with respect to thesecond operation chamber 75. This is because when the refrigeration cycle apparatus operated with low ability, since only suction refrigerant passes through thefirst operation chamber 25, temperature of the cylinder becomes low. Further, this is because if the low temperature cylinder is located at a low location, it is possible to restrain the suction refrigerant from receiving heat from discharged refrigerant from a standpoint of temperature stratification. - The
lower frame 7 is covered with amuffler 23. Themuffler 23 has a space capable of receiving refrigerant which is compressed by thefirst compression mechanism 3. Aflow path 26 penetrates thelower frame 7, the first cylinder 5, amiddle plate 53, thesecond cylinder 55 and theupper frame 6. According to this configuration, refrigerant moves from the space of themuffler 23 into thehermetic container 1. - A projecting direction of the first
eccentric portion 4 a is deviated from a projecting direction of the second eccentric portion 4 b by 180°. That is, a phase of thefirst piston 8 is deviated from a phase of thesecond piston 58 by a rotation angle of the shaft of 180°. - Refrigerant is supplied to the
first compression mechanism 3 through thefirst suction path 14. Refrigerant is supplied to thesecond compression mechanism 33 through thesecond suction path 15. Refrigerant is compressed by thefirst compression mechanism 3 or thesecond compression mechanism 33 and discharged into thehermetic container 1. Thefirst suction path 14 and thesecond suction path 15 are connected to theaccumulator 12. One of thesuction paths accumulator 12. - As shown in
FIG. 2 , since thecommunication passage 16 is not connected to thesecond compression mechanism 33, a suction volume of thesecond compression mechanism 33 is always constant. Thecommunication passage 16 is connected only to thefirst compression mechanism 3 so that only a suction volume of thefirst compression mechanism 3 can be changed. According to this, production costs of therotary compressor 200 can be suppressed. Of course, thecommunication passage 16 may be connected to thefirst compression mechanism 3 and thesecond compression mechanism 33 so that suction volumes of thefirst compression mechanism 3 and thesecond compression mechanism 33 can be changed. - In this embodiment, the
first compression mechanism 3 is disposed on a side far from themotor 2 and thesecond compression mechanism 33 is disposed on a side close to themotor 2. That is, themotor 2, thesecond compression mechanism 33 and thefirst compression mechanism 3 are arranged in this order along an axial direction of theshaft 4. Since thesecond compression mechanism 33 has the constant suction volume, thesecond compression mechanism 33 requires greater torque than that of thefirst compression mechanism 3 which can be operated with substantially zero suction volume. Therefore, since thesecond compression mechanism 33 is disposed on the side close to themotor 2, a load which is applied to theshaft 4 when thefirst compression mechanism 3 is operated with the substantially zero suction volume is reduced. According to this, it is possible to reduce machine losses of theupper frame 6 and thelower frame 7. If thefirst compression mechanism 3 which can be operated with the substantially zero suction volume is disposed on a lower side, it is possible to reduce a pressure loss which is generated when compressed refrigerant flows into theinterior space 28 of thehermetic container 1 through themuffler 23. However, a positional relation between thefirst compression mechanism 3 and thesecond compression mechanism 33 is not limited to the above-described relation. - In this embodiment, a normal suction volume of the
first compression mechanism 3 and a suction volume of thesecond compression mechanism 33 are the same. Here, a case where thefirst compression mechanism 3 is operated with substantially zero suction volume is defined as a low volume mode, and a case where thefirst compression mechanism 3 is operated with a normal suction volume is defined as a high volume mode. At this time, if a suction volume in the high volume mode of therotary compressor 200 is defined as V, a suction volume in the low volume mode is V/2. - Next, the
inverter 42 which drives themotor 2 with an arbitrary number of rotations, and control procedure of the control mechanism 30 (on-off valve 32) and theinverter 42 performed by thecontrol unit 44 which controls theinverter 42 will be described with reference toFIG. 3A . - In
step 1, the number of rotations of themotor 2 is adjusted in accordance with requested ability. More specifically, the number of rotations of themotor 2 is adjusted so that a necessary flow rate of refrigerant is obtained. Insteps motor 2 is reduced or increased. If it is determined instep 2 that the number of rotations is reduced, the procedure proceeds on to step 3, and it is determined whether the current number of rotations is 30 Hz or less. If the current number of rotations is 30 Hz or less, it is determined instep 4 whether the on-offvalve 32 is closed. If the on-offvalve 32 is closed, processing to open the on-offvalve 32 and processing to increase the number of rotations of themotor 2 to a double value of the current number of rotations are carried out. Although the order of the processing operations in step 5 is not especially limited, it is possible to increase the number of rotations of themotor 2 substantially at the same time when the on-offvalve 32 is opened. - If it is determined in
step 2 that processing to increase the number of rotations is carried out on the other hand, the processing proceeds on to step 7, and it is determined whether the current number of rotations is 70 Hz or more. If the current number of rotations is 70 Hz or more, it is determined instep 8 whether the on-offvalve 32 is opened. If the on-offvalve 32 is opened, processing to close the on-offvalve 32 and processing to reduce the number of rotations of themotor 2 to ½ of the current number of rotations are carried out instep 9. Although the order of the processing operations instep 9 is not especially limited, it is possible to reduce the number of rotations of themotor 2 substantially at the same time when the on-offvalve 32 is closed. - By carry out the control in accordance with the flowchart in
FIG. 3A , a relation between a state of the on-offvalve 32 and the number of rotations of themotor 2 has hysteresis as shown inFIG. 4 . According to such control, it is possible to prevent hunting of thecompression mechanism 3. - According to the
rotary compressor 200 of this embodiment, in a state where the on-offvalve 32 is closed, i.e., in the high volume mode in which refrigerant is prohibited from returning from theoperation chamber 25 to thesuction path 14 through thecommunication passage 16, a suction volume of thecompression mechanism 3 is “V”. When the number of rotations of themotor 2 is reduced from the high rotation side to the first number of rotations (e.g., 30 Hz) or less during operation in the high volume mode, thecontrol unit 44 carries out processing concerning the on-offvalve 32 to reduce the suction volume and processing concerning theinverter 42 to increase the number of rotations of themotor 2. The processing concerning the on-offvalve 32 to reduce the suction volume is processing to open the on-offvalve 32. The processing concerning theinverter 42 to increase the number of rotations of themotor 2 is processing to set the target number of rotations of themotor 2 to a double value of the last number of rotations. - The
control unit 44 controls the on-offvalve 32 and theinverter 42 to compensate for the increase in the suction volume by reducing the number of rotations of themotor 2. A state where the on-offvalve 32 is opened, i.e., in the low volume mode in which refrigerant is prohibited from returning from theoperation chamber 25 to thesuction path 14 through thecommunication passage 16, a suction volume of thecompression mechanism 3 is “V/2”. When the number of rotations of themotor 2 is increased to the second number of rotations (e.g., 70 Hz) or more during operation in the low volume mode, thecontrol unit 44 carries out processing concerning the on-offvalve 32 to increase the suction volume and processing concerning theinverter 42 to reduce the number of rotations of themotor 2. The processing concerning the on-offvalve 32 to increase the suction volume is processing to close the on-offvalve 32. The processing concerning theinverter 42 to reduce the number of rotations of themotor 2 is processing to set the target number of rotations of themotor 2 to ½ of the last number of rotations. - As shown in
FIG. 4 , if the number of rotations of themotor 2 is reduced to 30 Hz in a state where the on-offvalve 32 is closed, the on-offvalve 32 is opened and the number of rotations of themotor 2 is increased to 60 Hz. If the number of rotations of themotor 2 is increased to 70 Hz in a state where the on-offvalve 32 is opened, the on-offvalve 32 is closed and the number of rotations of themotor 2 is reduced to 35 Hz. If the number of rotations when the on-offvalve 32 is opened and the number of rotations of themotor 2 is increased is defined as the third number of rotations and the number of rotations when the on-offvalve 32 is closed and the number of rotations of themotor 2 is reduced is defined as the fourth number of rotations, a relation (first number of rotations)<(fourth number of rotations) and a relation (third number of rotations)<(second number of rotations) are established. For example, if the first number of rotations is set to 30 Hz or less, it is possible to operate therotary compressor 200 with wider ability. A lower limit value of the first number of rotations is not especially limited, but an example of the lower limit value is 20 Hz. - When the
control mechanism 30 is controlled such that thefirst compression mechanism 3 is operated with substantially zero suction volume, theinverter 42 is controlled to compensate for reduction of the suction volume by increasing the number of rotations of themotor 2. According to this, it becomes unnecessary to largely reduce the number of rotations of themotor 2 even when the refrigeration cycle apparatus is operated with ability lower than the rated ability. That is, even when the refrigeration cycle apparatus is operated with low ability, it is possible to drive themotor 2 with the number of rotations capable of exerting high efficiency. Therefore, efficiency of therotary compressor 200 is also enhanced. - More specifically, as shown by solid lines in
FIG. 5 , therotary compressor 200 in this embodiment can exert high efficiency even when therotary compressor 200 is operated with low ability. InFIG. 5 , the rated ability of therotary compressor 200 is defined as “100%”. If the rated ability is a criterion, the efficiency of therotary compressor 200 is lowered as the ability to be exerted is lowered, i.e., as the number of rotations of themotor 2 is reduced. As shown by broken lines, when themotor 2 is driven with the number of rotations which is 50% or less of the rated number of rotations, the efficiency is largely deteriorated. In this embodiment, when relatively low ability is required, themotor 2 is operated in the low volume mode having a suction volume V/2. According to this, it is possible to drive themotor 2 with the number of rotations which is close to the rated number of rotations as close as possible. Therefore, even in a region where necessary ability is 50% or less of the rated ability, it is possible to provide arotary compressor 200 capable of exerting high efficiency. - It is not absolutely necessary to completely 100% compensate for reduction in ability of the
rotary compressor 200 caused by reduction of a suction volume by increasing ability of therotary compressor 200 by increasing the number of rotations of themotor 2. For example, when the on-offvalve 32 is opened and a suction volume is reduced to ½, if the number of rotations of themotor 2 is increased by two times, ability of therotary compressor 200 is not changed by the switching operation between the modes. However, even if ability of therotary compressor 200 is increased or reduced by the switching operation between the modes, there is no problem. - Heights of the first cylinder 5 and the
second cylinder 55 may be made different from each other in accordance with a rate of suction volumes to be changed, and a normal suction volume of thefirst compression mechanism 3 and a suction volume of thesecond compression mechanism 33 may be changed. More specifically, when a suction volume of thefirst compression mechanism 3 is defined as V1 and a suction volume of thesecond compression mechanism 33 is defined as V2, a suction volume VH in the high volume mode is V1+V2, and a suction volume VL in the low volume mode is V2. Usually, it is preferable that a ratio (VL/VH) of the suction volume VL in the low volume mode to the suction volume VH in the high volume mode is in a range of 0.2 to 0.8. - If the heights of the first cylinder 5 and the
second cylinder 55 are made different from each other in accordance with a rate of suction volumes to be changed and the normal suction volume of thefirst compression mechanism 3 and the suction volume of thesecond compression mechanism 33 are changed, more specifically, if the suction volume of thefirst compression mechanism 3 is defined as V1 and the suction volume of thesecond compression mechanism 33 is defined as V2, the suction volume in the high volume mode is V1+V2, and the suction volume in the low volume mode is V2. This situation will be discussed below. At this time, if the high volume mode and the low volume mode are switched, the number of rotations of themotor 2 can be adjusted in accordance with the ratio (VL/VH) of the suction volume VL in the low volume mode to the suction volume VH in the high volume mode. When the high volume mode is switched to the low volume mode, the number of rotations (target number of rotations) of themotor 2 is set to the number of rotations which is obtained by dividing the number of rotations of themotor 2 immediately before the switching operation between the modes by the ratio (VL/VH). Similarly, when the low volume mode is switched to the high volume mode, the number of rotations of themotor 2 is set to the number of rotations which is obtained by multiplying the number of rotations of themotor 2 immediately before the switching operation between the modes by the ratio (VL/VH). According to this, it is possible to smoothly switch between the operation modes of the high volume mode and the low volume mode. - This embodiment does not have ability in which the
control mechanism 30 decompresses refrigerant. Sucked refrigerant is not substantially compressed in the compression-discharge chamber and returned into thefirst suction path 14 through thecommunication passage 16. Therefore, deterioration in efficiency caused by a pressure loss is extremely small. However, the embodiment may have the ability in which thecontrol mechanism 30 decompresses refrigerant only within a range not largely affecting the efficiency of therotary compressor 200. - Next, another control procedure of the on-off
valve 32 and theinverter 42 will be described. - Even when the number of rotations of the
motor 2 is reduced to the first number of rotations (e.g., 30 Hz) in the high volume mode, if a flow rate of refrigerant is excessively large, thecontrol unit 44 may carry out the processing concerning the on-offvalve 32 to reduce the suction volume and the processing concerning theinverter 42 to increase the number of rotations of themotor 2. That is, thecontrol unit 44 determines whether it is necessary to switch between the modes before the number of rotations of themotor 2 is actually reduced to the first number of rotations. Similarly, even when the number of rotations of themotor 2 is increased to the second number of rotations (e.g., 70 Hz) in the low volume mode, if the flow rate of refrigerant is not sufficient, thecontrol unit 44 may carry out the processing concerning the on-offvalve 32 to increase the suction volume and the processing concerning theinverter 42 to reduce the number of rotations of themotor 2. That is, thecontrol unit 44 determines whether it is necessary to switch between the modes before the number of rotations of themotor 2 is actually increased to the second number of rotations. An example of such control will be described with reference toFIG. 3B . - As shown in
FIG. 3B , the necessary number of rotations of themotor 2 is first calculated instep 11. Here, “necessary number of rotations” means the number of rotations for obtaining a necessary flow rate of refrigerant. Next, it is determined instep 12 whether the necessary number of rotations is equal to or less than the first number of rotations (e.g., 30 Hz). If the necessary number of rotations is equal to or less than the first number of rotations, it is determined instep 13 whether the on-offvalve 32 is closed. If the on-offvalve 32 is closed, instep 15, the on-offvalve 32 is opened and the number of rotations of themotor 2 is adjusted to a value capable of obtaining a necessary flow rate of refrigerant. If the on-offvalve 32 is opened, only the number of rotations of themotor 2 is adjusted instep 14. - If the necessary number of rotations is more than the first number of rotations on the other hand, it is determined in
step 16 whether the necessary number of rotations is equal to or more than the second number of rotations (e.g., 70 Hz). If the necessary number of rotations is equal to or more than the second number of rotations, it is determined instep 17 whether the on-offvalve 32 is opened. If the on-offvalve 32 is opened, instep 18, the on-offvalve 32 is closed and the number of rotations of themotor 2 is adjusted to a value capable of obtaining the necessary flow rate of refrigerant. If the on-offvalve 32 closed, only the number of rotations of themotor 2 is adjusted instep 19. - By carrying out the control described with reference to
FIGS. 3A and 3B , therotary compressor 100 can exert high efficiency also when low ability is required (when, is small) as shown by solid lines inFIG. 5 . InFIG. 5 , the rated ability of therotary compressor 100 is defined as “100%”. If the rated ability is defined as a criterion, the efficiency of therotary compressor 100 is lowered as the as ability to be exerted is reduced, i.e., as the number of rotations of themotor 2 is reduced. As shown by the broken lines, when themotor 2 is driven with the number of rotations which is 50% or less of the rated number of rotations, the efficiency is largely lowered. In this embodiment, when relatively low ability is required, the operation is carried out in the low volume mode with the suction volume V/2. According to this, themotor 2 can be driven with the number of rotations which is close to the rated number of rotations as close as possible. Therefore, even in a region where necessary ability is 50% or less of the rated ability, therotary compressor 100 can exert excellent efficiency. - As shown in
FIG. 6 , arotary compressor 300 of a third embodiment includes acontrol mechanism 30 having a structure different from that of therotary compressor 100 of the first embodiment. Other structures are the same as those described in the first embodiment. - As the
control mechanism 30, therotary compressor 300 includes acommunication passage 16, a three-way valve 90 and ahigh pressure path 92. Thecommunication passage 16 is composed of anupstream portion 16 h which brings the three-way valve 90 and aninterior space 28 into communication with each other, and a downstream portion which brings the three-way valve 90 and asuction path 14 into communication with each other. Thehigh pressure path 92 has one end connected to the three-way valve 90 and the other end connected to anoil reservoir 22. Thehigh pressure path 92 is a path for supplying pressure which is equal to that of compressed refrigerant to aninterior space 28. Therotary compressor 300 of this embodiment is a so-called high pressure shell type compressor in which an interior of ahermetic container 1 is filled with compressed refrigerant. Oil having pressure which is substantially equal to that of compressed refrigerant is held in theoil reservoir 22. The three-way valve 90 connects one of thesuction path 14 and thehigh pressure path 92 to theupstream portion 16 h of thecommunication passage 16. By controlling the three-way valve 90, therotary compressor 300 can be operated in any of a high volume mode and a low volume mode. - In the low volume mode, the three-
way valve 90 is controlled such that thesuction path 14 is brought into communication with theupstream portion 16 h of thecommunication passage 16. In this case, as a volume of theoperation chamber 25 is reduced, afirst check valve 35 a opens, and refrigerant is discharged to outside of theoperation chamber 25. The discharged refrigerant returns to thesuction path 14 through thecommunication passage 16. Hence, pressure in theoperation chamber 25 does not rise. At this time, since refrigerant is not discharged from theinterior space 28 into thehermetic container 1, therotary compressor 300 is operated with substantially zero suction volume. - In the high volume mode on the other hand, the three-
way valve 90 is controlled such that thehigh pressure path 92 is brought into communication with theupstream portion 16 h of thecommunication passage 16. In this case, since refrigerant does not return from theoperation chamber 25 to thesuction path 14 through thecommunication passage 16, pressure of oil in theoil reservoir 22 is introduced into theinterior space 28. Hence, if a suction stroke of refrigerant is completed, a compression stroke of refrigerant is immediately started. At this time, compressed refrigerant is discharged into theinterior space 28 through afirst passage 34 a. When pressure in theinterior space 28 exceeds pressure in thehermetic container 1, asecond check valve 35 b opens and refrigerant is discharged into thehermetic container 1. At this time, therotary compressor 300 is operated with a normal suction volume. - In this embodiment, it is preferable that a portion between the three-
way valve 90 and thehigh pressure path 92 is composed of a capillary tube (not shown) or the like having a relatively small cross-sectional area as compared with thecommunication passage 16. Compressed refrigerant is discharged into theinterior space 28 through thefirst passage 34 a, but if refrigerant-passage resistance of thehigh pressure path 92 is large, thesecond check valve 35 b smoothly opens, and refrigerant in theinterior space 28 is discharged into thehermetic container 1. - In this embodiment, the
high pressure path 92 has one end connected to (opened toward) theoil reservoir 22. To achieve a purpose of supplying high pressure to theinterior space 28, the one end of thehigh pressure path 92 may be connected to any portion of the interior of thehermetic container 1. When therotary compressor 300 is used in the refrigeration cycle apparatus, thehigh pressure path 92 may be connected to a high pressure portion (e.g., a portion between therotary compressor 300 and a radiator) of the refrigerant circuit. However, in the embodiment, if the interior space is closed, a sealing effect by oil can be obtained. This is preferable to prevent efficiency from being deteriorated by leakage of refrigerant. - Although the three-
way valve 90 is used as thecontrol mechanism 30 in this embodiment, a four-way valve may be used. - More specifically, three ends of the four-way valve are connected to the
high pressure path 92, theupstream portion 16 h of thecommunication passage 16 which is in communication with theinterior space 28, and thecommunication passage 16 which is in communication with thesuction path 14, and remaining one end of the four-way valve is always closed. According to this configuration also, the same effect as that of the embodiment can be obtained. - As shown in
FIG. 7 , arefrigeration cycle apparatus 500 can be configured using therotary compressor 100. Therefrigeration cycle apparatus 500 includes therotary compressor 100, aradiator 502, anexpansion mechanism 504 and anevaporator 506. These devices are connected to one another in this order through refrigerant pipes to form a refrigerant circuit. Theradiator 502 is composed of an air-refrigerant heat exchanger for example, and cools refrigerant which is compressed by therotary compressor 100. Theexpansion mechanism 504 is composed of an expansion valve, and expands refrigerant which is cooled by theradiator 502. Theevaporator 506 is composed of an air-refrigerant heat exchanger for example, and heats refrigerant which is expanded by theexpansion mechanism 504. Therotary compressors rotary compressor 100 of the first embodiment. - Some of the embodiments described in this specification can be combined together within a range not departing from the subject matter of the invention. For example, even if the on-off
valve 30 described in the second embodiment is combined with the three-way valve 90 described in the third embodiment, the effect described in the second embodiment can be obtained. - The present invention is effective for a compressor of a refrigeration cycle apparatus which can be utilized for a water heater, a hydronic heater and an air conditioner. Especially, the invention is effective for a compressor of the air conditioner which requires wide ability.
Claims (11)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP2011126974 | 2011-06-07 | ||
JP2011-126974 | 2011-06-07 | ||
PCT/JP2012/003699 WO2012169181A1 (en) | 2011-06-07 | 2012-06-06 | Rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140099218A1 true US20140099218A1 (en) | 2014-04-10 |
Family
ID=47295766
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/124,494 Abandoned US20140099218A1 (en) | 2011-06-07 | 2012-06-06 | Rotary compressor |
Country Status (4)
Country | Link |
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US (1) | US20140099218A1 (en) |
JP (1) | JP6057181B2 (en) |
CN (1) | CN103620224B (en) |
WO (1) | WO2012169181A1 (en) |
Cited By (7)
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CN105041649A (en) * | 2015-07-09 | 2015-11-11 | 广东美芝制冷设备有限公司 | Compressor and air conditioning system with same |
CN106662090A (en) * | 2014-09-30 | 2017-05-10 | 松下电器产业株式会社 | Hermetic compressor and refrigeration device |
US20170292739A1 (en) * | 2014-10-16 | 2017-10-12 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
US20180017057A1 (en) * | 2016-07-14 | 2018-01-18 | Fujitsu General Limited | Rotary compressor |
US10309700B2 (en) | 2016-02-26 | 2019-06-04 | Lg Electronics Inc. | High pressure compressor and refrigerating machine having a high pressure compressor |
US10465682B2 (en) * | 2015-08-24 | 2019-11-05 | Guangdong Meizhi Compressor Co., Ltd. | Rotary compressor and refrigeration cycle device having same |
US10731647B2 (en) * | 2016-02-26 | 2020-08-04 | Lg Electronics Inc. | High pressure compressor and refrigerating machine having a high pressure compressor |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2015135214A (en) * | 2014-01-17 | 2015-07-27 | 株式会社東芝 | Air conditioner |
CN107842486B (en) * | 2017-11-24 | 2024-01-26 | 安徽美芝精密制造有限公司 | Compressor and air conditioning system with same |
CN107989768A (en) * | 2017-11-24 | 2018-05-04 | 安徽美芝精密制造有限公司 | Compressor and refrigerating plant |
CN111287970A (en) * | 2018-12-10 | 2020-06-16 | 广东美芝精密制造有限公司 | Compressor and refrigeration equipment |
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US10731647B2 (en) * | 2016-02-26 | 2020-08-04 | Lg Electronics Inc. | High pressure compressor and refrigerating machine having a high pressure compressor |
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Also Published As
Publication number | Publication date |
---|---|
CN103620224B (en) | 2016-01-20 |
JP6057181B2 (en) | 2017-01-11 |
CN103620224A (en) | 2014-03-05 |
WO2012169181A1 (en) | 2012-12-13 |
JPWO2012169181A1 (en) | 2015-02-23 |
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