CN102395759A - Fluid machine and refrigeration cycle apparatus - Google Patents
Fluid machine and refrigeration cycle apparatus Download PDFInfo
- Publication number
- CN102395759A CN102395759A CN2011800017666A CN201180001766A CN102395759A CN 102395759 A CN102395759 A CN 102395759A CN 2011800017666 A CN2011800017666 A CN 2011800017666A CN 201180001766 A CN201180001766 A CN 201180001766A CN 102395759 A CN102395759 A CN 102395759A
- Authority
- CN
- China
- Prior art keywords
- compressor
- decompressor
- inlet hole
- working fluid
- axle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 239
- 238000005057 refrigeration Methods 0.000 title description 3
- 238000005192 partition Methods 0.000 claims description 44
- 239000006200 vaporizer Substances 0.000 claims description 27
- 230000007246 mechanism Effects 0.000 claims description 24
- 230000002093 peripheral effect Effects 0.000 claims description 23
- 238000007599 discharging Methods 0.000 claims description 16
- 230000006835 compression Effects 0.000 claims description 10
- 238000007906 compression Methods 0.000 claims description 10
- 238000001704 evaporation Methods 0.000 claims description 3
- 230000008020 evaporation Effects 0.000 claims description 3
- 230000005855 radiation Effects 0.000 claims description 3
- 230000008878 coupling Effects 0.000 abstract 1
- 238000010168 coupling process Methods 0.000 abstract 1
- 238000005859 coupling reaction Methods 0.000 abstract 1
- 238000011144 upstream manufacturing Methods 0.000 description 21
- 230000009471 action Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000000314 lubricant Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 150000005827 chlorofluoro hydrocarbons Chemical class 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 239000012467 final product Substances 0.000 description 1
- 235000015927 pasta Nutrition 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000008093 supporting effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
- F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
-
- 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
- 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
-
- 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
- F04C23/001—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 of similar working principle
-
- 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
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- 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
- F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
- F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/14—Power generation using energy from the expansion of the refrigerant
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Disclosed is a fluid machine (8A) provided with an expander (4) having an expander suction hole (4a) and an expander discharge hole (4b), a compressor (6) having a compressor suction hole (6a) and a compressor discharge hole (6b), and a shaft (81) for coupling the expander (4) to the compressor (6). The expander suction hole (4a) and the compressor suction hole (6a) are opened or closed in accordance with the rotation of the shaft (81). The expander suction hole (4a) is open when the compressor suction hole (6a) is closed. The compressor suction hole (6a) is open and does not communicate with the compressor discharge hole (6b) when the expander suction hole (4a) is closed.
Description
Technical field
The present invention relates in hot-warer supplying machine or air conditioner etc. the fluid machinery that uses and used the refrigerating circulatory device of this fluid machinery.
Background technique
At present, known have decompressor and compressor to link through axle, utilizes the power that reclaims from expanded working fluid decompressor to come the such fluid machinery of Driven Compressor.The fluid machinery 100 of that kind shown in Figure 12 for example, is disclosed in patent documentation 1.
Shown in figure 12, in fluid machinery 100, decompressor 110 links through axle 101 with compressor 120.Decompressor 110 and compressor 120 are rotary type, and axle 101 has first eccentric part 102 of decompressor 110 usefulness, second eccentric part 103 of compressor 120 usefulness.
Shown in figure 13, decompressor 110 has the decompressor piston 112 chimeric with first eccentric part 102 of axle 101, accommodates the decompressor clutch release slave cylinder 111 of decompressor piston 112.And, between the outer circumferential face of the inner peripheral surface of decompressor clutch release slave cylinder 111 and decompressor piston 112, be formed with the decompressor working room 113 of crescent shape.Decompressor working room 113 is inflated machine partition member 114 and is separated into the suction side and discharges side.Decompressor partition member 114 forms as one with decompressor piston 112, on decompressor clutch release slave cylinder 111, can be provided with rotatably 114 supportings of decompressor partition member are reciprocal columned piston shoes (shoe) 117 freely.That is, decompressor piston 112 is a fulcrum and changing swing in the distance of this fulcrum with the center of piston shoes 117.
On decompressor clutch release slave cylinder 111, be provided with to decompressor working room 113 import the inlet hole 110a of working fluids and from the decompressor working room 113 discharge working fluids tap hole 110b.Inlet hole 110a was communicated with decompressor working room 113 via the connectivity slot 116 that is formed on the intercommunicating pore 115 on the piston shoes 117 and be formed on the decompressor partition member 113 in the moment of regulation.That is, piston shoes 117 and decompressor partition member 113 constitute the suction control mechanism that opens and closes inlet hole 110a along with the rotation of axle 101.(being communicated with decompressor working room 113) that inlet hole 110a is opened is positioned at from decompressor piston 112 constantly and makes top dead center that decompressor partition member 114 retreats most till about 140 ° of rotation.
Shown in figure 14, compressor 120 has: compressor piston 122, and it is made up of roller bearing, and is chimeric with second eccentric part 103 of axle 101; Compressor operating cylinder 121, it accommodates compressor piston 122.And, between the outer circumferential face of the inner peripheral surface of compressor operating cylinder 121 and compressor piston 122, be formed with the compressor operating chamber 123 of crescent shape.Compressor operating chamber 123 is compressed machine partition member 124 and is separated into the suction side and discharges side.Compressor partition member 124 is pressed on the compressor piston 122 by spring.
On compressor operating cylinder 121, be provided with the inlet hole 120a that imports working fluids to compressor operating chamber 123, on the obstruction component adjacent, be provided with from the compressor operating chamber with compressor operating cylinder 121 and compressor piston 122 113 discharge working fluids tap hole 120b.Inlet hole 120a is at the inner peripheral surface opening of compressor operating cylinder 121, only the sliding point in compressor piston 122 sliding on the inner peripheral surface of compressor operating cylinder 121 be positioned on the inlet hole 120a during be compressed machine piston 122 and close.
In addition, the refrigerating circulatory device shown in Figure 15 200 that uses above-mentioned fluid machinery 100 and process is disclosed in patent documentation 1.This refrigerating circulatory device 200 is to utilize 120 pairs on the compressor of fluid machinery 100 to be drawn into the device that working fluid in the main compressor 210 carries out pre-loading, and main compressor 210, radiator 220, decompressor 110, vaporizer 230 and compressor 120 are linked in sequence through stream and constitute operating fluid loop.
[look-ahead technique document]
[patent documentation]
[patent documentation 1] TOHKEMY 2004-324595 communique
Suppose that fluid machinery 100 does not possess driving mechanisms such as motor, and self-starting under the pressure of the working fluid in the refrigerating circulatory device 200 of that kind shown in Figure 15.That is, start, thereby the working fluid of high pressure is flowed into to the suction side of the decompressor working room 113 of decompressor 110 through making main compressor 210.Thus, in the suction side of decompressor working room 113 and discharge between the side and produce differential pressure, give torque through this differential pressure to axle 101 and make fluid machinery 100 startings.
Yet when fluid machinery 100 stopped under the pent state of the inlet hole 110a of decompressor 110, the working fluid of high pressure can't flow into to decompressor working room 113, can not produce the torque that makes axle 101 rotations.
To this, inventor of the present invention etc. are before the present invention, and the working fluid of the high pressure of considering will to discharge from main compressor in when starting also guides to the compressor of fluid machinery, in compressor, also can give torque to axle like this.Promptly; The high pressure stream that connects between main compressor and radiator or radiator and the decompressor and the bypass of the low pressure stream between vaporizer and the compressor are set; The working fluid that the time makes high pressure in starting also flows into to the suction side of the compressor operating chamber of compressor, between the suction side of compressor operating chamber and discharge side, also can produce differential pressure thus.Thus, in compressor, also can give torque to axle.
Yet,, still have the situation that does not produce the torque that makes axle 101 rotations even in patent documentation 1 disclosed fluid machinery 100, be suitable for above-mentioned technology.It the reasons are as follows.
In patent documentation 1 disclosed fluid machinery 100; The position of the position of decompressor partition member 114 and compressor partition member 124 axle 101 axially on consistent, the eccentric direction of the eccentric direction of first eccentric part 102 and second eccentric part 103 staggers 180 °.In addition, in compressor 120, at the sliding point of compressor piston 121 through tap hole 120b and during near inlet hole 120a, inlet hole 120a is communicated with tap hole 120b via compressor operating chamber 123.
Therefore, if the angle of swing of the axle 101 when decompressor piston 112 is positioned at top dead center is made as 0 °, then in decompressor 110, the angle of swing of axle 101 be 0 ° during about 140 ° working fluid can flow into to the suction side of decompressor working room 113.On the other hand; In compressor 120, though the angle of swing of axle 101 be about 190 ° during about 200 °, the inlet hole 120a of compressor 120 is compressed machine piston 122 and closes; But during in addition, working fluid can flow into to the suction side of compressor operating chamber 123.
Yet, the angle of swing of axle 101 be about 190 ° during about 200 °, decompressor inlet hole 110a and this two side of compressor inlet hole 120a are closed, and in decompressor 110 and compressor 120, all can't produce the torque that axle 110 is rotated.In addition; In the angle of swing of axle 101 for close on inlet hole 120a about 190 ° from the sliding point of compressor piston 121 about 180 ° of the sliding points through tap hole 120b during to compressor piston 121; As above-mentioned; Inlet hole 120a is communicated with tap hole 120b via compressor operating chamber 123, discharges from tap hole 120b from the working fluid that inlet hole 120a flow into the compressor operating chamber 123.And this moment, the inlet hole 110a of decompressor 110 also was closed.Thereby, be that fluid machinery 100 stops under the state between about 180 ° and about 200 ° in the angle of swing of axle, can't utilize this moment the pressure of working fluid to produce the torque that makes axle 101 rotations, can't make fluid machinery 100 self-startings.
Summary of the invention
The present invention In view of the foregoing makes, and its purpose is to provide a kind of refrigerating circulatory device that no matter under which kind of state, stops to utilize the self-running fluid machinery of pressure of working fluid and used this fluid machinery.
In order to solve said problem, fluid machinery provided by the invention possesses: decompressor, and it makes from the working fluid expansion of decompressor inlet hole suction and from the decompressor tap hole and discharges, and reclaims power from working fluid thus; Compressor, it boosts the working fluid that sucks from the compressor inlet hole and discharges from the compressor tap hole; Axle; It links said decompressor and said compressor; Thereby utilize the power that is reclaimed by said decompressor to drive said compressor, said decompressor inlet hole and said compressor inlet hole open and close along with the rotation of said axle, and said fluid machinery is maintained in; In said compressor inlet hole closed period; Said decompressor inlet hole is in the state of opening, and in said decompressor inlet hole closed period, said compressor inlet hole is in state of opening and the state that is not communicated with said compressor tap hole.
In addition; Refrigerating circulatory device provided by the present invention has used above-mentioned fluid machinery; It possesses: operating fluid loop; It makes working fluid cycles, comprise compression working fluid main compressor, make the working fluid heat radiation after the compression radiator, make said decompressor that the working fluid that flows out from said radiator expands, make the vaporizer of the working fluid evaporation after the expansion and will boost from the working fluid that said vaporizer flows out and the said compressor supplied with to said main compressor; Bypass, it is connected the part between the part between the said main compressor in the said operating fluid loop and the said radiator or said radiator and the said decompressor and said vaporizer with part between the said compressor.
[invention effect]
According to above-mentioned structure; Working fluid can be all the time a certain side or both sides in the suction side of the suction side of decompressor working room and compressor operating chamber flow into; And prevent to flow into the situation that the working fluid in the compressor operating chamber is discharged from the compressor tap hole; Therefore no matter fluid machinery stops under which kind of state, can both utilize the pressure of working fluid to make the fluid machinery self-starting.
Description of drawings
Fig. 1 has been to use the structural drawing of the refrigerating circulatory device of the related fluid machinery of first mode of execution of the present invention.
Fig. 2 is the longitudinal sectional view of the related fluid machinery of first mode of execution of the present invention.
Fig. 3 is the III-III line sectional view of Fig. 2.
Fig. 4 is the IV-IV line sectional view of Fig. 2.
Fig. 5 is the V-V line sectional view of Fig. 2.
Fig. 6 A～6C is the schematic diagram of movements of the related fluid machinery of first mode of execution of the present invention.
Fig. 7 A～7C is the schematic diagram of movements of the related fluid machinery of first mode of execution of the present invention.
Fig. 8 is the longitudinal sectional view of the related fluid machinery of second mode of execution of the present invention.
Fig. 9 is the IX-IX line sectional view of Fig. 8.
Figure 10 A～10C is the schematic diagram of movements of the related fluid machinery of second mode of execution of the present invention.
Figure 11 A～11C is the schematic diagram of movements of the related fluid machinery of second mode of execution of the present invention.
Figure 12 is the longitudinal sectional view of existing fluid machinery.
Figure 13 is the A-A line sectional view of Figure 12.
Figure 14 is the B-B line sectional view of Figure 12.
Figure 15 has been to use the structural drawing of refrigeration cycle of the fluid machinery of Figure 12.
Embodiment
Below, with reference to accompanying drawing mode of execution of the present invention is described.Need to prove that the present invention is not limited to following mode of execution.
(first mode of execution)
< structure of refrigerating circulatory device >
Fig. 1 has been to use the structural drawing of the refrigerating circulatory device 1 of the related fluid machinery 8A of first mode of execution of the present invention.This refrigerating circulatory device 1 possesses the working fluid of making (refrigeration agent) circuit operating fluid loop 7.Operating fluid loop 7 comprises main compressor 2, radiator 3, decompressor 4, vaporizer 5, and as the compressor 6 of auxiliary compressor, above-mentioned 2～6 are linked in sequence by this through first～the 5th stream (pipe arrangement) 7a～7e constitutes.Can use for example carbon dioxide or chloro-fluoro-hydrocarbons substitute as working fluid.
The working fluid of the low-temp low-pressures after 5 pairs in vaporizer expands in decompressor 4 heats and makes its evaporation.The outlet of vaporizer 5 is connected with the suction port of compressor 6 via the 4th stream 7d.
The working fluid of 6 pairs of warm low pressure from vaporizer 5 outflows of compressor carries out pre-loading and it is supplied with to main compressor 2.In this mode of execution, compressor 6 constitutes (details narration in the back) by rotary compressor.The exhaust port of compressor 6 is connected with the suction port of main compressor 2 via the 5th stream 7e.
And then refrigerating circulatory device 1 shown in Figure 1 possesses: first bypass 91 that is connected with operating fluid loop 7 with the mode two ends that get around vaporizer 5 and compressor 6; Second bypass (being equivalent to bypass of the present invention) 93 that is connected with operating fluid loop 7 with the mode two ends that get around decompressor 4 and vaporizer 5.On first bypass 91, be provided with first bypass valve 92 of the circulation of the working fluid in control first bypass 91, on second bypass 93, be provided with second bypass valve 94 of the circulation of the working fluid in control second bypass 93.
Ratio first bypass valve 92 of first bypass valve 92 in first bypass 91 can circulate working fluid when leaning on the pressure of the working fluid in downstream side (outlet side) to be lower than the pressure of working fluid of upstream side (inlet side) in first bypass 91, on the contrary the time working fluid can not be circulated in first bypass 91.Promptly; When the pressure of the working fluid in the 5th stream 7e between the suction port of the exhaust port of compressor 6 and main compressor 2 was lower than the pressure of the working fluid in the stream (the 3rd stream 7c, vaporizer 5, the 4th stream 7d) between the suction port of exhaust port and compressor 6 of decompressor 4, working fluid flowed into to the 5th stream 7e via first bypass 91 from the 3rd stream 7c.
In addition, in refrigerating circulatory device shown in Figure 11, between the outlet of the vaporizer 5 in the 4th stream 7d and the position that the downstream of second bypass 93 links to each other, be provided with the upstream of compressor valve 71 of the circulation of the working fluid among control the 4th stream 7d.In this mode of execution, used open and close valve as upstream of compressor valve 71.Upstream of compressor valve 71 cuts out in starting control, prevents situation that working fluid flows to compressor 6 from vaporizer 5, and the working fluid that in the 4th stream 7d, flows into through second bypass 93 situation about flowing to vaporizer 5 thus.
< action of refrigerating circulatory device >
Refrigerating circulatory device 1 at first starts control, begins steady running afterwards.In refrigerating circulatory device 1, when the running holding state (when stopping), the pressure approximate equality of the working fluid in the operating fluid loop 7.
In starting control, at first open second bypass valve 94, close compressor upstream valve 71.Thus, second bypass 93 is open-minded, and the 4th stream 7d seals between the downstream of the outlet of vaporizer 5 and second bypass 93.Then, starting main compressor 2 sucks working fluid in the 5th stream 7e, and the working fluid that leans in first bypass 91 in downstream side than first bypass valve 92 in main compressor 2.
Working fluid begins when main compressor 2 sucks, and the working fluid in the 5th stream 7e, and leans on the pressure of the working fluid in first bypass 91 in downstream side to reduce than first bypass valve 92.Thus, open first bypass valve 92 as safety check, the working fluid in the stream till exhaust port to the upstream of compressor valve 71 of decompressor 4 (the 3rd stream 7c, vaporizer 5, the 4th stream 7d an one) flows into to first bypass 91.That is, working fluid and the working fluid five stream 7e in of the working fluid in the stream till exhaust port to the upstream of compressor valve 71 of decompressor 4 in first bypass 91 is drawn into the main compressor 2 and is compressed, and discharges to the first stream 7a.Consequently, than first bypass valve 92 lean on working fluid in first bypass 91 of upstream side, and stream till exhaust port to the upstream of compressor valve 71 of decompressor 4 in the pressure of working fluid also reduce.
On the other hand, the working fluid that is drawn in the main compressor 2 is compressed and discharges, and the pressure of the working fluid in the stream (the first stream 7a, radiator 3, the second stream 7b) till the suction port of exhaust port to the decompressor 4 of main compressor 2 rises thus.In addition; Since when control starting second bypass valve 94 open and upstream of compressor valve 71 cuts out, therefore the working fluid in the stream till the suction port of exhaust port to the decompressor 4 of main compressor 2 is through the part inflow between the suction port of the second bypass 93 also upstream of compressor valve 71 to the 4th stream 7d and compressor 6.Thus, the pressure of the working fluid in the stream till the suction port of upstream of compressor valve 71 to compressor 6 (the 4th stream 7d an one) rises.
Thereby, between the working fluid (low pressure) in the working fluid (high pressure) in the suction port effluent road of decompressor 4 (the second stream 7b) and exhaust port effluent road (the 3rd stream 7c), and the suction port effluent road (part of the 4th stream 7d) of compressor 6 in working fluid (high pressure) and exhaust port effluent road (the 5th stream 7e) in working fluid (low pressure) between generation pressure difference just respectively.The height pressure difference of this working fluid does not act on decompressor 4 and the compressor 6, thereby can easily make fluid machinery 8A self-starting.
When above-mentioned starting feeler mechanism detects compressor 6 and has started this situation, close second bypass valve 94, open upstream of compressor valve 71.Thus, seal second bypass 93, open the 4th stream 7d.And refrigerating circulatory device 1 finishes starting control, shifts to and makes working fluid circuit steady running in operating fluid loop 7.
When steady running, the working fluid in the 4th stream 7d, and lean on working fluids in second bypass 93 in downstream side to be inhaled in the compressor 6 than second bypass valve 94 and boost, discharge to the 5th stream 7e.Thus; The pressure of the working fluid in the 5th stream 7e, and lean on than first bypass valve 92 pressure of the working fluid in first bypass 91 in downstream side be higher than the working fluid in the stream (the 3rd stream 7c, vaporizer 5, the 4th stream 7d) till the suction port of exhaust port to the compressor 6 of decompressor 4 pressure, and lean on the pressure of the working fluid in first bypass 91 of upstream side than first bypass valve 92, close first bypass valve 92 into safety check.In steady running, the working fluid in the 5th stream 7e, and lean on pressure and the above-mentioned high pressure that likewise becomes of the working fluid in first bypass 91 in downstream side than first bypass valve 92, so first bypass valve 92 is kept closed condition.Thus, the working fluid in the steady running circulates in operating fluid loop 7.
< structure of fluid machinery >
Next, the structure of fluid machinery 8A at length is described.Fig. 2 is the longitudinal sectional view of fluid machinery 8A.In addition, Fig. 3～5th, the transverse sectional view of the fluid machinery 8A corresponding with III-III line～V-V line of Fig. 2.Need to prove, in Fig. 3～5, omitted seal container 80.
As stated, fluid machinery 8A is a decompressor 4 and compressor 6 links the power recovery system that utilizes the power driven compressor 6 that decompressor 4 reclaimed through axle 81.In this mode of execution, axle 81 extends along vertical, and decompressor 4 is configured in the bottom in the seal container 80, and compressor 6 is configured in the top in the seal container 80.Wherein, decompressor 4 can turn upside down with the position relation of compressor 6, and axle 81 also can be along horizontal expansion, and decompressor 4 can also be along transversely arranged with compressor 6.In addition, lubricant oil in seal container 80, be filled to pasta be positioned at compressor 6 above degree.
1) axle
2) decompressor
As stated, in this mode of execution, decompressor 4 is made up of the rotary type decompressor.Yet decompressor 4 is not limited to the rotary type decompressor, also can be made up of the decompressor of scroll expansion machine or other form.Decompressor 4 makes it discharge from decompressor tap hole 4b through making the working fluid expansion that sucks from decompressor inlet hole 4a, reclaims power from working fluid thus.
Particularly, as shown in Figure 4, decompressor 4 has the decompressor piston 42 chimeric with the first eccentric part 81b of axle 81, accommodates the decompressor clutch release slave cylinder 41 of decompressor piston 42.Decompressor clutch release slave cylinder 41 has the inner peripheral surface that forms the central shaft barrel surface consistent with the axle center of axle 81, and decompressor piston 42 carries out off-centre along with the rotation of axle 81 along the inner peripheral surface of decompressor clutch release slave cylinder 41 and rotatablely moves.That is, between the outer circumferential face of the inner peripheral surface of decompressor clutch release slave cylinder 41 and decompressor piston 42, form the decompressor working room 43 of crescent shape.
In addition; As shown in Figure 2, decompressor 4 has from first obstruction component (inboard obstruction component) 49 of the inaccessible decompressor of compressor 6 sides working room 43, from second obstruction component (outside obstruction component) 46 of the inaccessible decompressor of the opposition side working room 43 of compressor 6, is configured in the bearing components 47 of the below of second obstruction component 46.
Be provided with the recess 46a of the center toroidal consistent at the lower surface of second obstruction component 46 with the axle center of axle 81, decompressor inlet hole 4a with from the upper surface of second obstruction component 46 to the mode of the straight extension in the bottom surface of recess 46a axial perforation second obstruction component 46 along axle 81.Decompressor inlet hole 4a is communicated with suction pipe 82 via suction space in the recess 46a and the inlet passage 47a that is formed on the bearing components 47.That is, the working fluid of high pressure from the second stream 7b shown in Figure 1 via the suction space in suction pipe 82, inlet passage 47a and the recess 46a from the suction side 43a of decompressor inlet hole 4a guiding decompressor working room 43.
On the other hand; As shown in Figure 4; Decompressor tap hole 4b is made up of pod 41b and translot 49a, and wherein, said pod 41b is formed on the inner peripheral surface of decompressor clutch release slave cylinder 41; And to the radial outside depression, said translot 49a forms with the mode of extending towards radial outside from the position corresponding with pod 41b at the lower surface of first obstruction component 49.The outboard end of decompressor tap hole 4b is communicated with discharge tube 83 via the discharge road 4c that forms with the mode of striding decompressor clutch release slave cylinder 41, second obstruction component 46 and bearing components 47 extensions.That is, the working fluid in the discharge side 43b of decompressor working room 43 is discharged to the 3rd stream 7c shown in Figure 1 via decompressor tap hole 4b, discharge road 4c and discharge tube 83.
And then, in recess 46a, dispose swivel plate 48 as the suction control mechanism that opens and closes decompressor inlet hole 4a along with the rotation of axle 81.This swivel plate 48 is installed on the axle 81 with the mode of rotation when the bottom surface with recess 46a joins.
As shown in Figure 4, decompressor inlet hole 4a extends near decompressor partition member 44 inner peripheral surface and being circular-arcly along decompressor clutch release slave cylinder 41.As shown in Figure 3, swivel plate 48 has the large-diameter portion 48a that blocks decompressor inlet hole 4a, the minor diameter part 48b that decompressor inlet hole 4a is exposed
In this mode of execution; Angular range and position according to large-diameter portion 48a and minor diameter part 48b; Decompressor piston 41 from top dead center to rotate about 140 ° during, decompressor inlet hole 4a is local or fully expose, decompressor inlet hole 4a is blocked by large-diameter portion 48a fully during other.Here, top dead center is meant the sliding point that on the inner peripheral surface of decompressor clutch release slave cylinder 41, slides and decompressor partition member 44 consistent location of decompressor piston 42.
Need to prove that the structure of decompressor 4 can be reversed up and down.Promptly; Can be with first obstruction component 49, decompressor clutch release slave cylinder 41, second obstruction component 46, swivel plate 48 and bearing components 47 from bottom to up by this arranged in order; Thereby first obstruction component 49 becomes outside obstruction component, and second obstruction component 46 becomes inboard obstruction component.In this case, can be on bearing components 47 the chimeric axle 81 of play, make first obstruction component 49 have the function of lower support for rotating with axle 81.
3) compressor
As stated, in this mode of execution, compressor 6 is made up of rotary compressor.Compressor 6 will boost from the working fluid that compressor inlet hole 6a sucks and it discharged from compressor tap hole 6b.
Particularly, as shown in Figure 5, compressor 6 has the compressor piston 62 chimeric with the second eccentric part 81c of axle 81, accommodates the compressor operating cylinder 61 of compressor piston 62.Compressor operating cylinder 61 has the inner peripheral surface that forms the central shaft barrel surface consistent with the axle center of axle 81, and compressor piston 62 carries out off-centre along with the rotation of axle 81 along the inner peripheral surface of compressor operating cylinder 61 and rotatablely moves.That is, between the outer circumferential face of the inner peripheral surface of compressor operating cylinder 61 and compressor piston 62, be formed with the compressor operating chamber 63 of crescent shape.
In addition; As shown in Figure 2, compressor 6 has from first obstruction component (inboard obstruction component) 49 of the inaccessible compressor operating of decompressor 4 sides chamber 63, from second obstruction component (outside obstruction component) 66 of the inaccessible compressor operating of the opposition side chamber 63 of decompressor 4, is configured in the cover member 67 of the top of second obstruction component 46.That is, in this mode of execution, decompressor 4 has first obstruction component 49 with compressor 6.Yet decompressor 4 also can have first obstruction component respectively with compressor 6.
Because compressor inlet hole 6a, therefore is compressed machine piston 62 in the inner peripheral surface upper shed of compressor operating cylinder 61 and opens and closes along with the rotation of axle.More detailed; Compressor inlet hole 6a the sliding point sliding on the inner peripheral surface of compressor operating cylinder 61 of compressor piston 62 be positioned on the compressor inlet hole 6a during be compressed machine piston 62 and close, in other words with top dead center (sliding point of compressor piston 62 and compressor partition member 64 consistent location) when being made as 0 ° compressor piston 62 rotate to from about 5 ° and be compressed machine piston 62 during about 15 ° and close.Need to prove; The diameter of the inner peripheral surface of compressor operating cylinder 61 is different with the diameter of the outer circumferential face of compressor piston 62; Therefore compressor inlet hole 6a can not be compressed machine piston 62 tightly and closes fully; But in this manual, as above-mentioned, be defined as sliding point at compressor piston 62 be positioned on the compressor inlet hole 6a during compressor inlet hole 6a be closed.
On the other hand, on second obstruction component 66, be formed with in upper surface open and by the discharge chamber 66a of cover member 67 obturations, from discharging the discharge road 66b of chamber 66a to discharge tube 85.Compressor tap hole 6b with from the lower surface of second obstruction component 66 to discharging mode that chamber 66a extends as the crow flies with axial perforation second obstruction component 66 of circular cross-section along axle 81, and be communicated with discharge tube 85 via discharging chamber 66a and discharging road 66b.That is, the working fluid in the discharge side 63b of compressor operating chamber 63 is discharged to the 5th stream 7e shown in Figure 1 via compressor tap hole 6b, discharge chamber 66a, discharge road 66b and discharge tube 85.
In this mode of execution; Because compressor tap hole 6b is configured on the position of the inner peripheral surface crosscut that is compressed machine clutch release slave cylinder 61; Therefore the sliding point of compressor piston 62 be positioned on the compressor tap hole 6b during compressor tap hole 6b be compressed machine piston 62 and close, in other words when top dead center is made as 0 ° compressor piston 62 from about 345 ° rotate to about 355 ° during compressor tap hole 6b be compressed machine piston 62 and close.Need to prove; With compressor inlet hole 6a likewise; Compressor tap hole 6b can not be compressed machine piston 62 tightly and close fully; But in this manual, as above-mentioned, be defined as sliding point at compressor piston 62 be positioned on the compressor tap hole 6b during compressor tap hole 6b be closed.
In addition, in discharging chamber 66a, dispose expulsion valve 68, this expulsion valve 68 automatically opens and closes compressor tap hole 6b through resiliently deformable under the pressure of the discharge side 63b of compressor operating chamber 63.
As stated,, can reduce the flow path resistance of the working fluid that flows into to compressor operating chamber 63 thus, the reduction of the pressure of the working fluid that can suppress to suck to compressor 6 through forming compressor inlet hole 6a.In addition, as stated,, can simplify the structure of compressor 6 thus, can reduce from the compressor operating chamber flow path resistance of 63 working fluids that flow out, the reduction of the pressure of the working fluid that can suppress to discharge from compressor 6 through forming compressor tap hole 6b.
Need to prove that the structure of compressor 6 can be reversed up and down.That is, also can be with cover member 67, second obstruction component 66, compressor operating cylinder 61 and first obstruction component 49 from bottom to up by this arranged in order, thus first obstruction component 49 becomes outside obstruction component, and second obstruction component 66 becomes inboard obstruction component.In this case, can be on second obstruction component 66 the chimeric axle 81 of play, make first obstruction component 49 have the function of upper support for rotating with axle 81.
4) correlation
In order to realize above-mentioned correlation; Preferably the sense of rotation with axle 81 be made as correct time the second eccentric part 81c eccentric direction with respect to the phase difference of the eccentric direction of the first eccentric part 81b be β c (wherein;-180 °＜β c≤180 °), the position of compressor partition member 64 with respect to the phase difference of the position of decompressor partition member 44 be β v (wherein;-180 °＜β v≤180 °) and the angle of swing of the axle of decompressor inlet hole 6a during opening when being θ o, the formula 1 below satisfying.
0.25 θ o≤β v-β c≤0.75 θ o ... (formula 1)
In this mode of execution, like Fig. 4 and shown in Figure 5, the position of the position of decompressor partition member 44 and compressor partition member 64 axle 81 axially on consistent, the eccentric direction of the second eccentric part 81c staggers-90 ° with respect to the eccentric direction of the first eccentric part 81b.That is, β c=-90 °, β v=0 °, c=90 ° of β v-β.In addition, according to the shape of the swivel plate 48 of above-mentioned that kind, about 140 ° of θ o=.Thus, 35 ° of 0.25 θ o ≈, 105 ° of 0.75 θ o ≈ satisfy formula 1.
Need to prove that the present invention is not limited thereto.For example; Also can the first eccentric part 81b and the second eccentric part 81c to equidirectional off-centre; The position of the position of decompressor partition member 44 and compressor partition member 64 changes in the scope that satisfies formula 1, also can eccentric direction and this two side of position of partition member in the scope that satisfies formula 1, change.
< action of fluid machinery >
Next, with reference to Fig. 6 A～6C and Fig. 7 A～7C, the action of the fluid machinery 8A in the steady running is described.In above-mentioned figure, the angle of swing θ of the axle 81 when decompressor piston 42 is positioned at top dead center is made as 0 °.
At first, the action to decompressor 4 describes.Shown in Fig. 6 A～6C, axle 81 ° begins rotation from θ=0, and swivel plate 48 is synchronously rotation therewith, and decompressor inlet hole 4a begins to expose from swivel plate 48 thus, and decompressor inlet hole 4a opens.And, be inhaled into to the suction side of decompressor working room 43 43a through decompressor inlet hole 4a from the working fluid of the high pressure of radiator 3.Afterwards, decompressor inlet hole 4a exposes fully when axle 81 has rotated about 30 °.On the other hand, shown in Fig. 7 A and 7B, swivel plate 48 begins to block decompressor inlet hole 4a when axle 81 has rotated about 125 °, and decompressor inlet hole 4a is blocked fully when axle 81 has rotated about 140 °, and decompressor inlet hole 4a closes.Thus, suction stroke finishes.
Afterwards, shown in Fig. 7 C, along with the rotation of axle 81, the volume of the suction side 63a of decompressor working room 63 increases gradually, and working fluid expands thus, and axle 81 is applied torque.And, be applied to this torque on 81 and be utilized power as compressor 6.Axle 81 rotations 360 ° and decompressor piston 42 passes through top dead center; The suction side 43a of decompressor working room 43 changes to discharging side 43b thus; Axle 81 rotates a circle afterwards, and the working fluid after expanding is thus discharged towards vaporizer 5 through decompressor tap hole 4b from discharging side 43b.
Next, the action to compressor 6 describes.Axle 81 rotation under the effect of the power that reclaims by decompressor 4.In this 81 rotation, compressor piston 62 also rotates, and compressor 6 is driven.
Shown in Fig. 6 C and Fig. 7 A, compressor inlet hole 6a opens when axle 81 has rotated about 105 °, comes the working fluid of the low pressure of from evaporator drier 5 to suck to the suction side of compressor operating chamber 63 63a through compressor inlet hole 6a.And; Compressor piston 62 is further rotated; The suction side 63a of compressor operating chamber 63 is with after compressor tap hole 6b is communicated with; Compressor piston 62 is through top dead center, and the suction side 63a of compressor operating chamber 63 changes to discharging side 63b thus, and this moment, the volume of the discharge side 63b of compressor operating chamber 63 along with the rotation of axle 81 dwindled gradually.Thus, the working fluid in the discharge side 63b of compressor operating chamber 63 is compressed and boosts.And; When the pressure of the working fluid in the discharge side 63b of compressor operating chamber 63 becomes when being higher than the pressure of discharging the working fluid in the 66a of chamber; The working fluid of discharging in the side 63b presses off expulsion valve 68, discharges towards main compressor 2 through compressor tap hole 6b.
< effect of this mode of execution and effect >
In this mode of execution, as stated, decompressor inlet hole 4a open during be θ=0 °～about 140 °, decompressor inlet hole 4a closed period is θ=about 140 °～360 °.On the other hand, compressor inlet hole 6a closed period is θ=about 95 °～about 105 °, compressor inlet hole 6a open during be 95 ° of θ=0 °～about and θ=about 105～360 °.In addition, compressor tap hole 6b via compressor operating chamber 63 be communicated with compressor tap hole 6b during be θ=about 85 °～about 95 °.That is, be communicated with back decompressor inlet hole 4a with the suction side 63a of compressor operating chamber 63 at compressor inlet hole 6a and close, open with decompressor inlet hole 4a before compressor tap hole 6b is communicated with at the suction side of compressor operating chamber 63 63a.
This hurdle is illustrated like < action of refrigerating circulatory device >; When refrigerating circulatory device 1 starting; Starting main compressor 2 under the state of opening second bypass valve 94 and close compressor upstream valve 71, thus between the working fluid and the working fluid in the exhaust port effluent road in the suction port effluent road of decompressor 4, and the suction port effluent road of compressor 6 in working fluid and the working fluid in the exhaust port effluent road between generation pressure difference just respectively.In other words, the upstream side stream of the decompressor inlet hole 4a of the suction pipe 82 through fluid machinery 8A, and the upstream side stream of the compressor inlet hole 6a through suction pipe 84 filled up by the working fluid of high pressure.
In this mode of execution; Fluid machinery 8A constitutes as above-mentioned; Therefore when refrigerating circulatory device 1 starting; No matter which angular orientation the axle 81 of fluid machinery 8A is positioned at, and has at least one side among decompressor inlet hole 4a or the compressor inlet hole 6a to open all the time, and at least one side inflow of working fluid in the suction side 63a of the suction side of decompressor working room 43 43a or compressor operating chamber 63 of high pressure arranged all the time.In addition, compressor inlet hole 6a is after decompressor inlet hole 4a opens via compressor operating chamber 63 and being communicated with of compressor tap hole 6b.Thereby no matter fluid machinery 8A stops under which kind of state, can both produce the torque that makes axle 81 rotations a side or the both sides of decompressor 4 and compressor 6, thereby can make fluid machinery 8A self-starting under the pressure of working fluid.
Particularly; Be positioned at axle 81 under the situation of scope of θ=0 °～about 85 °; Because decompressor inlet hole 4a and compressor inlet hole 6a all open; The working fluid of high pressure flows into to the suction side 63a of the suction side of decompressor working room 43 43a and compressor operating chamber 63, therefore on decompressor 4 and compressor 6, produces torque.
Be positioned at axle 81 under the situation of scope of θ=about 85 °～about 95 °; Compressor inlet hole 6a closes; But be communicated with compressor tap hole 6b via compressor operating chamber 63; Working fluid flows through to compressor tap hole 6b from compressor inlet hole 6a, therefore on compressor 6, does not produce torque.Yet because decompressor inlet hole 4a opens, the working fluid of high pressure flows into to the suction side of decompressor working room 63, therefore on decompressor 4, produces torque.
Be positioned at axle 81 under the situation of scope of θ=about 95 °～105 °.Compressor inlet hole 6a closes, and on compressor 6, does not produce torque, but because decompressor inlet hole 4a opens, and the working fluid of high pressure flows into to the suction side of compressor operating chamber 63 63a, therefore on compressor 6, produces torque.
Be positioned at axle 81 under the situation of scope of θ=about 105 °～about 140 °; Because decompressor inlet hole 4a and compressor inlet hole 6a all open; The working fluid of high pressure flows into to the suction side 63a of the suction side of decompressor working room 43 43a and compressor operating chamber 63, therefore on decompressor 4 and compressor 6, produces torque.
Be positioned at axle 81 under the situation of scope of θ=about 140 °～360 °; Decompressor inlet hole 4a closes; On decompressor 4, do not produce torque; But because compressor inlet hole 6a opens, the working fluid of high pressure flows into to the suction side of compressor operating chamber 63 63a, therefore on compressor 6, produces torque.
Like this, in this mode of execution, when refrigerating circulatory device 1 starting, only utilize the pressure of working fluid just can make fluid machinery 8A self-starting reliably, can improve the reliability of refrigerating circulatory device 1 with drive unit.
(second mode of execution)
Next, with reference to Fig. 8 and Fig. 9, the fluid machinery 8B related to second mode of execution of the present invention describes.Need to prove, in this mode of execution,, and omit explanation the structure division mark prosign identical with first mode of execution.In addition, used the refrigerating circulatory device of fluid machinery 8B identical, therefore also omitted explanation with refrigerating circulatory device 1 shown in Figure 1.
< structure of fluid machinery >
The difference of the fluid machinery 8B of this mode of execution and the fluid machinery 8A of first mode of execution is that suction pipe 84 is connected this point with second obstruction component 66, and compressor 6 does not possess expulsion valve 68 (with reference to Fig. 2) and becomes hydrodynamic pressure motor-type compressor.That is, compressor 6 boosts working fluid under the situation of the volume that does not change working fluid.
Particularly; Compressor inlet hole 6a is only to be arranged on second obstruction component 66 to the mode that the suction side of compressor operating chamber 63 63a exposes, and compressor tap hole 6b is arranged on second obstruction component 66 with the mode of only exposing to the discharge side 63b of compressor operating chamber 63.Compressor inlet hole 6a and compressor tap hole 6b be extending axially along axle 81 all.In addition, the discharge road 6d that on second obstruction component 66, be formed with inlet passage 6c that the upper end with compressor inlet hole 6a is communicated with suction pipe 84, the upper end of compressor tap hole 6b is communicated with discharge tube 85.
More detailed, compressor inlet hole 6a and compressor tap hole 6b extend near the mode with the inner peripheral surface that leaves compressor operating cylinder 61 gradually of compressor partition member 64.And, consistent circular-arc of the outer circumferential face of the compressor piston 62 the when outer side of compressor inlet hole 6a and compressor tap hole 6b (limit of the inner peripheral surface side of compressor operating cylinder 61) forms and is positioned at top dead center with compressor piston 62.That is, compressor inlet hole 6a closes at the machine that is compressed the in a short time piston 63 that compressor piston 62 is positioned at atdc fully, and compressor tap hole 6b closes at the machine that is compressed the in a short time piston 63 that compressor piston 62 is positioned at budc fully.
In addition, in this mode of execution, the eccentric direction of the first eccentric part 81b of axle 81 is identical with first mode of execution with the relation of the position of the relation of the eccentric direction of the second eccentric part 82b, the position that reaches decompressor partition member 44 and compressor partition member 64.
Need to prove that compressor inlet hole 6a and compressor tap hole 6b may not be arranged on second obstruction component 66, also can arbitrary side or both sides be arranged on first obstruction component 49.
< action of fluid machinery 8B >
Next, with reference to Figure 10 A～10C and Figure 11 A～11C, the action of the fluid machinery 8A in the steady running is described.In above-mentioned figure, the angle of swing θ of the axle 81 when decompressor piston 42 is positioned at top dead center is made as 0 °.Need to prove,, therefore omit its explanation because the action of decompressor 4 is identical with first mode of execution.
Shown in Figure 10 C and Figure 11 A～11C, compressor inlet hole 6a rotates to from 90 ° at axle 81 and is compressed machine piston 62 during about 95 ° and closes fully.After about 95 ° of axle 81 rotations, compressor inlet hole 6a opens gradually, comes the working fluid of the low pressure of from evaporator drier 5 to be inhaled into to the suction side 63a of compressor suction working room 63 through compressor inlet hole 6a.Afterwards, shown in Figure 10 A and 11B, after compressor piston 62 rotated to about 360 °, compressor inlet hole 6a closed gradually.When axle 81 rotated to 90 ° once more, suction stroke finished.The suction side 63a of compressor operating chamber 63 changes to discharging side 63b.Behind axle 81 half-twists, compressor tap hole 6b opens gradually, and the working fluid of discharging in the side 63b is discharged towards main compressor 2 through compressor tap hole 6b.The extrusion of the working fluid that is carried out through such compressor piston 62, working fluid is boosted.Compressor tap hole 6b closes after about 300 ° of axle 81 rotation gradually, axle 81 rotate to from about 85 ° 90 ° during be compressed machine piston 62 and close fully.
< effect of this mode of execution and effect >
In this mode of execution, as stated, decompressor inlet hole 4a open during be θ=0 °～about 140 °, decompressor inlet hole 4a closed period is θ=about 140 °～360 °.On the other hand, compressor inlet hole 6a closed period is θ=90 °～about 95 °, compressor inlet hole 6a open during be θ=0 °～90 ° and θ=about 95～360 °.That is, be communicated with back decompressor inlet hole 4a with the suction side 63a of compressor operating chamber 63 at compressor inlet hole 6a and close, decompressor inlet hole 4a opens before compressor inlet hole 6a closes.
This hurdle is illustrated like < action of refrigerating circulatory device >; During refrigerating circulatory device 1 starting; Starting main compressor 2 under the state of opening second bypass valve 94 and close compressor upstream valve 71, thus between the working fluid and the working fluid in the exhaust port effluent road in the suction port effluent road of decompressor 4, and the suction port effluent road of compressor 6 in working fluid and the working fluid in the exhaust port effluent road between generation pressure difference just respectively.In other words, the upstream side stream of the decompressor inlet hole 4a of the suction pipe 82 through fluid machinery 8A, and the upstream side stream of the compressor inlet hole 6a through suction pipe 84 filled up by the working fluid of high pressure.
In this mode of execution; Fluid machinery 8A constitutes as above-mentioned; Therefore when refrigerating circulatory device 1 starting; No matter which angular orientation the axle 81 of fluid machinery 8A is positioned at, and at least one side among decompressor inlet hole 4a or the compressor inlet hole 6a also can open all the time, at least one side inflow that the working fluid of high pressure all the time can be in the suction side 63a of the suction side of decompressor working room 43 43a or compressor operating chamber 63.Thereby no matter fluid machinery 8A stops under which kind of state, can both on side of decompressor 4 and compressor 6 or both sides, produce a torque that makes axle 81 rotations, thereby can make fluid machinery 8A utilize the pressure self-starting of working fluid.
Particularly; Be positioned at axle 81 under the situation of scope of θ=0 °～90 °; Because decompressor inlet hole 4a and compressor inlet hole 6a all open; The working fluid of high pressure flows into to the suction side 63a of the suction side of decompressor working room 43 43a and compressor operating chamber 63, therefore produces torque by decompressor 4 and compressor 6.
Be positioned at axle 81 under the situation of scope of θ=90 °～about 95 °; Compressor inlet hole 6a closes, and does not produce torque at compressor 6, but owing to decompressor inlet hole 4a opens; The working fluid of high pressure flows into to the suction side of compressor operating chamber 63 63a, therefore produces torque at compressor 6.
Be positioned at axle 81 under the situation of scope of θ=about 95 °～about 140 °; Because decompressor inlet hole 4a and compressor inlet hole 6a all open; The working fluid of high pressure flows into to the suction side 63a of the suction side of decompressor working room 43 43a and compressor operating chamber 63, therefore produces torque by decompressor 4 and compressor 6.
Be positioned at axle 81 under the situation of scope of θ=about 140 °～360 °; Decompressor inlet hole 4a closes; Do not produce torque at decompressor 4; But because compressor inlet hole 6a opens, the working fluid of high pressure flows into to the suction side of compressor operating chamber 63 63a, therefore produces torque at compressor 6.
Like this, in this mode of execution, when refrigerating circulatory device 1 starting, the pressure through working fluid just can make the fluid machinery 8A self-starting reliably with drive unit, can improve the reliability of refrigerating circulatory device 1.
(other mode of execution)
In said mode of execution, utilize swivel plate 48 to constitute the suction control mechanism that opens and closes decompressor inlet hole 4a along with the rotation of axle 81, but suction control mechanism of the present invention is not limited thereto, can adopt various structures.For example; The suction control mechanism of patent documentation 1 disclosed structure can be adopted, the suction control mechanism of the connectivity slot of the suction side 43a that is communicated with said arc groove and decompressor working room 43 can also be employed on the upper surface of axle 81 the first eccentric part 81b arc groove is set, on the lower surface of first obstruction component 49, be provided with.
Utilizability in the industry
The present invention can realize the self-starting of fluid machinery reliably, and this fluid machinery is being particularly useful as in the refrigerating circulatory device of power recovery system.
Claims (10)
1. fluid machinery, it possesses:
Decompressor, it makes from the working fluid expansion of decompressor inlet hole suction and from the decompressor tap hole and discharges, and reclaims power from working fluid thus;
Compressor, it boosts the working fluid that sucks from the compressor inlet hole and discharges from the compressor tap hole;
Axle, it links said decompressor and said compressor, thereby utilizes the power that is reclaimed by said decompressor to drive said compressor,
Said decompressor inlet hole and said compressor inlet hole open and close along with the rotation of said axle,
Said fluid machinery is maintained in; In said compressor inlet hole closed period; Said decompressor inlet hole is in the state of opening, and in said decompressor inlet hole closed period, said compressor inlet hole is in state of opening and the state that is not communicated with said compressor tap hole.
2. fluid machinery according to claim 1, wherein,
Said axle has second eccentric part that first eccentric part that said decompressor uses and said compressor are used,
Said compressor comprises: and the chimeric compressor piston of said second eccentric part, accommodate said compressor piston the compressor operating cylinder, will be formed on the compressor partition member that compressor operating chamber between said compressor piston and the said compressor operating cylinder is separated into the suction side and discharges side
Said decompressor inlet hole open during in, said compressor piston is through the sliding point that on the inner peripheral surface of said compressor operating cylinder, slides and the consistent top dead center of said compressor partition member of this compressor piston.
3. fluid machinery according to claim 2, wherein,
Said decompressor comprises: the decompressor piston chimeric with said first eccentric part; Accommodate the decompressor clutch release slave cylinder of said decompressor piston; The decompressor working room that is formed between said decompressor piston and the said decompressor clutch release slave cylinder is separated into suction side and the decompressor partition member of discharging side,
The eccentric direction that is made as said second eccentric part in correct time in the sense of rotation with said axle is that the position of β c, said compressor partition member is that the angle of swing of the said axle during β v and said decompressor inlet hole are opened is θ o with respect to the phase difference of the position of said decompressor partition member with respect to the phase difference of the eccentric direction of said first eccentric part; Wherein,-180 °＜β c≤180 °; During-180 °＜β v≤180 °
Satisfy 0.25 θ o≤β v-β c≤0.75 θ o.
4. according to claim 2 or 3 described fluid machineries, wherein,
Said compressor inlet hole is arranged on the said compressor operating cylinder and in the inner peripheral surface upper shed of said compressor operating cylinder,
With after the suction side of said compressor operating chamber is communicated with, said decompressor inlet hole is closed at said compressor inlet hole, and with before said compressor tap hole is communicated with, said decompressor inlet hole is opened in the suction side of said compressor operating chamber.
5. fluid machinery according to claim 4, wherein,
Said compressor comprises that also the pressure of the discharge side of utilizing said compressor operating chamber opens and closes the expulsion valve of said compressor tap hole.
6. according to claim 2 or 3 described fluid machineries, wherein,
Said compressor also comprises: from the inboard obstruction component of the inaccessible said compressor operating of said expander side chamber; From the outside obstruction component of the inaccessible said compressor operating of the opposition side of said decompressor chamber,
Said compressor inlet hole is arranged on said inboard obstruction component or the said outside obstruction component with the mode of only exposing to the suction side of said compressor operating chamber,
With after the suction side of said compressor operating chamber is communicated with, said decompressor inlet hole is closed at said compressor inlet hole, and said decompressor inlet hole is opened before said compressor inlet hole is closed.
7. fluid machinery according to claim 6, wherein,
Said compressor tap hole is only to be arranged on said inboard obstruction component or the said outside obstruction component to the mode that the discharge side of said compressor operating chamber is exposed.
8. fluid machinery according to claim 3, wherein,
Said decompressor also comprises the suction control mechanism that opens and closes said decompressor inlet hole along with the rotation of said axle.
9. fluid machinery according to claim 8, wherein,
Said decompressor also comprises: from the inboard obstruction component of the inaccessible said decompressor of said compressor side working room; From the outside obstruction component of the inaccessible said decompressor of the opposition side of said compressor working room,
Said decompressor inlet hole is arranged on this inboard obstruction component or this outside obstruction component with the mode that connects said inboard obstruction component or said outside obstruction component,
Said suction control mechanism is a swivel plate; This swivel plate is installed on the said axle with the mode that when the face with the said decompressor working room opposition side of said inboard obstruction component or said outside obstruction component joins, is rotated, and the minor diameter part that has the large-diameter portion that blocks said decompressor inlet hole and said decompressor inlet hole is exposed.
10. refrigerating circulatory device, it has used each described fluid machinery in the claim 1～9, and it possesses:
Operating fluid loop; It makes working fluid cycles, comprise compression working fluid main compressor, make the working fluid heat radiation after the compression radiator, make said decompressor that the working fluid that flows out from said radiator expands, make the vaporizer of the working fluid evaporation after the expansion and will boost from the working fluid that said vaporizer flows out and the said compressor supplied with to said main compressor;
Bypass, it is connected the part between the part between the said main compressor in the said operating fluid loop and the said radiator or said radiator and the said decompressor and said vaporizer with part between the said compressor.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010104775 | 2010-04-30 | ||
| JP2010-104775 | 2010-04-30 | ||
| PCT/JP2011/002050 WO2011135779A1 (en) | 2010-04-30 | 2011-04-06 | Fluid machine and refrigeration cycle apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102395759A true CN102395759A (en) | 2012-03-28 |
Family
ID=44861108
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011800017666A Pending CN102395759A (en) | 2010-04-30 | 2011-04-06 | Fluid machine and refrigeration cycle apparatus |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20120131949A1 (en) |
| JP (1) | JPWO2011135779A1 (en) |
| CN (1) | CN102395759A (en) |
| WO (1) | WO2011135779A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104564678A (en) * | 2013-10-28 | 2015-04-29 | 珠海格力节能环保制冷技术研究中心有限公司 | Expansion compressor device and air conditioner comprising same |
| CN105179020A (en) * | 2014-05-26 | 2015-12-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Expanding mechanical air suction control device |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010073586A1 (en) * | 2008-12-22 | 2010-07-01 | パナソニック株式会社 | Refrigeration cycle device |
| CN103967787B (en) * | 2013-01-25 | 2016-02-17 | 北京星旋世纪科技有限公司 | Slewing gear and apply its rotor-type compressor and fluid motor |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5741120A (en) * | 1995-06-07 | 1998-04-21 | Copeland Corporation | Capacity modulated scroll machine |
| CN1726338A (en) * | 2002-12-11 | 2006-01-25 | 大金工业株式会社 | Volume expander and fluid machine |
| US20070154328A1 (en) * | 2003-05-13 | 2007-07-05 | Lg Electronics Inc. | Rotary compressor |
| CN101089395A (en) * | 2006-06-13 | 2007-12-19 | 日立空调·家用电器株式会社 | Cubage type fluid machinery |
| CN101506597A (en) * | 2006-10-25 | 2009-08-12 | 松下电器产业株式会社 | Refrigeration cycle device and fluid machine used for the same |
| JP2009204201A (en) * | 2008-02-27 | 2009-09-10 | Panasonic Corp | Refrigeration cycle device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4976970B2 (en) * | 2007-09-27 | 2012-07-18 | パナソニック株式会社 | Refrigeration cycle equipment |
-
2011
- 2011-04-06 CN CN2011800017666A patent/CN102395759A/en active Pending
- 2011-04-06 US US13/257,485 patent/US20120131949A1/en not_active Abandoned
- 2011-04-06 JP JP2011533471A patent/JPWO2011135779A1/en not_active Withdrawn
- 2011-04-06 WO PCT/JP2011/002050 patent/WO2011135779A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5741120A (en) * | 1995-06-07 | 1998-04-21 | Copeland Corporation | Capacity modulated scroll machine |
| CN1726338A (en) * | 2002-12-11 | 2006-01-25 | 大金工业株式会社 | Volume expander and fluid machine |
| US20070154328A1 (en) * | 2003-05-13 | 2007-07-05 | Lg Electronics Inc. | Rotary compressor |
| CN101089395A (en) * | 2006-06-13 | 2007-12-19 | 日立空调·家用电器株式会社 | Cubage type fluid machinery |
| CN101506597A (en) * | 2006-10-25 | 2009-08-12 | 松下电器产业株式会社 | Refrigeration cycle device and fluid machine used for the same |
| JP2009204201A (en) * | 2008-02-27 | 2009-09-10 | Panasonic Corp | Refrigeration cycle device |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104564678A (en) * | 2013-10-28 | 2015-04-29 | 珠海格力节能环保制冷技术研究中心有限公司 | Expansion compressor device and air conditioner comprising same |
| CN105179020A (en) * | 2014-05-26 | 2015-12-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Expanding mechanical air suction control device |
| CN105179020B (en) * | 2014-05-26 | 2017-11-21 | 珠海格力节能环保制冷技术研究中心有限公司 | Expansion machinery suction control device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2011135779A1 (en) | 2013-07-18 |
| US20120131949A1 (en) | 2012-05-31 |
| WO2011135779A1 (en) | 2011-11-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101680300B (en) | Refrigeration cycle device and fluid machine used therefor | |
| CN101506597B (en) | Refrigeration cycle device and fluid machine used for the same | |
| CN101779039B (en) | Fluid machine and refrigeration cycle device | |
| AU2005268057B2 (en) | Expander | |
| US7896627B2 (en) | Rotary type expander and fluid machinery | |
| AU2005268055B2 (en) | Positive displacement expander and fluid machinery | |
| JP2003139059A (en) | Fluid machine | |
| CN102395759A (en) | Fluid machine and refrigeration cycle apparatus | |
| CN102483276A (en) | Refrigeration cycle apparatus | |
| JP5036593B2 (en) | Refrigeration cycle equipment | |
| CN101680303B (en) | Fluid machine and refrigeration cycle device with the same | |
| WO2004053298A1 (en) | Volume expander and fluid machine | |
| CN102575885A (en) | Refrigeration cycle device | |
| CN105526166B (en) | Compressor and the heat-exchange system with it | |
| JP2004324652A (en) | Rotary compressor | |
| JP2004197640A (en) | Positive displacement expander and fluid machinery | |
| CN102037217B (en) | Fluid machine and refrigeration cycle device | |
| EP2527591B1 (en) | Positive displacement expander and refrigeration cycle device using the positive displacement expander | |
| JP2006132377A (en) | Fluid machine | |
| JP2005106064A (en) | Rotary expander | |
| JP4626635B2 (en) | Fluid machinery | |
| WO2012104934A1 (en) | Scroll expander, and refrigeration cycle with the scroll expander | |
| JP2007170290A (en) | Scroll type expander and rankine cycle power generation system | |
| JP2006118438A (en) | Rotary expansion machine | |
| JP2004360611A (en) | Displacement-type machine and freezer in which the machine is used |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20120328 |