WO2005026499A1 - ロータリ式膨張機及び流体機械 - Google Patents
ロータリ式膨張機及び流体機械 Download PDFInfo
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- WO2005026499A1 WO2005026499A1 PCT/JP2004/012836 JP2004012836W WO2005026499A1 WO 2005026499 A1 WO2005026499 A1 WO 2005026499A1 JP 2004012836 W JP2004012836 W JP 2004012836W WO 2005026499 A1 WO2005026499 A1 WO 2005026499A1
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- WIPO (PCT)
- Prior art keywords
- rotary
- pressure chamber
- fluid
- expander
- rotary mechanism
- Prior art date
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Classifications
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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
- F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/32—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01C13/04—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby for driving pumps or compressors
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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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
- F04C18/34—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
-
- 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
Definitions
- the present invention relates to an expander that generates power by expansion of a high-pressure fluid, and to a fluid machine including the expander.
- a so-called rotary type fluid machine has been known, and is widely used as a compressor for compressing a refrigerant in a refrigeration apparatus.
- an expander as an expansion mechanism is provided in a refrigerant circuit to recover power from a refrigerant that is a supercritical high-pressure fluid.
- the rotary fluid machine described above can also be used as such an expander for recovering power.
- high-pressure fluid is introduced into a rotary fluid machine as an expander, and power is obtained by expansion of the high-pressure fluid.
- the power recovered by the expander in this way is used to drive the compressor.
- the high-pressure fluid is intermittently introduced into the expansion chamber.
- the flow of the high-pressure fluid to the expansion chamber is interrupted during the process of increasing the volume of the expansion chamber.
- the flow of the high-pressure fluid toward the expansion chamber is interrupted when the flow rate of the high-pressure fluid is relatively high.
- a liquid high-pressure fluid in a supercritical state to a rotary expander Since the high-pressure fluid is incompressible, a water hammer phenomenon occurs, which causes problems such as excessive vibration and noise, and in some cases, damage to piping and the like.
- the present invention has been made in view of power, and an object thereof is to provide a rotary expander that obtains power by expansion of a high-pressure fluid, and a fluid machine including the rotary expander.
- the first invention is a cylinder (71, 81) having both ends closed, and a piston (75, 85) for forming a fluid chamber (72, 82) in each of the cylinders (71, 81). And a blade (76, 86) for partitioning the fluid chamber (72, 82) into a high-pressure side high-pressure chamber (73, 83) and a low-pressure side low-pressure chamber (74, 84), respectively.
- a plurality of rotary mechanisms (70, 80) and one eccentric part (41, 42) that engages with the piston (75, 85) is formed in the same number as the rotary mechanism (70, 80). It is intended for a rotary expander having a shaft (40).
- the plurality of rotary mechanism units (70, 80) are connected in series in order from one having a different displacement volume and a smaller displacement volume, and are connected to each other in the plurality of rotary mechanism units (70, 80). With the two connected, the fluid flows from the low-pressure chamber (74) of the rotary mechanism (70) on the front stage to the high-pressure chamber (83) of the rotary mechanism (80) on the rear stage.
- the second invention is a cylinder (71, 81) having both ends closed, and a piston (75, 85) for forming a fluid chamber (72, 82) in each of the cylinders (71, 81). And a blade (76, 86) for partitioning the fluid chamber (72, 82) into a high-pressure side high-pressure chamber (73, 83) and a low-pressure side low-pressure chamber (74, 84), respectively.
- a plurality of rotary mechanisms (70, 80) and one eccentric part (41, 42) that engages with the piston (75, 85) is formed in the same number as the rotary mechanism (70, 80). It is intended for a rotary expander having a shaft (40).
- the plurality of rotary mechanism units (70, 80) are connected in series in order from one having a different displacement volume and a smaller displacement volume, and are connected to each other in the plurality of rotary mechanism units (70, 80).
- the low-pressure chamber (74) of the rotary mechanism (70) on the front stage and the high-pressure chamber (83) of the rotary mechanism (80) on the rear stage communicate with each other to form one expansion chamber (66). ).
- the plurality of rotary mechanisms (70, 80) The timings at which the blades (76, 86) are most retracted to the outer peripheral side of the cylinders (71, 81) are synchronized with each other.
- each eccentric portion (
- each eccentric portion (
- the cylinder (71, 81) of each rotary mechanism (70, 80) has an intermediate plate (63) interposed therebetween.
- Each of the intermediate plates (63) has a low-pressure chamber (74) and a rear-stage side of the rotary mechanism (70) on the front stage of the two adjacent rotary mechanisms (70, 80).
- a communication passage (64) for communicating with the high-pressure chamber (83) of the rotary mechanism (80) is formed so as to penetrate the intermediate plate (63) in the thickness direction, while the cylinders (71) , 81) are arranged in a posture in which the length of the communication path (64) is the shortest.
- the cylinder (71, 81) of each rotary mechanism (70, 80) includes an intermediate plate (63) between the cylinders (71, 81).
- Each of the intermediate plates (63) is stacked in a state of being sandwiched between the low-pressure chamber (74) of the rotary mechanism (70) on the front stage and the rear stage of the rotary mechanism (70) of the two adjacent rotary mechanisms (70, 80).
- a communication passage (64) for communicating with the high pressure chamber (83) of the rotary mechanism (80) on the side is formed so as to penetrate the intermediate plate (63) in the thickness direction, while the communication passage (64) is formed. ),
- the eccentric directions of the eccentric portions (41, 42) on the rotating shaft (40) are different from each other by a predetermined angle so that the length becomes the shortest.
- the two rotary mechanisms (70, 80) of the plurality of rotary mechanisms (70, 80) are connected to each other at the preceding rotary mechanism (
- the low-pressure chamber (74) of the 70) and the high-pressure chamber (83) of the downstream rotary mechanism (80) are connected via a communication passage (64).
- An intermediate chamber (65) having a predetermined volume is provided for reducing pressure fluctuation in the passage (64).
- a ninth invention is directed to any one of the first to eighth forces, wherein the blade (
- the blade in any one of the first to eighth aspects, the blade (
- 76, 86 are formed integrally with the pistons (75, 85) so as to protrude from the side surfaces of the pistons (75, 85), and are supported by the cylinders (71, 81) so as to be able to advance and retreat and to be rotatable. Is what is done.
- the fluid introduced into the high-pressure chamber (73) of the rotary mechanism (70) having the smallest displacement is a critical force. It is carbon dioxide above pressure.
- a twelfth invention provides a rotary expander (60) according to the first invention, and a compressor (50) engaged with a rotary shaft (40) of the rotary expander (60).
- a fluid machine that includes a casing (31) in which the rotary expander (60) and the compressor (50) are housed, and in which the fluid compressed by the compressor (50) is discharged into the casing (31). It is intended for.
- the plurality of rotary mechanisms (70, 80) provided in the rotary expander (60) are arranged at positions farther from the compressor (50) as the displacement becomes larger. is there.
- a thirteenth invention provides a rotary expander (60) according to the second invention, and a compressor (50) engaged with a rotation shaft (40) of the rotary expander (60).
- a fluid machine which comprises a casing (31) in which the rotary expander (60) and the compressor (50) are housed, and in which the fluid compressed by the compressor (50) is discharged into the casing (31) It is intended for.
- the plurality of rotary mechanisms (70, 80) included in the rotary expander (60) are arranged at positions farther from the compressor (50) as the displacement is larger.
- the plurality of rotary mechanisms (70, 80) are configured such that each of the blades (76, 86) extends outwardly of the cylinder (71, 81). The timing of the most retired state is synchronized with each other.
- a fifteenth invention is directed to the fluid machine according to the twelfth or thirteenth invention, wherein the rotary expander (60) includes the rotary expander (60) from the fluid in the casing (31).
- a heat insulating member (100) for inhibiting heat transfer to the flowing fluid is provided.
- the rotary expander (60) is provided with a plurality of rotary mechanism parts (70, 80) having different displacement volumes. These multiple rotary mechanisms ( 70, 80) are connected in series in ascending order of displacement. In other words, the outflow side of the rotary mechanism section (70) on the front side having a small displacement is connected to the inflow side of the rotary mechanism section (80) on the rear side having a large displacement.
- the high-pressure fluid is first introduced into the rotary mechanism (70) having the smallest displacement. Specifically, the high-pressure fluid is introduced into the high-pressure side of the fluid chamber (72) in the rotary mechanism (70), that is, into the high-pressure chamber (73). The high-pressure fluid continues to flow until the volume of the fluid chamber (72) is maximized. In other words, the high-pressure fluid continues to flow into the high-pressure chamber (73) from the state in which the blade (77) is most retracted to the outer peripheral side of the cylinder (71) until the rotation shaft (40) makes one rotation.
- the rotation angle of the rotation shaft (40) in a state where the blade (77) is most retracted to the outer peripheral side of the cylinder (71) is 0 °
- the rotation angle is 0 ° until the force reaches 180 °.
- the rate of increase in the volume of the high-pressure chamber (73) gradually increases, and until the rotation angle reaches 180 ° or 360 °, the rate of increase in the volume of the high-pressure chamber (73) gradually decreases.
- the flow rate of the fluid flowing into the high-pressure chamber (73) gradually increases until the rotation angle of the rotating shaft (40) reaches 0 ° and 180 °, and the rotation angle changes from 180 ° to 360 °. Until it gradually slows down. Therefore, when the flow of the fluid directed to the high-pressure chamber (73) is interrupted, the flow velocity of the fluid is almost zero.
- the fluid chamber (72) filled with the high-pressure fluid becomes a low-pressure chamber (74) on the low-pressure side, and the high pressure of the rear-side rotary mechanism (80) having a large displacement is increased. Communicates with room (83).
- the fluid in the low-pressure chamber (74) expands while flowing into the high-pressure chamber (83) of the rotary mechanism (80) on the subsequent stage.
- the expansion chamber (66) composed of the low-pressure chamber (74) of the front rotary mechanism (70) and the high-pressure chamber (83) of the rear rotary mechanism (80).
- the fluid expands inside the.
- the fluid repeats such expansion sequentially, and is finally sent out from the rotary mechanism (80) having the largest displacement.
- the rotation shaft (40) of the rotary expander (60) is driven by the expansion of the fluid. That is, the high-pressure fluid introduced into the rotary expander (60) is converted into the internal energy S and the rotational power of the rotating shaft (40).
- the timing at which the blades (76, 86) retreat most in the rotary mechanism (70, 80) is synchronized with each other.
- Low pressure in the rotary mechanism (70) on the front stage At the point in time when the volume of the chamber (74) becomes maximum, the volume of the high-pressure chamber (83) becomes minimum in the rotary mechanism (80) on the subsequent stage.
- the volume of the low-pressure chamber (74) starts to decrease at the rotary mechanism (70) on the front stage
- the volume of the high-pressure chamber (83) starts to increase at the rotary mechanism (80) on the rear stage.
- the volume of the low-pressure chamber (74) is minimized in the rotary mechanism (70) on the upstream side
- the volume of the high-pressure chamber (83) is maximized in the rotary mechanism (80) on the downstream side.
- the eccentric portions (41, 42) of the rotating shaft (40) are formed so as to be eccentric in directions different from each other. For this reason, the force that the rotating shaft (40) receives from the fluid in the high-pressure chamber (73,83) of each rotary mechanism (70,80) via the piston (75,85) is different from each other in the directions in which they act. Different.
- the eccentric directions of the eccentric portions (41, 42) on the rotating shaft (40) are shifted at a constant angular interval.
- the eccentric directions are 180 ° apart, and in the case of three, the respective eccentric directions are 120 °. Interval.
- the force applied to the rotating shaft (40) from the fluid in the high-pressure chamber (73, 83) of each rotary mechanism (70, 80) has a substantially constant angular interval in the respective action directions.
- the communication path (64) is formed in the intermediate plate (63), and the communication path (64) is provided in the low-pressure chamber (74) of the rotary mechanism section (70) on the upstream side. ) And the high pressure chamber (83) of the rotary mechanism (80) on the subsequent stage.
- the low pressure chamber (74) is formed on the right side of the blade (77) in the rotary mechanism section (70) on the front stage
- the left side of the blade (86) is formed in the rotary mechanism section (80) on the rear stage.
- a high-pressure chamber (83) is formed in the chamber.
- the intermediate chamber (65) is provided in the middle of the communication path (64).
- the intermediate chamber (65) is formed to have a volume that can reduce pressure fluctuations in the communication passage (64).
- the fluid that has flowed out of the low-pressure chamber (74) of the rotary mechanism (70) on the upstream side passes through the communication path (64) and the intermediate chamber (65), and the fluid of the rotary mechanism (80) on the downstream side.
- the blade (76, 86) is formed separately from the biston (75, 85).
- each rotary mechanism (70, 80) is configured as a so-called rolling piston type.
- each rotary mechanism (70, 80) the blade (76, 86) is formed integrally with the piston (75, 85).
- the blades (76, 86) are movable back and forth with respect to the cylinders (71, 81) while being supported by the cylinders (71, 81).
- the pistons (75, 85) integral with the blades (76, 86) perform oscillating motion in the cylinders (71, 81) while engaging with the eccentric portions (41, 42) of the rotating shaft (40). That is, in the present invention, each rotary mechanism (70, 80) is configured as a so-called swinging piston.
- carbon dioxide (CO 2) is sent into the high-pressure chamber (73) of the plurality of rotary mechanism sections (70, 80) having the smallest displacement.
- This high pressure chamber 73) of the plurality of rotary mechanism sections (70, 80) having the smallest displacement.
- the pressure of carbon dioxide introduced into (73) is equal to or higher than the critical pressure of carbon dioxide. Then, the carbon dioxide flowing into the high-pressure chamber (73) expands while sequentially passing through a plurality of rotary mechanism sections (70, 80) connected in series.
- the rotary expander (60) and the compressor (50) of the first aspect are housed in the casing (31).
- the rotary expander (60) and the compressor (50) of the second aspect are housed in a casing (31).
- the compressor (50) is engaged with the rotary shaft (40) of the rotary expander (60).
- the compressor (50) is driven by the power obtained by the rotary expander (60), and sucks and compresses a fluid.
- the fluid compressed by the compressor (50) is discharged into a space inside the casing (31), and after passing through this space, is sent out of the casing (31).
- the compressor (50) is not required to be driven only by the rotary expander (60) .
- the compressor (50) is driven by both the electric motor and the rotary expander (60). It may be,
- the rotary expander (60) according to the twelfth and thirteenth inventions, a plurality of rotary machines are provided.
- the structural parts (70, 80) are arranged at positions farther from the compressor (50) as the displacement volume is larger.
- the temperature of the fluid passing through the rotary expander (60) decreases as the fluid expands and the pressure decreases.
- the fluid flowing into the rotary expander (60) sequentially passes from the rotary mechanism (70) having a small displacement to the rotary mechanism (80) having a large displacement.
- the temperature of the fluid passing therethrough decreases as the rotary mechanism (80) has a larger displacement.
- the rotary mechanism (80) having a lower temperature of the fluid passing therethrough is provided at a position farther from the compressor (50) for discharging the fluid having a high temperature and a high pressure.
- the rotary expander (60) is provided with the heat insulating member (100).
- the fluid that passes through the rotary expander (60) has a lower temperature than the fluid that is compressed by the compressor (50) and discharged into the casing (31). It is heated to some extent by heat transfer from the discharged fluid.
- the heat insulating member (100) inhibits heat transfer from the fluid discharged from the compressor (50) to the fluid passing through the rotary expander (60), and heats the fluid passing through the rotary expander (60). Reduce.
- the supplied high-pressure fluid is first introduced into the high-pressure chamber (73) of the rotary mechanism (70) having the smallest displacement. Then, the flow velocity of the fluid toward the high-pressure chamber (73) gradually increases and decreases according to the volume change rate of the high-pressure chamber (73).
- the flow of the fluid to be introduced is interrupted in a state where the flow velocity is relatively high, and a steep pressure fluctuation occurs accordingly.
- the flow velocity of the fluid flowing toward the high-pressure chamber (73) changes slowly, so that a steep pressure fluctuation of the introduced fluid can be prevented. Therefore, according to the present invention, the pulsation of the fluid introduced into the rotary expander (60) can be greatly reduced, and the vibration and noise accompanying the pulsation can be greatly reduced, thereby improving the reliability of the rotary expander (60).
- the timing at which the volume of the low-pressure chamber (74) begins to decrease in the front-stage rotary mechanism (70) and the time when the rear-stage rotary mechanism (80) starts The time when the volume of the high pressure chamber (83) starts to increase from the minimum value is synchronized. Therefore, the expansion force S of the high-pressure fluid supplied to the rotary expander (60) is smoothly performed, and power can be efficiently recovered from the high-pressure fluid.
- the eccentric portions (41, 42) of the rotating shaft (40) are eccentric in directions different from each other. For this reason, the forces acting on the rotating shaft (40) from the fluid in the high-pressure chambers (73, 83) of the respective rotary mechanisms (70, 80) have different directions of action, and cancel each other out to some extent. Fit. Therefore, according to these inventions, when the eccentric directions of the eccentric portions (41, 42) are the same and the rotating shaft (40) receives a force in the same direction from the fluid in the high-pressure chamber (73, 83). The radial load acting on the rotating shaft (40) can be reduced, and the friction loss between the rotating shaft (40) and the bearing can be reduced to improve the efficiency of the rotary expander (60). .
- the eccentric directions of the eccentric portions (41, 42) on the rotating shaft (40) are at equal angular intervals. For this reason, the forces that the rotating shaft (40) receives from the fluid in the high-pressure chambers (73, 83) of the rotary mechanism sections (70, 80) are at equal angular intervals in their respective working directions, and almost completely cancel each other. Fit. Therefore, according to the present invention, the frictional loss between the rotating shaft (40) and the bearing can be greatly reduced, and the power S can be greatly improved to greatly improve the efficiency of the rotary expander (60).
- the length of the communication path (64) is shortened as much as possible by shifting the arrangement angle of each cylinder (71, 81).
- the pressure loss of the fluid from the low pressure chamber (74) of the rotary mechanism (70) on the front stage to the high pressure chamber (83) of the rotary mechanism (80) on the rear stage can be reduced, and the rotary expansion
- the power recovered in the machine (60) can be increased.
- the intermediate chamber (65) having a relatively large capacity is provided in the communication path (64). For this reason, pressure fluctuation of the fluid flowing through the communication passage (64) from the low-pressure chamber (74) of the rotary mechanism section (70) on the front side to the high-pressure chamber (83) of the rotary mechanism section (80) on the downstream side is reduced. can do.
- carbon dioxide in a supercritical state is introduced into the rotary expander (60). That is, the fluid to be introduced is substantially incompressible and adversely affected by the pulsation of the fluid.
- the configuration of the present invention is applied to a rotary type expander that has been harmful. Therefore, according to the present invention, in a rotary expander in which the harm caused by the pulsation at the time of introducing a fluid is large, the occurrence of such pulsation is surely suppressed, and the reliability is reliably improved. That can be S.
- the rotary mechanism (80) having a larger displacement capacity is smaller. It is located at a position away from the compressor (50). In other words, the temperature of the passing fluid is lower, and the rotary mechanism (80) is located farther from the compressor (50), and the rotary mechanism where the temperature of the passing fluid is as high as possible is closer to the compressor (50). (70) is located. Therefore, according to the present invention, the rotary expander (60) can be obtained from the discharge fluid of the compressor (50) as compared with the case where the rotary mechanism (80) having a large displacement is arranged closer to the compressor (50). The amount of heat transferred to the fluid can be reduced.
- heat transfer to the fluid of the rotary expander (60) is inhibited by the heat insulating member (100). Therefore, according to the present invention, the amount of heat transferred from the discharge fluid of the compressor (50) to the fluid of the rotary expander (60) can be further reduced.
- FIG. 1 is a piping diagram of an air conditioner according to Embodiment 1.
- FIG. 2 is a schematic sectional view of a compression / expansion unit according to Embodiment 1.
- FIG. 3 is an enlarged view of a main part of an expansion mechanism according to the first embodiment.
- FIG. 4 is a cross-sectional view of a main part showing a state of each rotary mechanism section at every 90 ° rotation angle of a shaft in the expansion mechanism section of Embodiment 1.
- FIG. 5 is a relationship diagram showing a relationship between a rotation angle of a shaft, a volume of an expansion chamber and the like, and an internal pressure of the expansion chamber in the expansion mechanism of the first embodiment.
- FIG. 6 is a relationship diagram showing a relationship between a rotation angle of a shaft and an inflow velocity of a fluid for the expansion mechanism of Embodiment 1 and a conventional rotary expander.
- FIG. 7 is an enlarged view of a main part of an expansion mechanism in Modification 1 of Embodiment 1.
- FIG. 8 is a cross-sectional view of a main part of an expansion mechanism according to a second modification of the first embodiment.
- FIG. 9 Each rotary mechanism section at every 90 ° rotation angle of the shaft in the expansion mechanism section of Embodiment 2.
- FIG. 4 is a cross-sectional view of a main part showing the state of FIG.
- FIG. 10 is a cross-sectional view of a main part showing a state of each rotary mechanism at every 90 ° rotation angle of a shaft in an expansion mechanism of Embodiment 3.
- FIG. 11 is a schematic sectional view of a compression / expansion unit according to Embodiment 4.
- FIG. 12 is a schematic sectional view of a compression / expansion unit according to a fifth embodiment.
- FIG. 13 is a schematic configuration diagram of a compression / expansion unit according to Embodiment 5 and a comparative example.
- FIG. 14 is a schematic sectional view of a compression / expansion unit according to a modification of the fifth embodiment.
- Embodiment 1 of the present invention will be described.
- the air conditioner (10) of the present embodiment includes the rotary expander according to the present invention.
- the air conditioner (10) is a so-called separate type, and includes an outdoor unit (11) and an indoor unit (13).
- the outdoor unit (11) includes an outdoor fan (12), an outdoor heat exchanger (23), a first four-way switching valve (21), a second four-way switching valve (22), and a compression / expansion unit (30). Is stored.
- the indoor unit (13) contains an indoor fan (14) and an indoor heat exchanger (24).
- the outdoor unit (11) is installed outdoors, and the indoor unit (13) is installed indoors.
- the outdoor unit (11) and the indoor unit (13) are connected by a pair of connecting pipes (15, 16). The details of the compression / expansion unit (30) will be described later.
- the air conditioner (10) is provided with a refrigerant circuit (20).
- the refrigerant circuit (20) is a closed circuit to which the compression / expansion unit (30), the indoor heat exchanger (24), and the like are connected.
- the refrigerant circuit (20) is filled with carbon dioxide (CO 2) as a refrigerant.
- Each of the outdoor heat exchanger (23) and the indoor heat exchanger (24) is a cross-fin type fin-and-tube heat exchanger.
- the refrigerant circulating in the refrigerant circuit (20) exchanges heat with outdoor air.
- the indoor heat exchanger (24) the refrigerant circulating in the refrigerant circuit (20) exchanges heat with indoor air.
- the first four-way switching valve (21) includes four ports.
- This first four-way switching valve (21 ) Has a first port connected to the discharge port (33) of the compression / expansion unit (30), a second port connected to one end of the indoor heat exchanger (24) via the communication pipe (15), and a third port connected to the third port.
- Port of the outdoor heat exchanger (21 ) Has a first port connected to the discharge port (33) of the compression / expansion unit (30), a second port connected to one end of the indoor heat exchanger (24) via the communication pipe (15), and a third port connected to the third port.
- Port of the outdoor heat exchanger (21 ) has a first port connected to the discharge port (33) of the compression / expansion unit (30), a second port connected to one end of the indoor heat exchanger (24) via the communication pipe (15), and a third port connected to the third port.
- a fourth port is connected to the suction port (32) of the compression / expansion unit (30), respectively.
- the first four-way switching valve (21) is in a state where the first port and the second port are in communication and the third port and the fourth port are in communication (the state shown by the solid line in FIG. 1). And a state where the first port and the third port communicate with each other and the second port and the fourth port communicate with each other (a state shown by a broken line in FIG. 1).
- the second four-way switching valve (22) includes four ports.
- the second four-way switching valve (22) has a first port connected to the outlet port (35) of the compression / expansion unit (30), a second port connected to the other end of the outdoor heat exchanger (23), The third port is connected to the indoor heat exchanger (
- a fourth port is connected to the inflow port (34) of the compression / expansion unit (30), respectively.
- the second four-way switching valve (22) is in a state where the first port and the second port are in communication and the third port and the fourth port are in communication (the state shown by the solid line in FIG. 1). And a state where the first port and the third port communicate with each other and the second port and the fourth port communicate with each other (a state shown by a broken line in FIG. 1).
- the compression / expansion unit (30) includes a casing (31), which is a horizontally long and cylindrical closed container. Inside the casing (31), a compression mechanism (50), an electric motor (45), and an expansion mechanism (60) are arranged in this order from left to right in FIG. Note that the terms “right” and “left” used in the following description refer to those in the drawings referred to.
- the electric motor (45) is arranged at the center in the longitudinal direction of the casing (31).
- This electric motor (45) is composed of a stator (46) and a rotor (47).
- the stator (46) is fixed to the casing (31).
- the rotor (47) is arranged inside the stator (46).
- the main shaft portion (44) of the shaft (40) penetrates through the rotor (47) coaxially with the rotor (47).
- the shaft (40) forms a rotating shaft.
- one small-diameter eccentric part (43) is formed on the left end side, and two large-diameter eccentric parts (41, 42) are formed on the right end side. It is made.
- the small-diameter eccentric portion (43) is formed to have a smaller diameter than the main shaft portion (44), and is eccentric by a predetermined amount from the axis of the main shaft portion (44).
- each large-diameter eccentric portion (41, 42) is formed to have a larger diameter than the main shaft portion (44).
- the right one constitutes the first large-diameter eccentric portion (41)
- the left one constitutes the second large-diameter eccentric portion (42). are doing.
- the first large-diameter eccentric portion (41) and the second large-diameter eccentric portion (42) are both eccentric in the same direction.
- the outer diameter of the second large-diameter eccentric part (42) is larger than the outer diameter of the first large-diameter eccentric part (41).
- the amount of eccentricity of the main shaft portion (44) with respect to the axis is larger in the second large-diameter eccentric portion (42) than in the first large-diameter eccentric portion (41).
- the compression mechanism (50) constitutes a so-called scroll compressor.
- the compressor mechanism (50) includes a fixed scroll (51), a movable scroll (54), and a frame (57).
- the compression mechanism (50) is provided with a suction port (32) and a discharge port (33).
- a fixed wall wrap (53) having a spiral wall shape is projected from the end plate (52).
- the end plate (52) of the fixed scroll (51) is fixed to the casing (31).
- a movable end wrap (56) having a spiral wall shape is projected from a plate-shaped end plate (55).
- the fixed scroll (51) and the movable scroll (54) are arranged so as to face each other.
- the compression wrap (59) is defined by the engagement of the fixed wrap (53) and the movable wrap (56).
- One end of the suction port (32) is connected to the outer periphery of the fixed wrap (53) and the movable wrap (56).
- the discharge port (33) is connected to the center of the end plate (52) of the fixed scroll (51), and one end of the discharge port (33) opens to the compression chamber (59).
- the end plate (55) of the orbiting scroll (54) has a protruding portion formed at the center of the right side surface, and the small-diameter eccentric portion (43) of the shaft (40) is inserted into the protruding portion. ing.
- the movable scroll (54) is supported by a frame (57) via an Oldham ring (58).
- the Oldham ring (58) is for restricting rotation of the orbiting scroll (54).
- the orbiting scroll (54) revolves at a predetermined turning radius without rotating.
- the expansion mechanism (60) is a so-called oscillating piston type fluid machine, and constitutes a rotary expander of the present invention.
- the expansion mechanism (60) is provided with two pairs of cylinders (81, 82) and pistons (75, 85).
- the expansion mechanism (60) includes a front head (61), an intermediate plate (63), and a rear head (62).
- the front head is arranged in order from left to right in FIG.
- the inner diameter of the second cylinder (81) is larger than the inner diameter of the first cylinder (71).
- the shaft (40) passes through the stacked front head (61), second cylinder (81), intermediate plate (63), first cylinder (71), and rear head (62). ing.
- the shaft (40) has its first large-diameter eccentric part (41) located in the first cylinder (71) and its second large-diameter eccentric part (42) located in the second cylinder (81). It is located in.
- a first piston (75) is provided in the first cylinder (71), and a second piston (85) is provided in the second cylinder (81). Let's do it.
- Each of the first and second pistons (75, 85) is formed in an annular or cylindrical shape.
- the outer diameter of the first piston (75) and the outer diameter of the second piston (85) are equal to each other.
- the inner diameter of the first piston (75) is approximately equal to the outer diameter of the first large-diameter eccentric portion (41), and the inner diameter of the second piston (85) is approximately equal to the outer diameter of the second large-diameter eccentric portion (42).
- a first large-diameter eccentric portion (41) penetrates the first piston (75), and a second large-diameter eccentric portion (42) penetrates the second piston (85).
- the first piston (75) has an outer peripheral surface on the inner peripheral surface of the first cylinder (71), one end surface S on the rear head ( 62 ), and the other end surface on the intermediate plate (63). Is in sliding contact.
- a first fluid chamber (72) is formed between the inner peripheral surface of the first cylinder (71) and the outer peripheral surface of the first piston (75).
- the second piston (85) has its outer peripheral surface on the inner peripheral surface of the second cylinder (81), one end surface on the front head (61), and the other end surface on the intermediate plate (63). They are in sliding contact.
- a second fluid chamber (82) is formed between the first fluid chamber and the second fluid chamber.
- Each of the first and second pistons (75, 85) is provided with a single blade (76, 86).
- the blade (76, 86) is formed in a plate shape extending in the radial direction of the piston (75, 85), and protrudes outward from the outer peripheral surface of the piston (75, 85).
- Each of the cylinders (71, 81) is provided with a pair of bushes (77, 87).
- Each bush (77, 87) is a small piece formed so that the inner surface is a flat surface and the outer surface is an arc surface.
- the pair of bushes (77,87) are installed with the blade (76,86) sandwiched therebetween.
- Each bush (77, 87) slides on its inner surface with the blade (76, 86) and its outer surface slides on the cylinder (81, 82).
- the blade (76, 86) integral with the piston (75, 85) is supported by the cylinder (71, 81) via the bush (77, 87) and rotates with respect to the cylinder (71, 81). It is self-contained and free to advance and retreat.
- the first fluid chamber (72) in the first cylinder (71) is partitioned by a first blade (76) integral with the first piston (75), and the first blade (76) in FIG.
- the left side is a first high pressure chamber (73) on the high pressure side
- the right side is a first low pressure chamber (74) on the low pressure side.
- the second fluid chamber (82) in the second cylinder (81) is partitioned by a second blade (86) integral with the second piston (85), and the left side of the second blade (86) in FIG.
- the high pressure side is the second high pressure chamber (83), and the right side is the low pressure side second low pressure chamber (84).
- the first cylinder (71) and the second cylinder (81) are arranged in such a posture that the positions of the bushes (77, 87) in the respective circumferential directions coincide.
- the arrangement angle of the second cylinder (81) with respect to the first cylinder (71) is 0 °.
- the first large-diameter eccentric portion (41) and the second large-diameter eccentric portion (42) are eccentric in the same direction with respect to the axis of the main shaft portion (44). Therefore, at the same time that the first blade (76) is most retracted to the outside of the first cylinder (71), the second blade (86) is most retracted to the outside of the second cylinder (81). .
- the first cylinder (71) is provided with an inflow port (34).
- the inflow port (34) is opened at a position on the inner peripheral surface of the first cylinder (71) slightly to the left of the bush (77) in FIG. 3 and FIG.
- the inflow port (34) can communicate with the first high-pressure chamber (73) (ie, the high-pressure side of the first fluid chamber (72)).
- an outflow port (35) is formed in the second cylinder (81).
- the outflow port (35) is located on the inner peripheral surface of the second cylinder (81), as shown in FIGS. At the slightly right side of the bush (87).
- the outflow port (35) can communicate with the second low pressure chamber (84) (ie, the low pressure side of the second fluid chamber (82)).
- the intermediate plate (63) is provided with a communication path (64).
- the communication path (64) is formed to penetrate the intermediate plate (63).
- On the surface of the intermediate plate (63) on the side of the first cylinder (71), one end of the communication path (64) is open at a location on the right side of the first blade (76).
- On the surface of the intermediate plate (63) on the side of the second cylinder (81), the other end of the communication path (64) is open at a position on the left side of the second blade (86).
- the communication path (64) extends obliquely with respect to the thickness direction of the intermediate plate (63), and is connected to the first low-pressure chamber (74) (that is, the first fluid chamber (72)). It can communicate with both the low pressure side) and the second high pressure chamber (83) (ie, the high pressure side of the second fluid chamber (82)).
- the first cylinder (71), the bush (77) provided therein, the first piston (75), One blade (76) constitutes a first rotary mechanism (70).
- the second cylinder (81), the bush (87) provided therein, the second piston (85), and the second blade (86) constitute a second rotary mechanism (80).
- the timing that retreats to the outside of () is synchronized. That is, the process of reducing the volume of the first low-pressure chamber (74) in the first rotary mechanism (70) and the capacity of the second high-pressure chamber (83) in the second rotary mechanism (80). The process of increasing the product is synchronized (see Fig. 4).
- the first low-pressure chamber (74) of the first rotary mechanism (70) and the second high-pressure chamber (83) of the second rotary mechanism (80) communicate with the communication path (64). Are in communication with one another. Then, one closed space is formed by the first low-pressure chamber (74), the communication path (64), and the second high-pressure chamber (83), and this closed space constitutes an expansion chamber (66). This will be described with reference to FIG.
- the rotation angle of the shaft (40) when the first blade (76) is most retracted to the outer peripheral side of the first cylinder (71) is 0 °.
- the description is made on the assumption that the maximum volume of the first fluid chamber (72) is 3 ml (milliliter) and the maximum volume of the second fluid chamber (82) is 10 ml.
- the capacity of the first low-pressure chamber (74) reaches the maximum value of 3 ml, and the capacity of the second high-pressure chamber (83) increases.
- the volume is Oml which is the minimum value.
- the volume of the first low-pressure chamber (74) gradually decreases as the shaft (40) rotates, and reaches the minimum Oml when the rotation angle reaches 360 °, as shown by the dashed line in the figure. .
- the volume of the second low-pressure chamber (84) gradually increases as the shaft (40) rotates, as indicated by the two-dot chain line in the same figure, and reaches the maximum value when the rotation angle reaches 360 °. It becomes 10 ml. If the volume of the communication passage (64) is neglected, the volume of the expansion chamber (66) at a certain rotation angle is equal to the volume of the first low-pressure chamber (74) and the volume of the second high-pressure chamber (83) at that rotation angle.
- the volume of the expansion chamber (66) reaches the minimum value of 3 ml when the rotation angle of the shaft (40) is 0 ° as shown by the solid line in the figure, and gradually increases as the shaft (40) rotates.
- the maximum value becomes 10 ml.
- the first four-way switching valve (21) and the second four-way switching valve (22) are switched to the state shown by the broken line in FIG. In this state, when the electric motor (45) of the compression / expansion unit (30) is energized, the refrigerant circulates in the refrigerant circuit (20) to perform a vapor compression refrigeration cycle.
- the refrigerant compressed by the compression mechanism (50) is discharged from the compression / expansion unit (30) through the discharge port (33). In this state, the pressure of the refrigerant is higher than its critical pressure.
- the discharged refrigerant is sent to the outdoor heat exchanger (23) through the first four-way switching valve (21). In the outdoor heat exchanger (23), the inflow refrigerant dissipates heat to outdoor air.
- the refrigerant radiated in the outdoor heat exchanger (23) passes through the second four-way switching valve (22), passes through the inflow port (34), and expands in the expansion mechanism section (30) of the compression / expansion unit (30). 60).
- the expansion mechanism (60) the high-pressure refrigerant expands, and its internal energy is converted into rotational power of the shaft (40).
- the expanded low-pressure refrigerant flows out of the compression / expansion unit (30) through the outflow port (35), passes through the second four-way switching valve (22), and is sent to the indoor heat exchanger (24).
- the indoor heat exchanger (24) the inflow refrigerant absorbs heat from the indoor air and evaporates, thereby cooling the indoor air.
- the low-pressure gas refrigerant discharged from the indoor heat exchanger (24) passes through the first four-way switching valve (21), passes through the suction port (32), and the compression mechanism (50) of the compression / expansion unit (30). Inhaled to.
- the compression mechanism (50) compresses and discharges the sucked refrigerant.
- the first four-way switching valve (21) and the second four-way switching valve (22) are switched to the state shown by the solid line in FIG. In this state, when the electric motor (45) of the compression / expansion unit (30) is energized, the refrigerant circulates in the refrigerant circuit (20) to perform a vapor compression refrigeration cycle.
- the refrigerant compressed by the compression mechanism (50) is discharged from the compression / expansion unit (30) through the discharge port (33). In this state, the pressure of the refrigerant is higher than its critical pressure.
- the discharged refrigerant passes through the first four-way switching valve (21) and is sent to the indoor heat exchanger (24). In the indoor heat exchanger (24), the inflow refrigerant dissipates heat to the indoor air, and the indoor air is heated.
- the refrigerant radiated by the indoor heat exchanger (24) passes through the second four-way switching valve (22), passes through the inflow port (34), and expands in the expansion mechanism section (30) of the compression / expansion unit (30). 60).
- the expansion mechanism (60) the high-pressure refrigerant expands, and its internal energy is converted into rotational power of the shaft (40).
- the expanded low-pressure refrigerant flows out of the compression / expansion unit (30) through the outflow port (35), passes through the second four-way switching valve (22), and is sent to the outdoor heat exchanger (23).
- the inflow refrigerant absorbs heat from outdoor air and evaporates.
- the low-pressure gas refrigerant flowing out of the outdoor heat exchanger (23) passes through the first four-way switching valve (21), passes through the suction port (32), and compresses (50) of the compression / expansion unit (30). Inhaled to The compression mechanism (50) compresses the sucked refrigerant and discharges it.
- the flow rate of the high-pressure refrigerant flowing into the first high-pressure chamber (73) is, as shown in FIG. 6 (A), until the rotation angle of the shaft (40) reaches 0 ° and 180 °. It gradually increases and gradually decreases from 180 ° to 360 ° of its rotational angular force. Then, when the rotation angle of the shaft (40) becomes 360 ° and the flow rate change rate of the high-pressure refrigerant becomes zero, the flow of the high-pressure refrigerant into the first high-pressure chamber (73) ends.
- both the first low-pressure chamber (74) and the second high-pressure chamber (83) are in communication with the communication passage (64), and the first low-pressure chamber
- the refrigerant starts flowing from the chamber (74) into the second high-pressure chamber (83).
- the rotational angular force of the shaft (40) gradually increases to 0 °, 180 °, and 270 °
- the volume of the first low-pressure chamber (74) gradually decreases, and at the same time, the volume of the second high-pressure chamber (83) gradually increases.
- the volume of the expansion chamber (66) gradually increases. This increase in the volume of the expansion chamber (66) continues until just before the rotational angular force of the shaft (40) reaches 3 ⁇ 460 °.
- the refrigerant in the expansion chamber (66) expands while the volume of the expansion chamber (66) increases, and the shaft (40) is driven to rotate by the expansion of the refrigerant.
- the refrigerant in the first low-pressure chamber (74) flows into the second high-pressure chamber (83) while expanding through the communication path (64).
- the refrigerant pressure in the expansion chamber (66) gradually decreases as the rotation angle of the shaft (40) increases, as shown by the broken line in Fig. 5.
- the supercritical refrigerant filling the first low-pressure chamber (74) has a rotation angle of the shaft (40) of about 55.
- the pressure drops rapidly until the pressure reaches, and a saturated liquid state is established.
- the refrigerant in the expansion chamber (66) gradually drops in pressure while a part of the refrigerant evaporates.
- the second low-pressure chamber (84) starts to communicate with the outflow port (35) when the rotation angle of the shaft (40) is 0 °. That is, the refrigerant starts flowing out of the second low-pressure chamber (84) to the outflow port (35). Then, the rotation angle of the shaft (40) is 90 °, 180 °, The low-pressure refrigerant after the expansion of the second low-pressure chamber (84) flows out until the rotation angle reaches 360 °.
- the high-pressure refrigerant flows into the middle of the process of increasing the volume of the fluid chamber in one cylinder, and after the flow of the high-pressure refrigerant is shut off, the refrigerant is expanded in the fluid chamber.
- the flow rate of the high-pressure refrigerant flowing into the high-pressure chamber gradually increases as the shaft rotates, as shown in Fig. 6 (B), but when the rotation angle of the shaft reaches a predetermined value, It had dropped sharply to zero.
- a steep pressure fluctuation occurred on the inflow side of the rotary expander, resulting in excessive noise and vibration.
- the figure shows the case where two cylinders are provided, and the introduction of the refrigerant into the first cylinder indicated by the solid line and the introduction of the refrigerant into the second cylinder indicated by the broken line are performed alternately. .
- the first high-pressure chamber is connected to the inflow port (34).
- the flow velocity of the refrigerant flowing into (73) changes gradually as the shaft (40) rotates (see Fig. 6 (A)). Then, even if the pipe is connected to the inflow port (34) of the expansion mechanism (60), the flow velocity of the refrigerant inside the pipe gradually changes. For this reason, it is possible to prevent a sudden pressure change of the refrigerant from occurring due to the operation of the expansion mechanism (60). Therefore, according to the present embodiment, the pulsation of the refrigerant introduced into the expansion mechanism (60) can be greatly reduced, and the resulting vibration and noise are significantly reduced, thereby improving the reliability of the expansion mechanism (60). Can be improved.
- the expansion mechanism (60) may be configured as follows.
- the second cylinder (81) is moved relative to the first cylinder (71) so that the openings of the communication passages (64) on both sides of the intermediate plate (63) overlap each other. May be shifted by a predetermined angle.
- the eccentric direction of the first large-diameter eccentric portion (41) and the eccentric direction of the second large-diameter eccentric portion (42) are different from each other.
- the angle between the eccentric direction of the first large-diameter eccentric portion (41) and the eccentric direction of the second large-diameter eccentric portion (42) is determined by the arrangement of the second cylinder (81) with respect to the first cylinder (71). The angle is the same as the angle. Therefore, also in this modified example, the first blade (76) is most outwardly located outside the first cylinder (71). The retreat timing is synchronized with the retraction timing of the second blade (86) to the outside of the second cylinder (81).
- the opening position of the communication passage (64) on each surface of the intermediate plate (63) on the first cylinder (71) side and the second cylinder (81) side is determined by the cylinder (71 , 81) in the circumferential direction. Therefore, the communication path (64) of the present modified example is formed so as to extend substantially in the thickness direction of the intermediate plate (63), and the length of the communication path (64) is minimized. Therefore, according to this modification, the pressure loss of the refrigerant from the first low-pressure chamber (74) of the first rotary mechanism (70) to the second high-pressure chamber (83) of the second rotary mechanism (80) is reduced. And the power that can be recovered by the expansion mechanism (60) can be increased.
- an intermediate chamber (65) may be provided in the middle of the communication path (64).
- the intermediate chamber (65) is formed to have a relatively large volume.
- the volume of the intermediate chamber (65) is larger than the volume of the communication passage (64) itself.
- Embodiment 2 of the present invention will be described. This embodiment is obtained by changing the configuration of the expansion mechanism (60) in the first embodiment.
- the points of the expansion mechanism (60) of the present embodiment that are different from those of the first embodiment will be described.
- the second cylinder (81) is arranged in a posture opposite to the first cylinder (71). That is, the arrangement angle of the second cylinder (81) with respect to the first cylinder (71) is 180 °.
- the eccentric direction of the first large-diameter eccentric portion (41) and the eccentric direction of the second large-diameter eccentric portion (42) differ by 180 °. That is, in the shaft (40), the eccentric direction of the first large-diameter eccentric portion (41) and the eccentric direction of the second large-diameter eccentric portion (42) are equiangularly spaced.
- the first blade (76) moves outward to the outside of the first cylinder (71). Is synchronized with the timing at which the second blade (86) retreats most to the outside of the second cylinder (81).
- the first low-pressure chamber (74) of the first rotary mechanism (70) and the second high-pressure chamber (83) of the second rotary mechanism (80) also communicate with the communication path (64). Communication is possible via
- the internal pressure of the high-pressure chamber (73, 83) is higher than the internal pressure of the low-pressure chamber (74, 84). Acts on each large-diameter eccentric portion (41, 42) of the shaft (40).
- the force acting on the second large-diameter eccentric portion (42) due to the internal pressure difference between the second low-pressure chamber (84) are opposite to each other.
- Embodiment 3 of the present invention will be described.
- This embodiment is obtained by changing the configuration of the expansion mechanism (60) in the first embodiment.
- the expansion mechanism (60) of the first embodiment is configured by a oscillating piston type fluid machine
- the expansion mechanism (60) of the present embodiment is a rolling piston type. It is composed of a fluid machine.
- the differences of the expansion mechanism (60) of the present embodiment from the first embodiment will be described.
- each rotary mechanism (70, 80) of the present embodiment the blade (76, 86) is formed separately from the piston (75, 85). That is, each piston (75, 85) of the present embodiment is formed in a simple annular or cylindrical shape. Further, each of the cylinders (71, 81) of the present embodiment is formed with one blade groove (78, 88).
- each rotary mechanism (70, 80) the blade (76, 86) is provided in a blade groove (78, 88) of the cylinder (71, 81) so as to be able to advance and retreat.
- the blades (76, 86) are urged by a panel (not shown), and the tip (the lower end in FIG. 10) is pressed against the outer peripheral surface of the piston (75, 85).
- the blades (76, 86) move along the blade grooves (78, 88) as shown in FIG. Up It moves down and its tip is kept in contact with the piston (75,85).
- the blade (76, 86) is provided in a blade groove (78, 88) of the cylinder (71, 81) so as to be able to advance and retreat.
- the blades (76, 86) are urged by a panel (not shown), and the tip (the lower end in FIG. 10) is pressed against the outer peripheral surface of the piston (75, 85).
- the blades (76, 86) move
- the fluid chambers (72, 82) become high pressure chambers (73, 83) on the high pressure side and low pressure chambers on the low pressure side, respectively. (74,84).
- Embodiment 4 of the present invention will be described. This embodiment is obtained by changing the configuration of the expansion mechanism (60) in the first embodiment. Here, the differences of the expansion mechanism (60) of the present embodiment from the first embodiment will be described.
- the first rotary mechanism section (70) is arranged closer to the electric motor (45), and is located farther from the electric motor (45).
- the second rotary mechanism ( 70) is arranged closer to the electric motor (45), and is located farther from the electric motor (45).
- the rear head (62) is in a stacked state.
- the left end face of the first cylinder (71) is closed by the front head (61)
- the right end face is closed by the intermediate plate (63).
- the second cylinder (81) has its left end face closed by an intermediate plate (63) and its right end face closed by a rear head (62).
- the left one constitutes the first large-diameter eccentric portion (41), and the right Constitutes the second large-diameter eccentric part (42).
- the first piston (75) is engaged with the first large-diameter eccentric portion (41) located in the first cylinder (71), and the second large-diameter eccentric portion located in the second cylinder (81).
- the second piston (85) is engaged with (42).
- Embodiment 5 of the present invention will be described.
- a difference of the compression / expansion unit (30) of the present embodiment from the fourth embodiment will be described.
- the compression / expansion unit (30) which is a fluid machine, is configured to be a vertical type.
- the casing (31) is a vertically-long cylindrical closed container.
- a compression mechanism (50), an electric motor (45), and an expansion mechanism (60) are arranged in order from bottom to top.
- the shaft (40) is installed in a posture extending vertically along the longitudinal direction of the casing (31).
- the compression mechanism (50) constitutes an oscillating piston type rotary compressor.
- the compressor structure (50) includes two cylinders (91, 92) and two pistons (97).
- the rear head (95), the first cylinder (91), the intermediate plate (96), the second cylinder (92), and the front head (94) are stacked.
- first and second cylinders (91, 92) Inside the first and second cylinders (91, 92), one cylindrical piston (97) is arranged. Then, a compression chamber (93) is formed between the outer peripheral surface of the piston (97, 97) and the inner peripheral surface of the cylinder (91, 92). Although not shown, a flat blade is protruded from the side surface of the piston (97), and the blade is supported by the cylinders (91, 92) via a swinging bush.
- Each of the first and second cylinders (91, 92) is provided with one suction port (32).
- Each suction port (32) penetrates the cylinder (91, 92) in the radial direction, and the terminal end is opened on the inner peripheral surface of the cylinder (91, 92).
- Each of the front head (94) and the rear head (95) has one discharge port.
- the discharge port of the front head (94) makes the compression chamber (93) in the second cylinder (92) communicate with the internal space of the casing (31).
- the discharge port of the rear head (95) connects the compression chamber (93) in the first cylinder (91) with the internal space of the casing (31).
- Each discharge port is provided with a discharge valve including a reed valve at the end thereof, and is opened and closed by the discharge valve. In FIG. 12, the illustration of the discharge port and the discharge valve is omitted.
- Two lower eccentric portions (98, 99) are formed in the lower portion of the shaft (40). These two lower eccentric portions (98, 99) are formed to have a larger diameter than the main shaft portion (44), the lower one being the first lower eccentric portion (98), and the upper one being the first one.
- Each of the lower eccentric portions (99) is formed.
- the first lower eccentric (98) is located in the first cylinder (91) and engages with the piston (97), and the second lower eccentric (99) is located in the second cylinder (92). To engage the piston (97).
- the first lower eccentric portion (98) and the second lower eccentric portion (99) have eccentric directions of the main shaft portion (44) with respect to the axis.
- the discharge pipe (36) is attached to the casing (31). This discharge pipe (36) is It is arranged between the motive (45) and the expansion mechanism (60), and communicates with the internal space of the casing (31). The gas refrigerant discharged from the compression mechanism (50) into the internal space of the casing (31) is discharged through the discharge pipe (36) into the compression / expansion unit (30).
- the configuration of the expansion mechanism (60) is the same as that of the fourth embodiment. However, as the compression-expansion unit (30) has become vertical, the expansion mechanism (60) has a front head (61), a first cylinder (71), an intermediate The plate (63), the second cylinder (81), and the rear head (62) are in a stacked state. That is, in the expansion mechanism (60), the first rotary mechanism (70) having a small displacement is arranged on the lower side near the compression mechanism (50), and the second rotary mechanism (80) having a large displacement is arranged. ) Is disposed above the compression mechanism (50).
- the high-temperature and high-pressure gas refrigerant compressed by the compression mechanism (50) flows into the discharge pipe (36) through the internal space of the casing (31). Therefore, the refrigerant passing through the expansion mechanism (60) is heated to some extent by the refrigerant discharged from the compression mechanism (50).
- the refrigerant passing through the expansion mechanism (60) is heated, the enthalpy of the low-pressure refrigerant delivered from the expansion mechanism (60) increases, and the amount of heat absorbed by the low-pressure refrigerant decreases accordingly.
- the compression mechanism (50) When heat is taken from the refrigerant compressed by the compression mechanism (50), the enthalpy of the high-pressure refrigerant discharged from the discharge pipe (36) decreases, and the heat radiation amount of the high-pressure refrigerant decreases accordingly. Then, in the air conditioner (10) of the present embodiment, the cooling capacity is reduced due to the decrease in the heat absorption of the low-pressure refrigerant, and the heating capacity is reduced due to the decrease in the heat radiation of the high-pressure refrigerant.
- the second opening one-way mechanism (80) through which the lower-temperature refrigerant flows is disposed above the compression mechanism (50). .
- the refrigerant passing through the expansion mechanism (60) and the compression mechanism (50) are different from the case where the second opening one-way mechanism (80) is arranged close to and below the compression mechanism (50). ), It is possible to reduce the amount of heat exchange between the refrigerants discharged from).
- FIG. 13 (A) when the second rotary mechanism (80) is disposed below the compression mechanism (50), the compressed 90 ° C high-pressure refrigerant is supplied to the second rotary mechanism. Heat exchange is performed with the low-pressure refrigerant at 0 ° C sent from the section (80), and the temperature difference between the refrigerants exchanging heat reaches about 90 ° C.
- FIG. 13 (B) when the first rotary mechanism (70) is disposed on the lower side near the compression mechanism (50), the compressed 90 ° C. high-pressure refrigerant is supplied to the first rotary mechanism. Heat exchange is performed with the high-pressure refrigerant at 30 ° C introduced into (70), and the temperature difference between the refrigerants exchanging heat with each other is suppressed to about 60 ° C.
- the second rotary mechanism (80) having a large displacement is arranged at a position far from the compression mechanism (50), the discharge of the compression mechanism (50) can be improved.
- the amount of heat input from the refrigerant to the refrigerant in the expansion mechanism (60) can be reduced. According to the present embodiment, it is possible to suppress a decrease in the cooling capacity and the heating capacity due to the heat transfer from the refrigerant discharged from the compression mechanism (50) to the refrigerant in the expansion mechanism (60).
- a heat insulating member (100) may be provided in the expansion mechanism (60).
- the heat insulating member (100) is formed in a substantially disk shape, and is provided so as to be in contact with the lower surface of the front head (61) in the expansion mechanism (60).
- the heat insulating member (100) is made of a material having relatively low thermal conductivity such as FRP.
- the expansion mechanism (60) may be configured as follows.
- the number of the rotary mechanism units provided with two rotary mechanism units (70, 80) in the expansion mechanism unit (60) is not limited to two, but is three or more. You may.
- the rotary mechanisms are configured such that their displacement volumes are different from each other, and are connected in ascending order of displacement volume.
- the inner diameter of each cylinder (71, 81) and the amount of eccentricity of each large-diameter eccentric portion (41, 42) are made different from each other to make each rotary mechanism (70, 80) eccentric.
- the force S that makes the displacement different, and instead, the displacement of each rotary mechanism (70,80) by making the height of each cylinder (71,81) and each piston (75,85) different. May be different. Further, the inner diameter of each cylinder (71, 81), the amount of eccentricity of each large-diameter eccentric part (41, 42), and the height of each cylinder (71, 81) and each piston (75, 85) are all determined. By making them different, the displacement volume of each rotary mechanism (70, 80) can be made different.
- the first piston (75) and the second piston (85) have a force S formed so that their outer diameters are equal to each other. Even if the diameter is different, it does not matter. In other words, as long as the displacement of the second rotary mechanism (80) is larger than the displacement of the first rotary mechanism (70), the outside of the first piston (75) and the second piston (85) can be reduced. One outer diameter may be larger than the other as long as the diameters do not need to be equal to each other.
- the present invention is useful for a rotary expander that drives a rotary shaft by expansion of a fluid, and a fluid machine including the rotary expander.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04772785A EP1669542A4 (en) | 2003-09-08 | 2004-09-03 | ROTARY RELIEF DEVICE AND FLUID TRANSFER MECHANISM |
US10/570,878 US7896627B2 (en) | 2003-09-08 | 2004-09-03 | Rotary type expander and fluid machinery |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-315179 | 2003-09-08 | ||
JP2003315179 | 2003-09-08 | ||
JP2004056741A JP3674625B2 (ja) | 2003-09-08 | 2004-03-01 | ロータリ式膨張機及び流体機械 |
JP2004-056741 | 2004-03-01 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005026499A1 true WO2005026499A1 (ja) | 2005-03-24 |
Family
ID=34315623
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/012836 WO2005026499A1 (ja) | 2003-09-08 | 2004-09-03 | ロータリ式膨張機及び流体機械 |
Country Status (4)
Country | Link |
---|---|
US (1) | US7896627B2 (ja) |
EP (1) | EP1669542A4 (ja) |
JP (1) | JP3674625B2 (ja) |
WO (1) | WO2005026499A1 (ja) |
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Also Published As
Publication number | Publication date |
---|---|
EP1669542A1 (en) | 2006-06-14 |
JP3674625B2 (ja) | 2005-07-20 |
US20070053782A1 (en) | 2007-03-08 |
JP2005106046A (ja) | 2005-04-21 |
EP1669542A4 (en) | 2011-06-29 |
US7896627B2 (en) | 2011-03-01 |
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