EP1748191B1 - Kompressionseinheit und damit versehene thermische Anlage - Google Patents

Kompressionseinheit und damit versehene thermische Anlage Download PDF

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Publication number
EP1748191B1
EP1748191B1 EP06015308A EP06015308A EP1748191B1 EP 1748191 B1 EP1748191 B1 EP 1748191B1 EP 06015308 A EP06015308 A EP 06015308A EP 06015308 A EP06015308 A EP 06015308A EP 1748191 B1 EP1748191 B1 EP 1748191B1
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EP
European Patent Office
Prior art keywords
way
valve
compressor
compression unit
pipe
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Not-in-force
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EP06015308A
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English (en)
French (fr)
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EP1748191A1 (de
Inventor
Patrice Saillard
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Individual
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Individual
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02743—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using three four-way 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/002—Machines, plants or systems, using particular sources of energy using solar energy
    • F25B27/005—Machines, plants or systems, using particular sources of energy using solar energy in compression type systems

Definitions

  • the present invention relates to a compression unit adapted to compress a heat transfer fluid phase change.
  • Such a compression unit of the type which comprises a low pressure inlet, a high pressure outlet, two compressors, a nonreturn valve and a four-way operating valve.
  • a first channel of the valve is connected to the common pipe for the parallel supply of compressors
  • a second channel which can not be put into communication with the first channel, is connected the output of the second compressor
  • the third and fourth channels which can not be connected to each other, are connected to the inlet at the outlet of the unit, the non-return valve being arranged in the supply line proper to the second compressor, the driving of output of the first compressor opening into the supply line of the second compressor, downstream of the valve.
  • This compression unit has the following two major disadvantages when the two compressors are in single stage: on the one hand, the output of the first compressor opening into the inlet of the second compressor, only the latter can operate, resulting in use only the compression potential of the unit, and, on the other hand, the non-return valve being arranged in the supply line of the second compressor, it is crossed by the fluid at low pressure, which causes a significant pressure drop.
  • the present invention aims to provide a compression unit that can be used in single or double stage, and which is configured to limit the pressure losses associated with the passage of the non-return valve, and to allow use of the entire its compression potential when it works in single storey.
  • the operating valve has a first channel which is connected (preferably directly) to the output of a first compressor whose input is connected (preferably directly) at the low pressure inlet, a second channel which can not be connected to the first channel and which is connected (preferably directly) to the low pressure inlet, a third channel which is connected (preferably directly) to the the inlet of the second compressor, the output of which is connected (preferably directly) to the high-pressure outlet, and a fourth channel which can not be put in communication with the third channel and which is connected (preferably directly) to the input of the valve whose output is connected (preferably directly) to the high pressure outlet.
  • the unit when the first channel of the valve, connected to the output of the first compressor, is in communication with the third channel, connected to the input of the second compressor, the unit operates in two stages, and no fluid passes through the check valve because its output, connected to the output of the unit, is in high pressure while its input, connected to the input of the unit by placing in communication the second and fourth channels of the valve, is in low pressure.
  • the output of the first compressor is connected to the high pressure outlet of the unit through the valve and the valve which is traversed by the fluid at high pressure. Therefore, in this configuration, the unit is not only single stage, but in addition, the two compressors are mounted entirely in parallel, which allows either to use only the first, or the second, or the two. In addition, the check valve being traversed by the fluid at high pressure, the pressure losses are less important.
  • the low pressure inlet is connected to the second channel of the operating valve via an additional non-return valve which allows circulation of the heat transfer fluid only in the direction of the low pressure input to the second channel.
  • the present invention aims to provide a thermal installation in which circulates a phase change heat transfer fluid for rejecting heat to a first site of the external environment, and to absorb at a second site.
  • the thermal installation comprises two heat exchangers, a compression unit and a four-way production valve, a first channel of which is connected (preferably directly) to a first exchanger, a second channel which can not be placed in communication with the first channel, is connected (preferably directly) to the second heat exchanger, a third channel is connected (preferably directly) to the low pressure inlet of the compression unit, and a fourth way which does not can be connected to the third channel, is connected (preferably directly) to the high pressure outlet of the compression unit.
  • the thermal installation comprises another heat exchanger which is connected (preferably directly) to the pipe connecting the third channel of the production valve to the low pressure inlet of the compression unit.
  • the thermal installation comprises, on the one hand, a compression unit having at least two compressors capable of operating in two stages, and, on the other hand, another heat exchanger which is connected (preferably directly) an internal pipe to the compression unit may be at the intermediate pressure.
  • the thermal installation comprises a four-way bypass valve of which a first channel is connected (preferably directly) to the high pressure outlet of the compression unit, of which a second channel which can not be communication with the first channel, is connected (preferably directly) to the line connecting the low pressure inlet of the compression unit to the third channel of the production valve, a third channel of which is connected (preferably directly ) at the fourth channel of the production valve, and whose fourth channel which can not be placed in communication with the third channel, is connected (preferably directly) to another heat exchanger.
  • the thermal installation comprises another heat exchanger that can act as a heat pipe (preferably a solar collector) which is connected to the high pressure outlet of the compression unit so as to supply a heat exchanger acting as a condenser connected to the production valve, and possibly to the bypass valve.
  • a heat pipe preferably a solar collector
  • FIGS. 1 to 4 relating to a first aspect of the present invention which relates to a unit of compression 1 adapted to compress a heat transfer fluid phase change in different modes of operation.
  • the compression unit 1 comprises a low pressure inlet 2, a high pressure outlet 3, a first compressor 4, a second compressor 5, a non-return valve 6 and a four-way operating valve 7 which can take two states.
  • the low pressure inlet 2 is connected, via a first pipe 8, to the inlet 9 of the first compressor 4.
  • the outlet 10 of this first compressor 4 is connected by a second pipe 11 to a first channel 12 of the valve 7.
  • the low pressure inlet 2 is also connected, by a third pipe 13, to a second channel 14 of the operating valve 7 which can not be placed in communication with the first channel 12.
  • the high-pressure outlet 3 is connected, by a fourth pipe 15, to the outlet 16 of the second compressor 5.
  • the inlet 17 of this second compressor 5 is connected by a fifth pipe 18 to a third channel 19 of the 7.
  • the high pressure outlet 3 is also connected, via a sixth pipe 20, to the fourth channel 21 of the operating valve 7 which can not be placed in communication with the third channel 19.
  • the sixth pipe 20 comprises the non-return valve 6 which is oriented so that the heat transfer fluid can circulate only in the direction of the fourth channel 21 to the high pressure outlet 3.
  • the first channel 12 of the operating valve 7 is connected directly to the outlet 10 of the first compressor 4 whose input 9 is connected directly to the low pressure inlet 2
  • the second channel 14 is connected directly to the low pressure inlet 2
  • the third channel 19 is connected directly to the inlet 17 of the second compressor 5 whose output 16 is directly connected to the high pressure outlet 3
  • the fourth channel 21 is connected directly to the non-return valve 6 which is connected directly to the high-pressure outlet 3.
  • the operating valve 7 When the operating valve 7 is in its first state, its first channel 12 is in communication with its third channel 19, and its second channel 14 is in communication with its fourth channel 21.
  • the output 10 of the first compressor 4 is connected at the inlet 17 of the second compressor 5 by the second 11 and fifth 18 conduits which are at an intermediate pressure.
  • the non-return valve 6 prohibits the circulation of heat transfer fluid between the high pressure outlet 3 and the low pressure inlet 2 yet connected by the sixth 20 and third 13 conduits.
  • the compression unit 1 can thus operate in two stages ( figure 1 ).
  • the operating valve 7 When the operating valve 7 is in its second state, its first channel 12 is in communication with its fourth channel 21, and its second channel 14 is in communication with its third channel 19.
  • the input 9 of the first compressor 4, by the first pipe 8, and the inlet 17 of the second compressor 5, by the third 13 and fifth 18 conduits are connected to the low pressure inlet 2, and, secondly, the outlet 10 of the first compressor 4, the second 11 and sixth 20 ducts, and the outlet 16 of the second compressor 5, by the fourth pipe 15, are connected to the high-pressure outlet 3.
  • the compression unit 1 can thus operate in a single stage ( Figures 2 to 4 ).
  • the compression unit 1 is shaped so that the second compressor 5 is supplied with lubricating oil only by the first compressor 4 which receives the assembly. oil from the compression unit 1.
  • the third pipe 13 which connects the inlet 17 of the second compressor 5 to the low pressure inlet 2 when the second 14 and third 19 tracks of the operating valve 7 are in communication, is shaped to form a siphon 22.
  • the compression unit 1 comprises an oil balancing pipe 23 which connects the casings of the two compressors 4,5.
  • the balancing pipe 23 comprises an obstruction device 24 allowing its selective closure depending on the pressure difference prevailing in the casings.
  • the balancing pipe 23 comprises a first section 25 which connects the casing of the first compressor 4 at the inlet 26 of the obstruction device 24, and a second section 27 which connects the outlet 28 of the obstruction device 24 to the casing of the second compressor 5.
  • the tapping of the first section 27 to the casing of the first compressor 4 is made at a height defining the maximum level of oil in this case, the balancing line 23 allowing the excess oil in the casing of the first compressor 4 to lubricate the second compressor 5.
  • the obstruction device 24 is shaped so that, when the pressure in the casing of the first compressor 4 is lower than that in the casing of the second compressor 5, it is in a closed state in which the balancing pipe 23 is closed, and when the pressure in the housing of the first compressor 4 is greater than or equal to that in the housing of the second compressor 5, it is in an open state in which the balancing pipe 23 is open.
  • the obstruction device 24 comprises an enclosure 29 in which the two sections 25, 27 of the balancing line 23 open.
  • the obstruction device also comprises a shutter 30 which is movable in the enclosure 29 under the effect of the flow of the oil circulating in the chamber 29 generated by the relative pressures of the housings of the two compressors 4,5.
  • the shutter 30 is formed by a flap 30 which is slidably mounted in the enclosure 29.
  • the shutter 30 is arranged with respect to the input 26 and the output 28 of the device 24, so that, firstly, when the pressure in the casing of the first compressor 4 is less than that in the casing of the second compressor 5, it is in a closed position in which it completely obstructs the inlet 26 of the obstruction device 24 which prevents any flow of oil to the casing of the second compressor 5 via the balancing line 23, secondly, when the pressure in the casing of the first compressor 4 is equal to that prevailing in the housing of the second compressor 5, it is in a first open position in which it is remote from the inlet 26 and the outlet 28 of the obstruction device 24 which allows the flow of the oil to the housing of the second compressor 5, and, thirdly, when the pressure in the housing of the first compressor 4 is greater than that in the housing of the second compressor 5, it is in a the open position in which it partially obstructs the outlet 28 of the blocking device 24 which also allows the flow of oil to the casing of the second compressor 5.
  • the outlet 28 of the device 24 includes
  • the compression unit 1 When the operating valve 7 is in its first state, the compression unit 1 operating in two stages, as can be seen in FIG. figure 1 , the crankcase pressure of the second compressor 5 is greater than that prevailing in the casing of the first compressor 4, which causes the closing of the balancing line 23, the oil supply of the second compressor 5 then being through the first 12 and third 19 conducted via the operating valve 7, the lubricant being driven by the coolant.
  • the compression unit 1 When the operating valve 7 is in its second state, the compression unit 1 operating in single stage using the two compressors 4,5, as can be seen in FIG. figure 1 , the pressure balance of the housings causes the shutter 30 in its first open position, which allows the supply of the second compressor 5 in oil.
  • the first compressor 4 When the compression unit 1 operates in single stage, the first compressor 4 is stopped, as can be seen at the figure 2 , the overpressure of the casing of the first compressor 4 relative to the casing of the second compressor 5 drives the shutter 30 in its second open position, which also allows the supply of the second compressor 5 in oil.
  • the second compressor 5 When the compression unit 1 operates in a single stage, the second compressor 5 is stopped, as can be seen in FIG. figure 3 , the overpressure of the casing of the second compressor 5 relative to the casing of the first compressor 4 causes the shutter 30 in its position closing, which prevents the supply of the second compressor 5 in oil.
  • This configuration of the compression unit 1 makes it possible to be able to modulate the compression power of the compression unit 1 when it operates in a single stage, and this especially as the number of compression chambers in parallel of each compressor is important.
  • a first compressor 4 comprising two compression chambers 32,33 in parallel
  • a second compressor 5 with a single compression chamber 34, it is possible to be able to deliver seven different compression powers.
  • the power ratio of the three compression chambers 32, 33, 34 it is possible to have a constant difference between the seven powers: if the first chamber 32 of the first compressor 4, the second chamber 33 of the first compressor 4 , and the chamber 34 of the second compressor 35 representing, respectively, 1/7, 2/7 and 4/7 of the total power of the three chambers 32,33,34, it is possible to use 14% (only the first chamber 32 of the first compressor 4 operates), 29% (only the second chamber 33 of the first compressor 4 operates), 43% (only the two chambers 32,33 of the first compressor 4 operate), 57% (only the second compressor 5 operates) , 71% (only the first chamber 32 of the first compressor 4 and the second compressor 5 operate), 86% (only the second chamber 33 of the first compressor 4 and the second compressor 5 operate) and 100% (the three chambers 32,33 , 34 of the compression unit 1 operate) of the total power of the compression unit 1.
  • the compression unit 1 according to the present invention makes it possible to achieve particularly flexible and economical thermal installations.
  • FIGS. 5 to 12 relating to a second aspect of the present invention which relates to a modular thermal installation comprising a compression unit 1 which may be of the type corresponding to the first aspect of the present invention.
  • the figure 5 shows a first thermal installation which comprises a compression unit 1 according to the first embodiment, a four-way production valve 35 which can take two states, a first heat exchanger 36 and a second heat exchanger 37.
  • the two heat exchangers 36, 37 are shaped so as to be able, on the one hand, to reject heat towards the external environment and, on the other hand, to absorb it.
  • the constituent elements of the first thermal installation are arranged relative to each other so that when one of the two heat exchangers 36,37 acts as a condenser, the other acts as an evaporator, the choice of the heat exchanger acting as an evaporator depending on the state of the production valve 35.
  • a first channel 38 of the production valve 35 is connected, by a seventh line 39, to a first end 40 of the first heat exchanger 36.
  • a second channel 41 of the production valve 35 which can not be put into communication with the first channel 38, is connected by an eighth line 42 to a first end 43 of the second heat exchanger 37.
  • a third channel 44 of the production valve 35 is connected by a ninth line 45 to the low pressure inlet 2 of the compression unit 1.
  • the fourth channel 46 of the production valve 35 which can not be placed in communication with the third channel 44, is connected, by a tenth line 47, to the high pressure outlet 3 of the compression unit 1.
  • the first channel 38 of the production valve 35 is connected directly to the first heat exchanger 36
  • the second channel 41 of the production valve 35 is connected directly to the second heat exchanger 37
  • the third channel 44 of the production valve 35 is connected directly to the low pressure inlet 2 of the compression unit 1
  • the fourth channel 46 of the production valve 35 is connected directly to the high pressure outlet 3 of the compression unit.
  • the second end 48 of the first heat exchanger 36 is connected to the second end 49 of the second heat exchanger 37 by an expansion network 50 which is configured so that, when one of the two heat exchangers 36, 37, rejects heat, the other 37.36 absorbs it.
  • the expansion network 50 comprises a common trunk 51 having a first end 52, a second end 53 and a reservoir 54 of heat transfer fluid located between the first 52 and second 53 ends of the common trunk 51.
  • the expansion network 50 also comprises a first pipe 55 which connects the second end 48 of the first heat exchanger 36 to the first end 52 of the common trunk 51, and which comprises a first non-return valve 56 oriented so that the heat transfer fluid can circulate in this first pipe 55 that in the direction of the second end 48 of the first heat exchanger 36 to the first end 52 of the common section 51.
  • the expansion network 50 further comprises a second pipe 57 which connects the second end 49 of the second heat exchanger 37 to the first end 52 of the common trunk 51, and which comprises a second non-return valve 58 oriented so that the heat transfer fluid can flow in this second pipe 57 only in the direction of the second end 49 of the second heat exchanger 37 to the first end 52 of the common core 51.
  • the expansion network 50 also includes a third canalis ation 59 which connects the second end 48 of the first heat exchanger 36 to the second end 53 of the common section 51, and which comprises a first two-way valve 60 and a first expander 61 disposed between the second end 48 of the first heat exchanger 37 and. the first valve 60.
  • the expansion network 50 finally comprises a fourth pipe 62 which connects the second end 49 of the second heat exchanger 37 to the second end 53 of the common trunk 51, and which comprises a second two-way valve 63 and a second expander 64 disposed between the second end 49 of the second heat exchanger 37 and the second valve 63.
  • the functionalities of the first thermal installation are independent of the operating mode of the compression unit 1.
  • the compressed vapor phase heat transfer fluid from the high pressure outlet 3 of the compression unit 1 is sent, via the production valve 35, into the two heat exchangers 36,37 where it condenses and releases heat to the outside environment.
  • the production valve 35 is in its first state in which its fourth channel 46 is in communication with its first channel 38, the heat transfer fluid is sent to the first heat exchanger 36 by the tenths 47 and seventh 39 ducts, and when it is in its second state in which its fourth channel 46 is in communication with its second channel 41, the heat transfer fluid is sent to the second heat exchanger 37 by the tenth 47 and eighth 42 conduits.
  • the coolant in the liquid phase enters the expansion network 50 where it undergoes expansion before being introduced into the other heat exchanger where it evaporates and absorbs heat. heat from the outside environment.
  • the production valve 35 When the production valve 35 is in its first state, the coolant, at the outlet of the first heat exchanger 36, passes successively through the first pipe 55 (including the first non-return valve 56), the common trunk 51, the fourth line 62 (including the second valve 63 and the second expander 64) and the second heat exchanger 37, the second non-return valve 58 preventing the fluid from passing through the second pipe 57.
  • the coolant at the outlet of the second heat exchanger 37, successively passes through the second pipe 57 (including the second non-return valve 58), the common trunk 51, the third pipe 59 (including the first valve 60 and the first expansion valve 61) and the first heat exchanger 36, the first non-return valve 56 preventing the fluid from passing through the first pipe 55.
  • the vapor-phase heat transfer fluid is sent into the low-pressure inlet 2 of the compression unit 1 via the production valve 35.
  • the production valve 35 When the production valve 35 is in its first state, the coolant passes through the eighth 42 and ninth 45 pipes, and when it is in its second state, the heat transfer fluid passes through the seventh 39 and ninth 45 pipes.
  • this first thermal installation comprises an economizer 65 which comprises a first element 66, a first end 67 of which is connected to the fifth conduit 18 of the compression unit 1 which is at the intermediate pressure when the compression unit 1 operates in two stages.
  • the first end 67 of the first element 66 of the economizer 65 is connected directly to the fifth pipe 18 of the compression unit 1.
  • the second end 68 of the first element 66 is connected to the expansion network 50, in this case, by a fifth pipe 69 which comprises a third two-way valve 70 and a third expander 71 disposed between the first element 66 of the economizer 65 and the third valve 69.
  • the fifth channel 69 opens into the common section 51, a portion 72 forms the second element 72 of the economizer 65.
  • the figure 6 shows a second thermal installation which comprises, in addition to the elements of the first installation, a third heat exchanger 73.
  • the third heat exchanger 73 is arranged relative to the other elements so as to act as an evaporator when one of the first two exchangers thermal 36,37 serves as a condenser (whatever the two heat exchangers 36,37 which fulfills this office condenser), the other of the first two heat exchangers 36,37 is turned off or act as an evaporator.
  • the boiling temperature in the two heat exchangers acting as evaporator is the same and it corresponds to the low pressure of the compression unit 1.
  • a first end 74 of the third heat exchanger 73 is connected by an eleventh conduct 75 to the ninth conduit 45 which connects the low input pressure 2 of the compression unit 1 to the third channel 44 of the production valve 35.
  • the first end 74 of the third heat exchanger 73 is connected directly to the ninth pipe 45.
  • a sixth pipe 77 which connects the second end 76 of the third heat exchanger 73 to the common section 51, comprises a fourth two-way valve 78 and a fourth expansion valve 79 disposed between the third heat exchanger 73 and the fourth valve 78.
  • the third 59, fourth 62 and sixth 77 pipes are mounted equivalently with respect to the common trunk 51.
  • the heat transfer fluid from the common trunk 51 may, depending on the state of the fourth valve 78, successively crossing the sixth pipe 77 (including the fourth valve 78 and the fourth expansion valve 79) and the third heat exchanger 73 before being sent, in the form of steam, into the low pressure inlet 2 of the pressure unit compression 1 via the eleventh 75 and ninth 45 conduits.
  • the figure 7 shows a third thermal installation which comprises, in addition to the elements of the second installation, a fourth heat exchanger 80.
  • the fourth heat exchanger 80 is arranged with respect to the other elements so as to act as an evaporator when one of the first two heat exchangers 36,37 acts as a condenser (whatever the two heat exchangers 36,37 which fulfills this function of condenser), that the other of the first two heat exchangers 36, 37 is switched off or acts as an evaporator, whether the third heat exchanger 73 is switched off or serves as an evaporator.
  • the boiling temperature of the fourth heat exchanger 80 corresponds to the pressure prevailing at the inlet 17 of the second compressor 5 and can, therefore, be greater than that of other heat exchangers acting as evaporator.
  • a first end 81 of the fourth heat exchanger 80 is connected by a twelfth line 82 to the fifth line 18 of the compression unit 1 which connects the inlet 17 of the second compressor 5 to the third channel 19 of the operating valve. 7 so as to be at the pressure prevailing at the inlet 17 of the second compressor 5 (for example, at the pressure of the intermediate when the compression unit 1 operates in two stages).
  • the first end 81 of the fourth heat exchanger 80 is connected directly to the fifth pipe 18.
  • the second end 83 of the fourth heat exchanger 80 is connected to the expansion network 50.
  • a seventh pipe 84 which connects the second end 83 of the fourth heat exchanger 80 to the common trunk 51 comprises a fifth valve two. 85 and a fifth expansion valve 86 disposed between the fourth heat exchanger 80 and the fifth valve 86.
  • the third 59, fourth 62, sixth 77 and seventh 84 pipes are mounted equivalently with respect to the common section 51.
  • the coolant from the common core 51 may, depending on the state of the fifth valve 85 , successively passing the seventh pipe 84 (including the fifth valve 85 and the fifth expander 86) and the fourth heat exchanger 80 before being sent, in the form of steam, into the inlet 17 of the second compressor 5 via the twelfth 82 and fifth 18 conduits.
  • the existence of the intermediate pressure thus makes it possible to have a boiling point of the fourth heat exchanger 80 higher than that in the other exchangers acting as an evaporator.
  • the present third thermal installation comprises a compression unit 1 according to a second embodiment.
  • the low pressure inlet 2 is connected to the second channel 14 of the operating valve 7, not directly, but via a non-return valve additional 87 which is oriented so that the heat transfer fluid can circulate only in the direction of the low pressure inlet 2 to the second channel 14 of the operating valve 7.
  • the additional check valve 87 thus prevents the flow of fluid coolant of the second channel 14 to the inlet 9 of the first compressor 4, and therefore, when the operating valve 7 is in its second state, it prevents the circulation of the coolant from the inlet 17 of the second compressor 5 to the input 9 of the first compressor 4.
  • the first compressor 4 can be supplied with low pressure heat transfer fluid from the low pressure inlet 2 while the second compresses ur 5 is supplied with intermediate pressure heat transfer fluid from the fourth heat exchanger 80, the two compressors 4,5 producing a heat transfer fluid at high pressure supplying the high pressure outlet 3.
  • the additional non-return valve 87 is directly connected, on the one hand, to the low pressure inlet 2 of the compression unit 1, in parallel with the inlet 9 of the first compressor 4, and secondly, to the second channel 14 of the operating valve 7.
  • the figure 9 shows a fourth thermal installation which comprises, in addition to the elements of the third installation, a four-way bypass valve 88 and a fifth heat exchanger 89.
  • the fifth heat exchanger 89 and the bypass valve 88 are arranged relative to the other elements so as to according to the state of the bypass valve 88, the fifth heat exchanger 89 is disconnected and the four other heat exchangers 36, 37, 73, 80 have the same functionalities as in the third thermal installation, either it acts as a condenser and the first four heat exchangers 36,37,73,80 can act as an evaporator independently of each other, the fourth heat exchanger 80 retaining its functionality to be able to have a higher boiling temperature than other heat exchangers acting as evaporators 36,37,73.
  • the high pressure outlet 3 of the compression unit 1 is connected to the fourth channel 46 of the production valve 35 via the bypass valve 88.
  • a first channel 90 of the bypass valve 88 is connected by a thirteenth pipe 91, at the high pressure outlet 3 of the compression unit 1.
  • a second channel 92 of the bypass valve 88 which can not be put in communication with the first channel 90 is connected by a fourteenth pipe 93 , at the ninth conduit 45 which connects the low pressure inlet 2 of the compression unit 1 to the third channel 44 of the production valve 35.
  • a third channel 94 of the valve The bypass 88 is connected by a fifteenth pipe 95 to the fourth channel 46 of the production valve 35.
  • the fourth channel 96 of the bypass valve 88 which can not be put into communication with the third channel 94 is connected by a sixteenth pipe 97 at a first end 98 of the fifth heat exchanger 89.
  • the first channel 90 of the bypass valve 88 is connected directly to the high pressure outlet 3
  • the second channel 92 of the bypass valve 88 is connected directly to the ninth line 45
  • the third channel 94 of the Bypass valve 88 is connected directly to the fourth channel 46 of the production valve 35
  • the fourth channel 96 of the bypass valve 88 is connected directly to the first end 98 of the fifth heat exchanger 89.
  • the second end 99 of the fifth heat exchanger 89 is connected to the expansion network 50.
  • An eighth duct 100 which connects the second end 99 of the fourth thermal fifth 89 to the common trunk 51 comprises a third nonreturn valve 101 oriented so that the heat transfer fluid can flow in this eighth pipe 100 only in the direction of the second end 99 of the fifth heat exchanger 89 to the common trunk 51.
  • the first 55, second 57 and eighth 100 pipes are mounted equivalently compared to the common core 51.
  • the bypass valve 88 when the bypass valve 88 is in its first state in which its first channel 90 is in communication with its third channel 94, the vapor-phase heat transfer fluid from the 3 high pressure outlet of the compression unit 1 is sent via the bypass valve 88 to the production valve 35, then depending on the state of the production valve 35 in one or the another of the first two heat exchangers 36,37 acting as a condenser, the subsequent circuit corresponding to that in the third installation. Furthermore, the third non-return valve 101 prevents the fluid from passing through the eighth pipe 101 and the fifth heat exchanger 89 which is connected with the low pressure inlet 2 of the compression unit 3 via the sixteenth 97 and fourteenth 93 pipes.
  • the bypass valve 88 when the bypass valve 88 is in its second state in which its first channel 90 is in communication with its fourth channel 96, the vapor-phase heat transfer fluid from the High pressure outlet 3 of the compression unit 1 is sent via the bypass valve 88 to the fifth heat exchanger 89 acting as a condenser.
  • the coolant in the liquid phase passes successively through the eighth duct 100 (including the third non-return valve 101) and the common trunk 51.
  • Dela according to the state first 60, second 63, fourth 78 and fifth 85 valves, it is sent into at least one of the first four heat exchangers 36,37,73,80 as an evaporator.
  • the heat transfer fluid finally joins either the low pressure inlet 2 of the compression unit 1 if it comes from the first 36, second 37 or third 73 heat exchanger, or the inlet 17 of the second compressor 5 if it comes from the fourth heat exchanger 80.
  • the figure 11 shows a fifth thermal installation which comprises, in addition to the elements of the fourth installation, and a sixth heat exchanger 102 formed by solar collector 102.
  • the solar collector 102 is arranged relative to the other elements so that, whatever the state production and bypass valves 88, when it is not switched off, the solar collector 102, depending on the state of the operating valve 7, either acts as an evaporator or serves as a heat pipe supplying heat transfer fluid, according to the state of the production valves 35 and bypass 88, the first 36, second 37 or fifth 89 heat exchanger which acts as a condenser.
  • a first end 103 of the solar collector 102 is connected by a seventeenth line 104 to the third line 13 of the compression unit 1 which connects the low pressure inlet 2 of the compression unit 1 to the second channel 14 of the operating valve 7.
  • the seventeenth pipe 104 comprises a complementary non-return valve 105 which is oriented so that the coolant can not only flow in the direction of the first end 103 of the solar collector 102 to the second channel 14 of the operating valve 7.
  • the seventeenth pipe 104 opens into the third pipe 13 after the outlet of the additional non-return valve 87.
  • the first end 103 of the solar collector 102 is connected to the inlet 17 of the second compressor 5 via the seventeenth 104, third 13 and fifth 18 conduits.
  • the solar collector 102 can act as an evaporator.
  • the boiling point of the solar collector 102 like that of the fourth heat exchanger 80, corresponds to the pressure prevailing at the inlet 17 of the second compressor 5 and can therefore be greater than that of the other heat exchangers serving as 'evaporator.
  • the sixth heat exchanger 102 because it is a solar collector, allows evaporation of the coolant even when the temperature of the external medium is lower than the boiling temperature corresponding to the prevailing pressure.
  • the first end 103 of the solar collector 102 is connected to the high-pressure outlet 3 of the compression unit 1 via the seventeenth 104, third 13 and sixth 20 pipes.
  • the solar collector 102 can act as a heat pipe.
  • the first end 103 of the solar collector 102 is connected directly to the inlet of the complementary non-return valve 105 whose output is connected directly to the third pipe 13.
  • the second end 106 of the solar collector 102 is connected to the expansion network 50.
  • a ninth pipe 107 which connects the second end 106 of the solar collector 102 to the common trunk 51 comprises a sixth two-way valve 108 and a sixth expansion valve 109 disposed between the solar collector 102 and the sixth valve 108.
  • a tenth duct 110 which also connects the second end 106 of the solar collector 102 to the common trunk 51 comprises a seventh two-way valve 111.
  • the third 59, fourth 62, sixth 77, seventh 84, ninth 107 and tenth 110 pipes are mounted equivalently with respect to the common trunk 51.
  • the heat transfer fluid from the common trunk 51 may, depending on the state of the sixth valve 108, successively cross the ninth pipe 107 (including the sixth valve 108 and the sixth expansion valve 109) and the solar collector 102 before being sent, in the form of steam, into the inlet 17 of the second compressor 5.
  • the presence of the additional check valve 87 makes it possible to have a boiling temperature different from that of the other heat exchangers acting as an evaporator.
  • the solar collector 102 When the operating valve 7 is in its first state, it is possible to fill the solar collector 102 with heat transfer fluid in liquid form at high pressure by using the compression unit 1 as drive means, the fluid having passed through the trunk common 51 then the tenth line 110 (including the seventh valve 111) without undergoing expansion.
  • the solar collector 102 can act as a heat pipe, the thermal radiation evaporating the coolant which is then directed to the high pressure outlet 3 of the compression unit 1 by short-circuiting the two compressors 4,5, then, depending on the state of the production and bypass valves 88, either in the first 36, second 37 or fifth 89 heat exchanger which acts as a condenser.
  • the compression unit 1 can be restarted to fill it again.
  • the present invention both in its first aspect (structure of the compression unit) and in its second aspect (structure of the thermal installation), is not limited to the embodiments given by way of examples in the present invention. description.
  • the shutter is formed by an oscillating flap, a floating ball or a rising ball driven from one to the other of their position by the oil flow.

Claims (14)

  1. Wärmeanlage mit einer Kompressionseinheit (1), welche ein Wärmeübertragungsfluid unter Veränderung der Phase komprimieren kann und welche aufweist einen Niederdruckeingang (2), einen Hochdruckausgang (3) und zwei Kompressoren (4, 5), wobei die Wärmeanlage aufweist ein Produktionsventil (35) mit vier Wegen und zwei Wärmetauscher (36, 37), wobei das Produktionsventil (25) auf weist einen ersten Weg (38), der mit einem ersten Ende (40) eines ersten Tauschers (36) verbunden ist, einen zweiten Weg (41), der nicht in Kommunikation mit dem ersten Weg (38) gebracht werden kann und der mit dem ersten Ende (43) des zweiten Tauschers (37) verbunden ist, einen dritten Weg (44), der mit dem Niederdruckeingang (2) der Kompressionseinheit (1) verbunden ist, und einen vierten Weg (46), der nicht mit dem dritten Weg (44) in Kommunikation gebracht werden kann und der mit dem Hochdruckausgang (3) der Kompressionseinheit (1) verbunden ist, wobei das zweite Ende (48) des ersten Tauschers (36) mit dem zweiten Ende (49) des zweiten Tauschers (37) durch ein Entspannungsnetz (50) verbunden ist, dadurch gekennzeichnet, dass die Kompressionseinheit (1) aufweist eine Rückschlagklappe (6) und ein Funktionsventil (7) mit vier Wegen, wobei das Funktionsventil (7) aufweist einen ersten Weg (12), der mit dem Ausgang (10) eines ersten Kompressors (4) verbunden ist, dessen Eingang (9) mit dem Niederdruckeingang (2) verbunden ist, einen zweiten Weg (14), der nicht mit dem ersten Weg (12) in Kommunikation gebracht werden kann und der mit dem Niederdruckeingang (2) verbunden ist, einen dritten Weg (19), der mit dem Eingang (17) des zweiten Kompressors (5) verbunden ist, dessen Ausgang (16) mit dem Hochdruckausgang (3) verbunden ist, und einen vierten Weg (21), der nicht mit dem dritten Weg (19) in Kommunikation gebracht werden kann und der mit dem Eingang der Klappe (6) verbunden ist, deren Ausgang mit dem Hochdruckausgang (3) verbunden ist.
  2. Wärmeanlage nach Anspruch 1, dadurch gekennzeichnet, dass der Niederdruckeingang (2) mit dem zweiten Weg (14) des Funktionsventils (7) mittels einer zusätzlichen Rückschlagklappe (87) verbunden ist, welche nur eine Zirkulation des Wärmeübertragungsfluids vom Niederdruckeingang (2) in Richtung des zweiten Weges (14) erlaubt.
  3. Wärmeanlage nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Ölversorgung des zweiten Kompressors (5) durch den ersten Kompressor (4) erfolgt, der die Gesamtmenge des Öls erhält, welche die Kompressionseinheit (1) versorgt, und dass die Ölversorgung des zweiten Kompressors (5) erfolgt, wenn der erste Weg (12) des Funktionsventils (7) in Kommunikation mit dem dritten Weg (19) steht, und zwar durch eine Leitung (11, 18), die durch das Wärmeübertragungsfluid, welches das Schmiermittel mitnimmt, benutzt wird, und wenn der erste Weg (12) durch eine Öl-Ausgleichsleitung (23) in Kommunikation mit dem vierten Weg (21) steht.
  4. Wärmeanlage nach Anspruch 3, dadurch gekennzeichnet, dass die Ausgleichsleitung (23) die Wannen der zwei Kompressoren (4, 5) verbindet und aufweist eine Sperreinrichtung (4), die so ausgebildet ist, dass diese, wenn der in der Wanne des ersten Kompressors (4) herrschende Druck niedriger als derjenige ist, der in dem zweiten Kompressor (5) herrscht, die Ausgleichsleitung (23) schließt, und, wenn dieser höher oder gleich desjenigen ist, der in der Wanne des zweiten Kompressors (5) herrscht, diese Leitung (23) offen lässt.
  5. Wärmeanlage nach Anspruch 4, dadurch gekennzeichnet, dass die Sperreinrichtung (24) einen Verschluss (30) umfasst, der unter dem Druckunterschied zwischen den beiden Wannen beweglich ist, zwischen erstens einer ersten Öffnungsposition, welche den Öldurchgang in die Ausgleichsleitung (23) ermöglicht, wenn die in den Wannen der beiden Kompressoren (4, 5) herrschenden Drucke gleich sind, zweitens einer Schließposition, welche die Ausgleichsleitung (23) vollständig schließt und den Öldurchgang verhindert, wenn der in der Wanne des ersten Kompressors (4) herrschende Druck unter demjenigen liegt, der in derjenigen des zweiten Kompressors (5) herrscht, und drittens einer zweiten Öffnungsposition, welche die Ausgleichsleitung (23) teilweise schließt und den Öldurchgang ermöglicht, wenn der in der Wanne des ersten Kompressors (4) herrschende Druck höher ist als derjenige, der in derjenigen des zweiten Kompressors (5) herrscht.
  6. Wärmeanlage nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass diese einen dritten Wärmetauscher (73) umfasst, von dem ein erstes Ende (74) mit der Leitung (45) verbunden ist, welche den dritten Weg (44) des Produktionsventils (35) mit dem Niederdruckeingang (2) verbindet, und von dem das zweite Ende (76) mit dem Entspannungsnetz (50) verbunden ist.
  7. Wärmeanlage einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass diese einen dritten Wärmetauscher (80) umfasst, von dem das erste Ende (81) mit der Leitung (18) verbunden ist, welche den dritten Weg (19) des Funktionsventils (7) zum Eingang (17) des zweiten Kompressors (5) verbindet, und von dem das zweite Ende (83) mit dem Entspannungsnetz (50) verbunden ist.
  8. Wärmeanlage nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass der Hochdruckausgang (3) der Kompressionseinheit (1) direkt mit dem vierten Weg (46) des Produktionsventils (35) verbunden ist.
  9. Wärmeanlage nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass der Hochdruckausgang (3) der Kompressionseinheit (1) mit dem vierten Weg (46) des Produktionsventils (35) mittels eines Abzweigventils (88) mit vier Wegen verbunden ist, von dem ein erster Weg (90) verbunden ist mit dem Hochdruckausgang (3) der Kompressionseinheit (1), von dem ein zweiter Weg (92), der nicht in Kommunikation mit dem ersten Weg (90) gebracht werden kann, verbunden ist mit der Leitung (45), welche den Niederdruckeingang (2) der Kompressionseinheit (1) mit dem dritten Weg (44) des Produktionsventils (35) verbindet, von dem ein dritter Weg (94) verbunden ist mit dem vierten Weg (46) des Produktionsventils (35) und von dem der vierte Weg (46), der nicht in Kommunikation mit dem dritten Weg (94) gebracht werden kann, verbunden ist mit einem ersten Ende (98) eines fünften Wärmetauschers (89), von dem das zweite Ende (99) mit dem Entspannungsnetz (50) verbunden ist.
  10. Wärmeanlage nach Anspruch 9, dadurch gekennzeichnet, dass der erste Weg (90) des Abzweigventils (88) direkt mit dem Hochdruckausgang (3) der Kompressionseinheit (1) verbunden ist.
  11. Wärmeanlage nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass der dritte Weg (94) des Abzweigventils (88) direkt verbunden ist mit dem vierten Weg (46) des Produktionsventils (35).
  12. Wärmeanlage nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass diese umfasst einen sechsten Wärmetauscher (102), von dem ein erstes Ende (103) verbunden ist mit der Leitung (13), welche den Niederdruckeingang (2) der Kompressionseinheit (1) mit dem zweiten Weg (14) des Funktionsventils (7) mithilfe einer komplementären Rückschlagklappe (105) verbindet, welche nur eine Zirkulation des Wärmeträgerfluids von dem ersten Ende (103) des sechsten Wärmetauschers (102) in Richtung der Leitung (13) ermöglicht, wobei das zweite Ende (106) des sechsten Tauschers (102) mit dem Entspannungsnetz (50) verbunden ist.
  13. Wärmeanlage nach Anspruch 12, dadurch gekennzeichnet, dass der sechste Wärmetauscher (102) ein Sonnenkollektor (102) ist.
  14. Wärmeanlage nach Anspruch 13, dadurch gekennzeichnet, dass das zweite Ende (106) des Sonnenkollektors (102) verbunden ist mit dem Entspannungsnetz (50), derart, dass der Kollektor als Wärmeohr funktionieren kann.
EP06015308A 2005-07-29 2006-07-22 Kompressionseinheit und damit versehene thermische Anlage Not-in-force EP1748191B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0508098A FR2889296B1 (fr) 2005-07-29 2005-07-29 Unite de compression comportant desux compresseurs et installation thermique comprenant une telle unite

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EP1748191A1 EP1748191A1 (de) 2007-01-31
EP1748191B1 true EP1748191B1 (de) 2011-02-02

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AT (1) ATE497583T1 (de)
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CN108131860B (zh) * 2018-02-02 2024-01-19 北京华誉能源技术股份有限公司 一种基于单机双级压缩机的超低温空气源热泵

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DE602006019931D1 (de) 2011-03-17
FR2889296A1 (fr) 2007-02-02
FR2889296B1 (fr) 2013-07-05
ATE497583T1 (de) 2011-02-15
EP1748191A1 (de) 2007-01-31

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