EP1096209B1 - Installation de pompage de chaleur, notamment à fonction frigorifique - Google Patents

Installation de pompage de chaleur, notamment à fonction frigorifique Download PDF

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Publication number
EP1096209B1
EP1096209B1 EP00402925A EP00402925A EP1096209B1 EP 1096209 B1 EP1096209 B1 EP 1096209B1 EP 00402925 A EP00402925 A EP 00402925A EP 00402925 A EP00402925 A EP 00402925A EP 1096209 B1 EP1096209 B1 EP 1096209B1
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EP
European Patent Office
Prior art keywords
heat pumping
zone
water
compression
pumping installation
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.)
Expired - Lifetime
Application number
EP00402925A
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German (de)
English (en)
French (fr)
Other versions
EP1096209A1 (fr
Inventor
Jean Françoais Reynaud
Guy Chambaron
Henri Rodie-Talbere
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Electricite de France SA
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Electricite de France SA
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Publication date
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Publication of EP1096209A1 publication Critical patent/EP1096209A1/fr
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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
    • F25B31/00—Compressor arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type

Definitions

  • the present invention relates to an installation heat pumping, in particular with refrigeration function, of the compression-expansion refrigerant cycle type, including a vaporization zone before compression and a condensation zone after the latter, in which the thermodynamic fluid used in said cycle as well as the fluid used in cycles coolant and coolant is water, exchanges thermal vaporization and respectively condensation between these last two cycles and said cycle refrigerant carried out directly, without the intermediary of exchange surfaces, and the cold produced by this installation usually being at a temperature greater than 0 ° C ("positive" cold) or at a temperature negative for ice production; it is of course however that the primary function of such installation could instead be the production of heat.
  • thermodynamic fluids such as than those of the CFC family (chlorofluorocarbons) which have an unfavorable impact on the greenhouse effect, or HCFCs (hydrochlorofluorocarbons) or HFCs (hydrofluorocarbons) whose impact on the greenhouse effect is less but still not negligible.
  • the object of the present invention is therefore, while retaining the advantages inherent in the use of water as a thermodynamic fluid, avoid disadvantages of prior techniques in a industrial scale heat pumping installation, especially for the primary purpose of producing cold but without excluding the production of heat.
  • installation in accordance with present invention is characterized in that the refrigerant cycle implements dynamic compression with two compression sections separated, connected to each other by at least one zone heat exchange (desuperheating and / or economizer) and enclosed in a vapor containment hermetic and thermally insulated, and in that the wheels of these two sections are mounted directly on the opposite ends of the shaft of an electric motor joint variable speed seal arranged in said enclosure, between these sections.
  • zone heat exchange desuperheating and / or economizer
  • centrifugal which will be used in preference to so-called axial compression sections, will include, classic way, for each stage constituting them (in principle one or two), a moving wheel preceded by a converging suction and followed by a static diffuser smooth or finned.
  • said electric motor will be a synchronous motor with permanent magnet rotor associated with a frequency converter that will vary the speed and therefore adapt the wheel rotation speed compressor at the treated steam flow rates, and operate at part load within the limits of aerodynamic stability of the compressor.
  • the adoption of a such an engine will ensure minimum losses thermal at the rotor, which is important held bad thermal exchanges in an enclosure where In the case of cold production, there will be a very low vapor pressure.
  • asynchronous motors with device for eliminating heat losses.
  • the shaft bearings of said electric motor can be of any type appropriate to their function, for example of the type with ceramic ball bearings, or still fluid or smooth, water type with device anticavitation, or even oil with device sealing, or magnetic type, as soon as any contamination of the refrigerant by means of lubrication is made impossible.
  • the shaft bearings of said motor are arranged on the latter side, the compressor wheels being the type cantilevered on the ends of said shaft, but the reverse arrangement is also possible: wheels compressor placed between the motor and the bearings, without overhang.
  • both compression sections are arranged in opposition to on both sides of the electric drive motor common, with their respective entrances (aspirations) directed towards the ends of the containment (unlike the prior art mentioned first plus top), vaporization and desuperheating zones being thus formed between these ends of the enclosure and, respectively, the entrance to the first and the entrance to the second compression section.
  • This provision compensates for axial reactions due to the wheels, contributes to obtaining very compact, particularly in length, and facilitates connection of external water circuits.
  • both compression sections are associated with a third compression section arranged in the enclosure of confinement - or communication with it - and consisting of a booster, which is arranged upstream or downstream of the compressor or between its two sections.
  • this booster will be driven by a hydraulic turbine working with water, particular borrowed from the internal circuit, at the level of the vaporization or condensation but it could be also driven by a steam expansion turbine or by an independent electric motor, possibly at a speed different from that of the compressor, even be shut down if conditions return normal climatic conditions.
  • said booster or compression sections consist of one or more compression wheels including a flange rotor rotating fitted with flat radial fins and possibly associated with static blasting fluid pre-rotation.
  • condensation zone is located at the end of the containment which is on the suction inlet side of the second section of compression, or that this condensation zone is located between the desuperheating zone and this entry suction of the second compression section.
  • Figure 1a we have shown a variant according to which is implemented two compression sections 1 ' and 2 'connected in parallel, with a common input 3' and driven by a common 6 'motor, to obtain higher cooling capacities. These sections can be followed by a compression section, this the latter can also consist of two sections in parallel and / or a booster.
  • Figure 2 also schematically represents a installation which includes a third section of compression (or booster) 7 driven by a motor independent electric 8, including suction inlet 9 communicates with the output of the second section of compression 2 and whose discharge 10 communicates with a condensation zone; the implementation of this booster in the installation will be better seen in figure 13, in which we used the same references as on the Figure 3, to designate the common areas.
  • a third section of compression (or booster) 7 driven by a motor independent electric 8
  • suction inlet 9 communicates with the output of the second section of compression 2 and whose discharge 10 communicates with a condensation zone
  • the movable wheels 11 and 12 of these two compression sections 1 and 2 are wedged in overhang on the opposite ends of the shaft 18 of the common electric motor 6 above, which is of the type synchronous and watertight, and the rotor of which is advantageously with permanent magnets.
  • the bearings of the shaft 18 being lubricated without oil, as will be described below, the maintenance is facilitated, and the risk of pollution of the refrigerant.
  • the enclosure 13 in order to simplify the maintenance operations which may involve different trades (refrigeration engineers, mechanics, thermodynamicians, electricians), is made up of three separate modules connected one to the next by flanges 19 and 20, the assembly of which is ensured by known means (bolts, "grasshoppers” etc). These three modules include a flash-evaporation module 21 containing a vaporization zone 22, a compression module 23 containing the two compression sections 1 and 2, and a condensing module 24 containing an area to desuperheating 25 and possibly economiser, and the condensation zone 26.
  • the vaporization zone 22 is established under the form of a flash evaporator in which internal energy fluid remains constant (isenthalpic expansion), the decrease of that of the liquid being exactly compensated by increasing that of the vaporized liquid.
  • the chilled water back to the facility by a line 27, which has been heated, for example up to about 12 ° C, by its passage in the circuit of use U that the installation aims to cool is injected as droplets into the zone 22 by a spray boom 28 and vaporizes instantly because of the very low absolute pressure, which can be of the order of 10 mbar, prevailing in this zone 22.
  • the energy required to vaporization of the liquid comes from the liquid itself, according to an adiabatic process.
  • the water thus cooled to a temperature which can be of the order of 7 ° C., is recovered at the bottom of the enclosure and is evacuated by a chilled water pipe referenced in 29.
  • the heat exchanges in this refrigerant cycle are direct (exchanges by contact and not through surfaces), and there is very little irreversibility; we have removed the "pinch" present in the installations at tubular or plate heat exchangers, which allows to obtain a higher practical performance coefficient to 7 for evaporation and condensation temperatures 7 and 30 ° C respectively.
  • the absence of surfaces of exchange for the evaporator and the condenser present plus the advantage of requiring no clearance longitudinal for stubbing or cleaning surfaces, hence a decrease in the space that must be reserved for installation.
  • the presence of water droplets in the vapor thus created is beneficial because it promotes desuperheating steam during the next phase of compression, resulting in a lower volume flow, allowing to reduce the passage sections, therefore the size of installation and cost.
  • the density is higher, which makes it possible to obtain a rate of more compression and helps increase the overall coefficient of performance.
  • the liquid / vapor separator or demister 25, 15 placed at the suction inlet 3, 4 of each section of compression can be, as detailed in Figure 4, followed or replaced by a fixed converging horn 30 special on the wall of which water can flow and whose the trailing edge ends in a water collector circular or gutter 31, provided with an outlet lower water outlet 32 and ensuring effective inertial separation between water and steam.
  • a fixed converging horn 30 special on the wall of which water can flow and whose the trailing edge ends in a water collector circular or gutter 31, provided with an outlet lower water outlet 32 and ensuring effective inertial separation between water and steam.
  • these blades are advantageously encircled, in their axial portion, by a hoop, referenced 33 in the perspective view of FIG. 5.
  • This hoop which also has an antivibration effect, can thus channel the aspirated water until it leaves the area axial.
  • the partial developed section view of the figure 6 also shows the possibility of conferring on the fins 34 of the rotor blades at an acute angle to in the plane of the rear flange 35, which favors water entrainment in the direction of rotation. he would also be possible to give these fins 34 a slight concavity, with the same effect (Figure 7).
  • Figure 8 shows a variant of simplified compressor usable if we wish to lower the cost price or reduce the rotating masses for booster 8 or for compression wheels, variant which in addition will eliminate the fret 33 mentioned above: the compressor has a rotor with rotating flange 37 provided with radial flat fins 38 and possibly associated with static blades 36 of fluid pre-rotation.
  • the vapor compressed in the first section 1 of the compressor is directed to the second section 2 by the traffic conduits 5 already mentioned and referenced also in Figure 3.
  • These conduits may include section outlet a smooth or finned radial diffuser 39, 39a and / or axial 40, 40a with fins (case of the part high of the drawing), intended to raise the vapor pressure by decreasing its speed. It may be necessary to provide an additional injection of water into the diffuser, downstream of the wheel in order to desuperheat the steam.
  • the vapor coming from the conduits 5 suffers from desuperheating in the desuperheating zone intermediate 25 mentioned above, located in this example near the end 17 of the enclosure of containment 13, this to avoid reaching excessive temperatures at the compressor outlet.
  • This desuperheating can be ensured by "flash-relaxation" of the water flow from the condenser and returned to the evaporator, which constitutes an economizer ensuring a partial cooling of this water. Indeed, water having a very high latent heat, the vaporization a small volume of liquid is sufficient to desuperheat the steam.
  • the vapor from the second section of compression 2 at a temperature close to condensation under the corresponding pressure then passes into the area of condensation 26 by other static conduits 41.
  • the condensation is carried out by mixing, exchange thermal occurring between the vapor phase from compressor and liquid droplets dispersed by a spray boom 42 supplied by a pipe 43 return of cooled water (at around 25 ° C) from the air cooler (A), being an air cooler classic coil and mechanical ventilation, preventing any contact between water and outside air, this for avoid biological or chemical contamination as well than the presence of dissolved gases in the water.
  • the water heated by condensation of steam is collected at the bottom of the enclosure and returns to the air cooler by a pipe 44 ( Figure 3).
  • the main resistance to condensation phenomenon is not related to convection in vapor but rather in conduction in the liquid, what it may be suitable for ensure a residence time of the liquid in the condenser as long as possible, increasing the areas of contact and with mixing with the steam circulating at counter current, created by a lining of the condenser such as Raschig rings.
  • a filling was shown schematically at 45 in Figure 9 and is surmounted by a distributor 46 supplied with water cooled by the ramp 42, a grid 47 being provided at the base of the lining for its retention inside a rack 48.
  • a pump vacuum which is carried out at the pressure of condensation.
  • the pump When the installation starts, the enclosure 13 being filled with pressurized air, the pump must exhaust this air to bring the absolute internal pressure to a value close to 40 mbar.
  • a "reflux” condenser at the exit from the condensation zone 26.
  • a condenser "reflux” shown in Figure 10, could be consisting of a column 50 at the base of which the steam residual from condensing zone 26 east injected through baffles 51, the incondensables saturated with moisture being discharged through its end upper 52 to the vacuum pump 49.
  • This column can successively include two zones against the current: on the one hand an area 53 in which part of the steam condenses thanks to a surface exchanger coil 54 in which the refrigeration supply is ensured by the return of water from the air cooler before spraying in the ramp 42 of the condenser, on the other hand a zone 55 in which another part of the vapor is condenses thanks to a surface exchanger 56 with tubes and water circulation baffles, the refrigeration contribution being here ensured by a low flow of chilled water 57 from of the vaporization zone 22.
  • the "reflux" condenser might only include one or the other of the two parts described above, or two types of swapped exchange surfaces.
  • FIG. 12a shows the thermodynamic diagram of the installation I.
  • Q F represents the heat taken from the cold source, namely the user circuit U; W represents the work received in installation I, and Q C the heat transferred to the hot source, namely the air cooler A (see also figure 12b), the relation which links these values being
  • the enthalpy diagram of FIG. 12b represents a conventional operation of the installation I.
  • the water is vaporized at a temperature T E of approximately 7 ° C in the evaporation zone 22, then compressed in the first compression section 1 , desuperheated to a temperature T D of approximately 18 ° C, compressed in the second compression section 2 to reach a temperature T C of approximately 30 ° C, and condensed in the condensation zone 26.
  • the water from condensation is pumped by a pump P 1 to the air cooler A at 44, and returns to a temperature of about 25 ° C, at 43 (heat transfer cycle).
  • the water is cooled by vaporization, between approximately 12 and 7 ° C, and is pumped into the user circuit U by a pump P 2 .
  • the installation could also have the primary function heat production, in which case the pressure at the interior of the enclosure could be greater than the atmospheric pressure to reach temperatures condensation above 100 ° C.
  • FIG. 14 shows a possible water bearing structure for shaft 18 of electric motor 6.
  • This bearing referenced in 59, comprises an inlet for pressurized liquid 60, which undergoes by dynamic effect partial relaxation in the interval 61 between the bore of the bearing and the surface of the shaft 18, before undergoing additional relaxation and partial vaporization at its exit from this interval, in 62. Steam and residual liquid are then directed in a plenum 63 by a deflector 64.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Central Heating Systems (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Compressor (AREA)
EP00402925A 1999-10-25 2000-10-23 Installation de pompage de chaleur, notamment à fonction frigorifique Expired - Lifetime EP1096209B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9913272A FR2800159B1 (fr) 1999-10-25 1999-10-25 Installation de pompage de chaleur, notamment a fonction frigorifique
FR9913272 1999-10-25

Publications (2)

Publication Number Publication Date
EP1096209A1 EP1096209A1 (fr) 2001-05-02
EP1096209B1 true EP1096209B1 (fr) 2004-07-28

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EP00402925A Expired - Lifetime EP1096209B1 (fr) 1999-10-25 2000-10-23 Installation de pompage de chaleur, notamment à fonction frigorifique

Country Status (10)

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US (1) US6397621B1 (es)
EP (1) EP1096209B1 (es)
JP (1) JP2001165514A (es)
AT (1) ATE272197T1 (es)
CA (1) CA2323941A1 (es)
DE (1) DE60012450T2 (es)
ES (1) ES2225051T3 (es)
FR (1) FR2800159B1 (es)
IL (1) IL139125A (es)
TW (1) TW534971B (es)

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US4420373A (en) 1978-05-30 1983-12-13 Dan Egosi Energy conversion method and system
US4282070A (en) * 1978-05-30 1981-08-04 Dan Egosi Energy conversion method with water recovery
US4323109A (en) * 1979-08-27 1982-04-06 General Electric Company Open cycle heat pump system and process for transferring heat
US4522035A (en) 1981-01-23 1985-06-11 Techmark Corporation Method and apparatus for recovering waste energy
US4437316A (en) * 1981-01-23 1984-03-20 Technology Marketing Inc. Method and apparatus for recovering waste energy
US4454720A (en) * 1982-03-22 1984-06-19 Mechanical Technology Incorporated Heat pump
JPS60147067A (ja) 1984-01-10 1985-08-02 協和醗酵工業株式会社 ヒ−トポンプ
EP0239680B1 (en) * 1986-03-25 1990-12-12 Mitsui Engineering and Shipbuilding Co, Ltd. Heat pump
DE4237664A1 (de) * 1992-11-07 1994-05-11 Asea Brown Boveri Verfahren zum Betrieb eines Turboverdichters

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ATE272197T1 (de) 2004-08-15
FR2800159B1 (fr) 2001-12-28
EP1096209A1 (fr) 2001-05-02
FR2800159A1 (fr) 2001-04-27
CA2323941A1 (fr) 2001-04-25
IL139125A0 (en) 2001-11-25
US6397621B1 (en) 2002-06-04
JP2001165514A (ja) 2001-06-22
DE60012450T2 (de) 2005-08-04
ES2225051T3 (es) 2005-03-16
DE60012450D1 (de) 2004-09-02
TW534971B (en) 2003-06-01
IL139125A (en) 2003-12-10

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