EP3830499A1 - Kältemittelkreislauf - Google Patents
KältemittelkreislaufInfo
- Publication number
- EP3830499A1 EP3830499A1 EP18750160.6A EP18750160A EP3830499A1 EP 3830499 A1 EP3830499 A1 EP 3830499A1 EP 18750160 A EP18750160 A EP 18750160A EP 3830499 A1 EP3830499 A1 EP 3830499A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- expansion
- mass flow
- refrigerant circuit
- pressure
- refrigerant
- 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
- 239000003507 refrigerant Substances 0.000 title claims abstract description 250
- 238000001816 cooling Methods 0.000 claims abstract description 49
- 230000006835 compression Effects 0.000 claims description 64
- 238000007906 compression Methods 0.000 claims description 64
- 230000010349 pulsation Effects 0.000 claims description 62
- 238000004781 supercooling Methods 0.000 claims description 42
- 230000005540 biological transmission Effects 0.000 claims description 15
- 230000001105 regulatory effect Effects 0.000 claims description 8
- 239000012071 phase Substances 0.000 claims description 6
- 230000001276 controlling effect Effects 0.000 claims description 5
- 230000001419 dependent effect Effects 0.000 claims description 3
- 239000000284 extract Substances 0.000 claims description 3
- 239000007791 liquid phase Substances 0.000 claims description 3
- 238000010438 heat treatment Methods 0.000 claims description 2
- 239000007788 liquid Substances 0.000 description 17
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 16
- 230000008901 benefit Effects 0.000 description 11
- 230000008878 coupling Effects 0.000 description 11
- 238000010168 coupling process Methods 0.000 description 11
- 238000005859 coupling reaction Methods 0.000 description 11
- 230000006870 function Effects 0.000 description 9
- 230000033228 biological regulation Effects 0.000 description 8
- 229910002092 carbon dioxide Inorganic materials 0.000 description 8
- 238000013016 damping Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000007257 malfunction Effects 0.000 description 4
- 239000012080 ambient air Substances 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- 238000009835 boiling Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000004069 differentiation Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 210000000056 organ Anatomy 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000010257 thawing Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
-
- 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
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/053—Compression system with heat exchange between particular parts of the system between the storage receiver and another part of the 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
- 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
- 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
-
- 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
- F25B2400/16—Receivers
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/13—Vibrations
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
Definitions
- the invention relates to a refrigerant circuit, comprising at least one refrigerant compressor, which compresses refrigerant supplied to a suction connection to high pressure, so that a compressor mass flow of the refrigerant compressed to high pressure emerges at a pressure port, at least one high-pressure-side heat-emitting heat exchanger with an inlet at which the refrigerant circuit feeds the compressor mass flow, and with an outlet from which a cooled total mass flow of refrigerant emerges, at least one expansion unit, comprising an expansion compression unit having an expander and a compressor stage, which leads one from the refrigerant circuit in the direction of the suction connection of the refrigerant compressor
- Expansion mass flow of the total mass flow expands from high pressure to an expansion pressure, and at least one cooling stage with at least one heat-absorbing heat exchanger, to which the refrigerant circuit supplies a main mass flow comprised by the expansion pressure mass flow expanded by the expansion unit, and which the refrigerant circuit, after leaving the cooling stage, supplies the refrigerant to the suction connection of the refrigerant supplies.
- a refrigerant circuit of the type described in the introduction in that the refrigerant circuit is assigned an emergency operating unit which comprises a bypass line which bypasses the expansion compression unit and which is functionally assigned to at least one expansion element, and in that the emergency operating unit
- the expansion compression unit changes from an inactive state to an active state in which it generates an emergency expansion mass flow for operating the cooling stage by expanding the high-pressure refrigerant by means of the expansion element, which the bypass line prevents Refrigerant circuit for forwarding to the cooling stage.
- the advantage of the solution according to the invention can be seen in the fact that the problem is solved by the emergency operating unit according to the invention that in the event of an expansion disturbance of the expansion unit, in particular the expansion compression unit, the refrigerant circuit is no longer functional or can only function to a very limited extent, so that it is insufficient Can provide cooling capacity on the cooling unit and thus the cooling capacity provided by the refrigerant circuit during normal operation is eliminated, which would lead to considerable damage, for example in the case of refrigerant circuits for cooling systems, for example in the case of temperature-sensitive goods.
- Emergency operating unit supplies the emergency expansion mass flow directly or indirectly to an expansion line of the refrigerant circuit that receives the expansion pressure mass flow.
- the bypass line does not necessarily have to flow directly into the expansion line, but can, for example, also open into the refrigerant circuit before the expansion line, provided that it is ensured that the emergency expansion mass flow is indirectly supplied to the expansion line.
- bypass line provides the emergency expansion mass flow during normal operation of the refrigerant circuit that is present under expansion pressure
- Emergency expansion mass flow can be operated at least with a partial output, since the line carrying the expansion pressure mass flow during normal operation is supplied with the emergency expansion mass flow.
- Such an expansion disturbance can be detected, for example, by the expansion element itself.
- the emergency operating unit detects a high pressure of the total mass flow or of the expansion mass flow before it enters the expander.
- an advantageous solution provides that the emergency operating unit detects a pressure difference between the high pressure of the total mass flow and / or the expansion mass flow before it enters the expander and a line section of the refrigerant circuit which is at expansion pressure.
- the emergency operating unit thus detects a differential pressure, so that it is possible, for example, to use a known pressure relief valve as an expansion element, which, for example, reacts automatically to such a pressure difference and opens automatically when a certain pressure difference is exceeded, thus generating the emergency expansion mass flow.
- the emergency operating unit detects a high pressure of the total mass flow or of the expansion mass flow before it enters the expander with regard to its absolute value.
- a pressure sensor is provided, for example.
- the emergency operating unit compares the high pressure of the total mass flow or of the expansion mass flow with a reference high pressure before it enters the expander.
- Emergency operating unit has a controller that transfers the emergency operating unit from the inactive state to the active state.
- a control for example, compares the detected high pressure of the total mass flow or the expansion mass flow before it enters the expander with a stored reference pressure, for example.
- the emergency operating unit comprises at least one shutdown element for turning off the expansion compression unit.
- An advantageous solution provides that the shutdown element of the emergency operating unit is arranged either in front of an expander inlet or after an expander outlet, so that there is primarily the possibility of switching off the expander of the expansion compression unit.
- an advantageous solution provides that a switching element is arranged in the bypass line of the emergency operating unit, which produces a direct or indirect connection between an expansion element for generating the supercooling mass flow of the expansion unit and an expansion pressure outlet connection of the expansion unit.
- This solution has the advantage that an expansion device, which is present in the expansion unit anyway, can be used by the emergency operating unit to generate a supercooling mass flow
- the switching element through the
- Control of the emergency operating unit is controllable.
- the switching element is a switching valve.
- 3/2 directional control valve that connects either the bypass line or an expander outlet to the expansion pressure outlet connection.
- a 3/2-way valve is preferably also used to close the expander outlet when the bypass line is connected to the expansion pressure outlet connection or to close the bypass line when the expander outlet is connected to the expansion pressure outlet connection.
- a further solution to the problem according to the invention provides that a pulsation damper unit is arranged in the refrigerant circuit.
- Such a pulsation damper unit has the great advantage that it is able to dampen pulsations, in particular pulsations generated by the expansion compression unit, in order to prevent damage and / or noise in the refrigerant circuit caused by such pulsations.
- a variant of such a pulsation damper unit provides that it has a damper housing enclosing a damper chamber, in which at least one gas bubble is formed from refrigerant and that the gas bubble leads to a line of the refrigerant circuit
- Pulsation transmission line picks up pulsations and is able to dampen them.
- the gas bubble is above a refrigerant bath and, in this case in particular, there is liquid refrigerant in the pulsation transmission line, which transmits the pulsations into the refrigerant bath from liquid refrigerant ,
- the pulsation damper unit is provided with a heater for maintaining the gas bubble made of refrigerant, so that this can also ensure that the refrigerant circuit is operated subcritically there is always a sufficient size of the gas bubble that dampens pulsations in the pulsation damper unit.
- the pulsation damper unit is heated,
- a pulsation damper unit has a damper housing with a piston movable in it and two chambers adjacent to the piston on opposite sides and separated from one another by the piston, and that in at least one of the chambers there is a gas bubble made of refrigerant formed.
- the piston serves to dampen at least one of the gas bubbles that form in at least one of the chambers
- the piston itself in the damper housing is additionally acted upon by elastic elements, for example springs, which hold the piston in an initial position, from which the piston then acts to dampen pulsations against the force of the elastic force Elements can move.
- elastic elements for example springs
- each of the chambers is connected to different flows of refrigerant lines of the refrigerant circuit by means of a pulsation transmission line.
- Such a pulsation damper unit thus serves, in particular, to dampen pulsations by using a connection between different flows of refrigerant lines, which for example can also be at different pressure levels,
- Lines can be transmitted and thus, in addition to the piston itself, a damping effect occurs due to the coupling of the different flows of lines carrying refrigerant.
- one pulsation transmission line is connected directly or indirectly to an input of the heat-emitting heat exchanger and the other pulsation transmission line is connected directly or indirectly to an output of the heat-emitting heat exchanger.
- damping effect of such a pulsation damper unit can be further improved if at least one pulsation transmission line is coupled to the refrigerant circuit via a throttle.
- an intermediate pressure collector is arranged in the bath, a liquid phase of the refrigerant collects and in the gas volume above the bath, a gas phase of the
- Refrigerant collects.
- the liquid phase is preferably fed to the cooling stage for expansion in the expansion element thereof.
- the intermediate pressure collector has the advantage that additional subcooling can be achieved in the intermediate pressure collector by the refrigerant kept at intermediate pressure.
- Such an additional mass flow can in particular be via
- cooling stage is connected to a freezer stage in the form of a booster.
- an intermediate pressure collector and an expansion element for controlling the additional mass flow discharged from the intermediate pressure collector furthermore makes it possible to regulate an intermediate pressure in the intermediate pressure collector to a specific pressure value by means of an intermediate pressure control which controls the expansion element.
- regulation is usually carried out to a fixed pressure value of the intermediate pressure, which is in particular independent of the regulation or control of the high pressure in the total mass flow, which is carried out via the control assigned to the expansion unit.
- the COP coefficient of performance
- the ratio of cooling power to mechanical power used, in particular in
- the intermediate pressure control which controls the expansion element detects the pressure and / or the temperature of the total mass flow in the high-pressure discharge line and the size of the inlet pressure of the compressor stage and controls the intermediate pressure in such a way that a predefined quantity suitable for these is determined Value of the inlet pressure.
- the pressure value at which the intermediate pressure in the intermediate pressure collector is regulated by the intermediate pressure control is based on your basic value, for example a value in the range from 30 bar to 45 bar in the case of CO2 as a refrigerant, and additional values with amounts, for example in the range from 0.5 bar to 7 bar in the case of CO2 as a refrigerant.
- This solution has the advantage that additional efficiency increases are possible by adapting the intermediate pressure and, for example, thus also due to the reaction on the expansion unit, in particular on an inlet pressure of the compressor stage.
- the surcharge values have positive values in summer operation and negative values in winter operation, the amounts of the surcharge values being in the range mentioned above.
- the size of the additional values is dependent on the values of the high pressure that arise when regulating the high pressure.
- the size of the surcharge values also varies depending on the resulting values of the control of the high pressure by means of the expansion unit mentioned at the beginning. For example, it is provided that in summer operation the additional values are higher for high values of the high pressure than for low values of the high pressure.
- the amounts of the surcharge values are in the range from 0.5 bar to 7 bar.
- expansion unit itself, no further details have been given, except that it comprises an expansion compression unit with an expander and a compressor stage.
- Expansion system which has a subcooling unit for subcooling the total mass flow of refrigerant supplied to the expansion unit, the expansion compression unit comprising the expander and the compressor stage, a branch which branches off a subcooling mass flow from the total mass flow supplied to the expansion unit and is connected to a feed line, which leads the supercooling mass flow to an inlet of the subcooling unit, has an expansion element provided in the feed line, which expands the subcooling mass flow to a subcooling pressure, and has a connecting line which supplies the subcooling mass flow emerging from the subcooling unit to the compressor stage, which in turn supplies the subcooling mass flow compressed to a high pressure return, which is at least one high pressure
- an electrically operating control which has at least one of the following variables such as: an ambient temperature, a temperature of the expansion unit and / or the expander stage
- the mass flow flowing to the expander stage and relevant for the inlet pressure of the expansion unit or the expansion compression unit is set exclusively via the control of the subcooling mass flow by means of the one controlled by the control
- Compression of the supercooling mass flow can be used in the compressor stage, so that, at the same time, optimal expansion of the expanded mass flow takes place before it expands.
- the expansion element includes an electrical one
- One solution provides for the controller to control the ambient temperature and / or the temperature of the mass flow of the refrigerant
- Another solution comprising the temperature of the mass flow of the refrigerant provides for the temperature of the mass flow of the refrigerant to be measured with a sensor before it enters the supercooling unit and before it enters the expander.
- control system detects the ambient temperature by means of a sensor and either alone or, if necessary, in
- control is an electronic control comprising a processor, which controls the expansion element electrically by means of a control program, since with a processor the various correlations between the measured temperature and that with the
- Expansion device to be controlled supercooling mass flow can be realized in a simple manner.
- control program is in particular designed such that it either has an algorithm for determining the
- Control of the expansion device includes or a stored
- Correlation table which correlates the setting of the expansion element with the measured temperature of the mass flow supplied.
- branching is arranged between the subcooling unit and the expansion compression unit and branches off the subcooling mass flow from the total mass flow after the subcooling unit.
- This solution also has the advantage that pulsations originating from the expansion compression unit are damped by the supply line leading away from the branch with the expansion element.
- the supercooling unit can be designed differently.
- the subcooling unit is designed as a heat exchanger unit and cools the mass flow of refrigerant flowing to the expander stage by the subcooling mass flow conducted in counterflow.
- the subcooling unit is designed as a collecting container, in which a bath of liquid refrigerant of the subcooling mass flow is formed, which is used for the
- Expander stage flowing mass flow of the refrigerant cools through the bath-guiding element, wherein a gas volume forms from the bath, from which the gaseous supercooling mass flow is removed.
- This solution has the advantage that, on the one hand, the mass flow guided through the element is optimally subcooled and, on the other hand, the removal of the subcooling mass flow from the gas volume ensures that no liquid refrigerant is supplied to the compressor stage for compression.
- the expander and the compressor stage could be coupled, for example, by a generator motor unit.
- a particularly advantageous solution provides that the expander and the compressor stage of the expansion compression unit are mechanically functionally coupled.
- this solution also has the advantage that the solution according to the invention, namely the control of the mass flow expanded by the expander, can be controlled in a simple manner via the supercooling mass flow, which is compressed by the compressor stage.
- the expander and the compressor stage can be formed by suitable types of rotatingly driven machines.
- a particularly advantageous solution provides that the expander and the compressor stage are formed by a free-piston machine in which at least one free-piston can move freely in a piston chamber.
- the expansion compression unit is preferably designed such that it has two piston chambers, in each of which a free piston can be moved.
- the free pistons can preferably be moved coupled to one another.
- a first free piston in the respective piston chamber is a first one
- Expansion chamber and a first compression chamber separate.
- a second free piston in the respective piston chamber separates a second expansion chamber from a second compression chamber.
- the two free pistons are arranged coaxially with one another in the piston chambers and are movable.
- the first piston chamber is expediently separated from the second piston chamber by a separating body.
- An advantageous operation of the expansion compression unit can be realized if the two expansion chambers are arranged adjacent to the separating body in the piston chambers.
- the two compression chambers are arranged on the sides of the respective free pistons opposite the expansion chambers.
- the free pistons can work independently of each other.
- the coupling element is designed such that it extends through the expansion chambers as far as the respective free piston.
- the inflow of the refrigerant to the expansion chambers it is preferably provided that these can be controlled by a slide system.
- Such a slide system is designed, for example, as an interchangeable slide, so that in a slide position the refrigerant flows into a
- Expansion chamber flows and flows out of the other expansion chamber and in the other slide position the refrigerant flows into the other expansion chamber and flows out of the other expansion chamber.
- the slide system can be controlled by a slide drive with which the two slide positions can be set.
- a slide drive can be implemented by an electrical control which detects at least one position of the free pistons by means of at least one position sensor assigned to them.
- an advantageous solution provides that the slide drive is caused by a pressure difference between an expander inlet and a
- Expander output is controllable.
- the slide drive is preferably designed as a double-acting actuating cylinder, the piston of which is acted upon on the one hand by the pressure at the expander inlet and on the other hand by the pressure at the expander outlet.
- the slide drive can be controlled by a control slide, which controls the application of pressure to the piston at the expander inlet on the one hand and at the expander outlet on the other hand.
- the control slide is preferably designed such that it detects the positions of the free pistons and moves accordingly.
- control slide can be moved by the free pistons.
- the expansion unit has one
- control unit is also arranged on the device base.
- control unit is also arranged on the device base.
- a high-pressure inlet connection and an expansion pressure outlet connection are arranged on the device base.
- a high-pressure outlet connection is arranged over the device base, via which the compressed supercooling mass flow flows out when the expansion unit is installed.
- a further advantageous solution provides that heat exchanger connection units are provided on the base of the device, by means of which several heat exchangers on the high-pressure side can be connected.
- each of the heat exchanger connection units is designed such that it each has a three-way valve and a bypass for the respective heat exchanger, so that the three-way valve enables the flow through the respective heat exchanger to be controlled.
- At least one of the heat exchanger connection units is connected to a heat exchanger on the high-pressure side that emits heat to the ambient air.
- Phase separator is arranged, the gas phase of which is fed from a suction pressure line to the refrigerant compressor.
- Such a phase separator has the advantage that it prevents liquid refrigerant from being supplied to the refrigerant compressor for compression.
- cooling stage has at least one expansion element, so that it is possible to use it to determine the pressure desired in the cooling stage.
- Figure 1 is a schematic representation of a first embodiment of a refrigerant circuit according to the invention with a first embodiment of an expansion unit according to the invention with a first embodiment of an emergency operating unit.
- FIG. 2 shows an enlarged schematic illustration of the first exemplary embodiment of an expansion unit according to the invention with the first embodiment of an emergency operating unit;
- FIG. 3 shows a schematic illustration of a first exemplary embodiment of an expansion compression unit according to the invention
- Fig. 4 is a schematic representation similar to Fig. 3 of a second
- FIG. 5 shows a schematic illustration of a second exemplary embodiment of the refrigerant circuit according to the invention with a second embodiment of an emergency operating unit; 6 shows a schematic illustration of the first exemplary embodiment of the expansion unit with a third embodiment of an emergency operating unit;
- Fig. 7 is a schematic representation of the first embodiment of the
- Fig. 8 is a schematic representation of the first embodiment of the
- FIG. 9 shows a schematic illustration of a second exemplary embodiment of an expansion unit according to the invention with a sixth embodiment of an emergency operating unit;
- FIG. 10 shows a schematic illustration of a third exemplary embodiment of an expansion unit according to the invention with the sixth embodiment of the emergency operating unit;
- Fig. 11 is a schematic representation of the first embodiment of the
- FIG. 12 shows a schematic illustration of the first exemplary embodiment of an expansion unit with the seventh embodiment of an emergency operating unit in a second position of the 3/2-way valve;
- FIG. 13 shows a schematic illustration of a fourth exemplary embodiment of an expansion unit; 14 shows a schematic illustration of a third exemplary embodiment of a refrigerant circuit according to the invention;
- FIG. 15 shows a schematic illustration of a fourth exemplary embodiment of a refrigerant circuit according to the invention.
- FIG. 16 shows a schematic illustration of a fifth exemplary embodiment of a refrigerant circuit according to the invention.
- a first exemplary embodiment of a refrigeration system according to the invention shown in FIG. 1, comprises a refrigerant circuit, designated as a whole by 10, in which a refrigerant compressor unit, designated as a whole by 12, is arranged, for example at least one
- Refrigerant compressor includes.
- the refrigerant compressor unit 12 has a suction port 14 and a pressure port 16, with refrigerant compressed to high pressure PHI usually being present at the pressure port 16.
- refrigerant compressed to high pressure is understood to mean that the refrigerant has the highest pressure present in the refrigerant circuit.
- a high-pressure line 18 leads from the pressure connection 16 a compressor mass flow V compressed by the refrigerant compressor unit 12 to high pressure PHI to an inlet 24 of a heat-emitting heat exchanger on the high-pressure side, designated as a whole by 22, which
- the expansion pressure outlet connection 36 which is at an expansion pressure PE, is connected to an expansion line 42, which in the simplest exemplary embodiment shown in FIG. 1 leads to a cooling stage 62, which in the simplest case has a heat exchanger 64 that absorbs heat for cooling.
- the heat-absorbing heat exchanger 64 is at the expansion pressure PE, so that no separate expansion valve is connected upstream of this heat exchanger 64.
- the heat-absorbing heat exchanger 64 is followed by a phase separator 72, which is arranged in a suction pressure line 74 and leads from the cooling stage 62 to the suction connection 14 of the refrigerant compressor unit 12 and prevents liquid refrigerant from the refrigerant compressor unit 12 at the suction connection 14 is sucked in.
- Expansion pressure PE is the expansion pressure mass flow EPM through the expansion line 42 to the cooling stage 62 and from the cooling stage 62 in turn via the suction pressure line 74 to the refrigerant compressor unit 12.
- the expansion pressure mass flow EPM does not correspond to the total mass flow, but the expansion unit 32 divides the total mass flow G into an expansion mass flow EM and a subcooling mass flow UM, which is generated by the expansion unit 32 at the high pressure outlet connection 38 at a return pressure PR as a subcooling return mass flow URM is returned to a return line 78 and is fed from the latter to the compressor mass flow V before it enters the heat-emitting high-pressure side heat exchanger 22.
- the refrigerant circuits 10 according to the invention are all preferably for carbon dioxide, that is to say CO2, or
- Ammonia designed so that a transcritical cycle is usually present under common ambient conditions, in which cooling of the refrigerant to a temperature that is above the thaw takes place only before the expansion of the refrigerant by the expansion unit 32, for example by means of the heat exchanger 22. and boiling line or saturation curve isotherms, so that none
- Condensation of the refrigerant takes place at a temperature that passes through the refrigerant's thawing and boiling line or saturation curve
- Expansion unit 32 comprises, as shown enlarged in FIG. 2, a
- Expansion system 30 which has a device base designated as a whole by 82, on which the high-pressure inlet connection 34 of the
- Expansion pressure outlet port 36 and the high pressure outlet port 38 are arranged.
- an expansion compression unit 84 is connected to the device base 82, which comprises an expander stage 86 and a compressor stage 88, which are integrated in the expansion compression unit 84 and are rigidly coupled to one another.
- the expansion compression unit 84 comprises an expander inlet 92 and an expander outlet 94, which is connected to the expansion pressure outlet connection 36, as well as a compressor inlet 96 and a compressor outlet 98, which in turn is connected to the high pressure outlet connection 38.
- a subcooling unit 102 is arranged on the device base 82, which in the first exemplary embodiment is designed as a countercurrent heat exchanger and has an input 104 and an output 106 for the mass flow to be cooled, in particular in this case the total mass flow G, and an input 112 and an output 114 for the subcooling mass flow UM which is conducted through the heat exchanger as a countercurrent.
- the subcooling mass flow UM is branched off at a branch 116 from the total mass flow G emerging and supercooled at the output 106 of the subcooling unit 102, so that an expansion mass flow EM is led from the branch 116 through a feed line to the expander inlet 92 and the subcooling mass flow UM through Shut-off device 124 and one with an actuator 123 driven expansion element 122 is guided in the feed line 126, in which the supercooling mass flow UM is expanded to a pressure PU, and is then fed to the input 112 of the subcooling unit 102, the subcooling mass flow UM in the subcooling unit 102 in counterflow from the input 104 to the output 106 flowing total mass flow G subcooled and from the outlet 114 by means of a
- Connection line 128 is supplied to the compressor input 96.
- the mechanical energy released in the expander stage 86 by expansion of the expansion mass flow EM is fed directly to the compressor stage 88 in the expansion compression unit 84 by a mechanical functional coupling, and in this leads to a compression of the supercooling mass flow UM from an inlet pressure EP of the compressor stage 88 to a return high pressure PR, which corresponds to or is higher than the pressure level PHI in the high pressure line 18, so that the subcooling return mass flow URM can be supplied from the high pressure outlet connection 38 to the compressor mass flow V via a high pressure return line 78.
- a controller 132 is also provided in the expansion system 30, which, on the one hand, detects the temperature of the mass flow of the refrigerant before its expansion in the expansion stage 86, for example with a sensor 134, which is in particular a temperature sensor and, for example, corresponding to this temperature by means of the actuator 123 Expansion organ 122 controls.
- sensor 134 is arranged, for example, between branch 116 and expander 86 as sensor 134i.
- the controller is assigned a sensor 135 with which it is able to detect the inlet pressure EP.
- the sensor 134 can also be used as a sensor 1342 between the high-pressure input connection 34 and the supercooling unit 102.
- the senor 134 as the sensor 134 3, measures the ambient temperature, which in particular decisively influences the temperature of the total mass flow G of the refrigerant at the outlet 26 of the heat exchanger 22 through the ambient air flowing through the heat exchanger 22.
- the controller 132 can operate autonomously, for example, so that the controller is part of the expansion system 30 which is installed as an independent unit in the refrigerant circuit.
- controller 132 is coupled to an external controller 138 which, as shown in FIG. 1, as an alternative or in addition to the sensors 134, the temperature of the total mass flow G in the high-pressure section 28 and / or the temperature or Pressure in the refrigerant compressor 12 is detected in order to control the actuator 123 directly or indirectly or by means of the control 132.
- the expansion element 122 serves to control the supercooling mass flow UM, and thereby the high pressure PH2 at the high pressure input connection 34 and thus also the high pressure PH2 in the high pressure line 28 in accordance with one of the controls 132 and / or the external controller 138, in particular in this one as a file or algorithm
- the controller 132 and / or the external controller 138 comprise, for example, a processor and a memory in which an algorithm or a
- Correlation tables are stored, by means of which a correlation between the settings of the expansion element 122 and the measured ones
- Expander inlet 92 which sets the high pressure PH2 corresponding to the temperature.
- the subcooling mass flow UM usually comprises approximately 15% to 35% of the total mass flow G, so that the expansion mass flow EM comprises approximately 85% to 65% of the total mass flow G.
- the regulation of the high pressure PH2 takes place in such a way that in the subcooling unit 102 the temperature of the total mass flow G on the hot side, ie at the inlet 104, is only a few Kelvin, for example less than 4 Kelvin, better still less than 3 Kelvin, in particular one up to two Kelvin, above the temperature of the subcooling mass flow UM at the outlet 114 of the subcooling unit 102, in order to substantially completely evaporate the refrigerant in the subcooling mass flow U.
- a sensor connected to the controller 132 is in particular still provided in the connecting line 128.
- the expansion compression unit designated as a whole by 84, is designed as a free-piston machine, which has a cylinder housing 142 in which two piston chambers 144 and 146, which are separate from one another, are arranged, with a movable free piston in each piston chamber 152, 154 is arranged.
- the free pistons 152 and 154 divide the respective piston chambers 144 and 146 into expansion chambers 162 and 164 and compression chambers 166 and 168.
- the free pistons 152 and 154 are preferably mechanically coupled to one another, in such a way that, at the maximum volume of the first expansion chamber 162, the first piston 152 is positioned such that the first compression chamber 166 has a minimum volume and at the same time the second free chamber piston 154 is such that its expansion chamber 164 has a minimum volume, while the compression chamber 168 has the maximum volume or vice versa.
- an increase in volume of the first expansion chamber 162 when it is acted upon by the high pressure at the expander inlet 92, leads to a compression of refrigerant of the supercooling mass flow U in the first compression chamber 166, at the same time to an expulsion of the refrigerant in the second compression chamber 168 in the direction of the expander outlet 94 and for drawing in refrigerant in the second compression chamber 168 via the compressor inlet 96.
- the first free piston 152 and the second free piston 154 are preferably arranged coaxially to one another and move in piston chambers 144 and 146 which are likewise arranged coaxially to one another and are separated from one another by a separating body 148, the separating body 148 being sealed by a coupling element 172 which penetrates the
- the coupling element 172 can be designed as a coupling rod which penetrates the separating body 158 and which moves with the free pistons 152, 154 and which is in free contact with the free pistons 152 and 154, that is to say is not firmly connected to them.
- the pressure in this expansion chamber 162 or 164 acts on the respective free piston 152 or 154 and at the same time a pressure which is higher in the respective compression chamber 168 or 166 of the other free piston 154 or 152 acts
- a pressure which is higher than that at the expander inlet 92 can be generated in the compression chamber 166 or 168 acted upon by the free piston 152 or 154 applied high pressure, so that the supercooling mass flow U can be compressed to a pressure present at the compressor outlet 98 which corresponds at least to the high pressure PHI at the inlet 24 of the heat-emitting heat exchanger or the pressure in the high pressure line 18, although the high pressure PH2, the expander inlet to Is available due to pressure losses in the heat exchanger 22 is slightly smaller than the high pressure PHI.
- Compressor inlet 96 are from compressor inlet 96
- Supply lines 182 are provided which lead to the inlet valves 184 and 186 assigned to the compression chambers 166 and 168, and the compressor outlet 98 is also connected to a pressure line 192 which leads from the outlet valves 194 and 196 assigned to the compression chambers 166 and 168 to the compressor outlet 98.
- the slide system 202 comprises a controller 203, which detects the positions of the free pistons 152 and 154 by means of position sensors 204 and 206 and controls an exchangeable slide, designated as a whole by 208, which has two slide positions and one in the slide position by means of an electric drive 207 Expander inlet 92 with the expansion chamber 162 and the expander outlet 94 with the
- Expansion chamber 164 and in the other slide position connects the expander inlet to the expansion chamber 164 and the expander outlet 94 to the expansion chamber 162.
- a pressure control of the change-over slide 208 is provided in a slide system 202 ', the drive 207' having a pressure-driven cylinder with a piston 205, which, controlled by an auxiliary slide 209, alternately on the one hand with the pressure at the expander inlet 92 and, on the other hand, the pressure at the expander outlet 94 or vice versa is applied, the auxiliary slide 209 also being designed as a change-over slide and its slide positions being achieved by mechanical detection of the positions of the free pistons 152 and 154 in their end positions facing the separating body 148.
- the expansion compression unit 84 is configured as a free-piston machine, malfunctions thereof can occur, so that no expansion pressure mass flow EPM or a sufficiently large expansion pressure mass flow EPM would be available for the cooling unit 62, cooling capacity would no longer be available on the cooling unit 62, so that Refrigerant circuit 10 would no longer be functional.
- the refrigerant circuit 10 is provided with an emergency operating unit 230, which prevents this case.
- a first embodiment of an emergency operating unit 230 provided in the expansion system 30 comprises, for example, an additional expansion element 232 which is arranged in a bypass line 234, which in turn is connected in parallel to the expander stage 86, in particular between its expander input 92 and expander output 94, and is designed as a pressure relief valve, which in turn opens when a predeterminable opening pressure PO is exceeded and then acts as an expansion element in the bypass line 234, so that an emergency operation expansion mass flow NEPM is fed to the expansion line 42 through the expansion element in the bypass line 234, which then is supplied in the cooling unit 62 Can absorb heat, so that the refrigerant circuit 10 can continue to run in emergency operation (Fig. 1 and Fig. 2).
- the emergency operating expansion mass flow NEPM is selected such that a minimum cooling capacity is available on the cooling unit 62.
- parts of the refrigerant circuit 10 adjacent to the expander stage 86, for example to the expansion line 42, are preferably one
- Pulsation damper 260 connected, which comprises a damper housing 262 enclosing a damper chamber 264, in which a bladder 266 is formed at least in a subcritical operating state
- gaseous refrigerant above a refrigerant bath 268 from liquid refrigerant, the refrigerant bath 268 being connected to the expansion line 42, for example, via a pulsation transmission line 272.
- the bubble 264 made of gaseous refrigerant thus makes it possible to dampen pulsations in the expansion pressure mass flow EPM, which also affect the bath 268 of the refrigerant.
- the damper housing 262 is preferably provided in the region of the region surrounding the bladder 266 with a heater 274 which is provided via a heat transport circuit 276 supplies heat from return line 78 to damper housing 262 to maintain bladder 266 of vaporous refrigerant.
- the first exemplary embodiment of the expansion unit 30 is assigned a third embodiment of an emergency operating unit 230 ", which is designed such that the expansion element 232 is arranged in a bypass line 234", which is the expander stage 86 and one in front of the expander - Input 92 arranged shut-off element 236 is connected in parallel, so that when the expansion element 232 is opened, there is the possibility, through the shut-off valve 236, of decommissioning the expander stage 86 and thus the entire expansion compression unit 84, so that only the emergency operating expansion mass flow NEPM flows from the high-pressure inlet connection 34 to the expansion pressure outlet connection 36.
- the compressor stage 88 is also out of operation, so that no supercooling return mass flow URM flows to the high-pressure line 18 via the high-pressure outlet connection 38 and the return line 78.
- shut-off element 236 is not arranged in front of the expander inlet 92, but immediately after the expander outlet 94, and the bypass line 234 ′′ is thus the expander stage 86 with the shut-off element 236, which is arranged following the expander output 94, connected in parallel.
- controller 238 is provided on the one hand to control the expansion element 232 and the shut-off element 236.
- the emergency operating unit 230" comprises the expansion element 237 and the shut-off element 236. This embodiment is the same as the third
- the shut-off element 236 arranged in front of the expander inlet 92 to by interrupting the in the expander 86
- Expansion member 122 enters, and connects the expansion pressure outlet port 36 together.
- Shut-off element 237 is provided, while the expansion member 122 provided for the expansion of the subcooling mass flow UM also serves as the expansion member for the emergency operating unit 230 "" and therefore the
- Expanders 86 is guided to the expansion pressure outlet connection 36.
- the emergency operation control 238 which controls the shut-off elements 236 and 237 when the sensor 242 is on
- the emergency expansion unit 230 is likewise formed by the bypass line 234.
- the shut-off element 237 while the shut-off element 236 connects directly to the expander outlet 94 is arranged in such a way that the bypass line 234 is led from the supply line 126 to the expansion pressure outlet connection 36 and opens into a bypass line between the shut-off element 236 and the expansion pressure outlet connection 36.
- bypass line 272 also leads into this bypass line, which leads to a pulsation damper 260, which is designed in the same way as described in connection with the first exemplary embodiment, in which case the heat transport circuit 276 likewise Is part of the expansion system 30 and extracts heat from a bypass line between the compressor outlet 98 and the high pressure outlet connection 38 and supplies it to the heater 274.
- a pulsation damper unit 280 is provided between the high-pressure input connection 34 and the high-pressure output connection 38, which has a damper housing 282, in which a piston 284 is arranged, which has a piston
- Damper housing 282 separates arranged first chamber 286 from a second chamber 288, wherein for example the first chamber 282 is connected to the high pressure input connection 34 via a first pulsation transmission line 292 and the second chamber 288 is connected to the high pressure output connection 38 via a second pulsation transmission line 294.
- the pulsation damper unit 280 is thus able to dampen pulsations propagating to the high-pressure inlet connection 34 or to the high-pressure outlet connection 38 in that the piston transmits pulsation, the piston 284 preferably being mounted between two spring-elastic damping elements 296 and 298 is that in the
- Chambers 286 and 288 are arranged.
- FIGS. 11 and 12 are based in principle on the fifth embodiment of the
- Emergency operating unit 230 in which case the emergency operating unit 230. has a bypass line 234. which leads from the supply line 126 to a
- 3/2 directional valve 235 leads, which is able either to connect the expander outlet 94 to the expansion pressure outlet connection 36 and to close the bypass line 234. or the bypass line
- the 3/2 way valve 235 also being controlled by the controller 238, which detects, for example, the high pressure of the expansion mass flow EM before it enters the expander.
- the expansion element 122 which is actually intended for the expansion of the supercooling mass flow UM, serves as an expansion element for the emergency operation unit 230 in the case of emergency operation.
- the expansion unit 32 ′′ is modified in such a way that the branch 116 ′ is arranged between the high-pressure inlet connection 34 and the inlet 104 of the supercooling unit 102 and thus the subcooling mass flow UM Flow through the supercooling unit 102 is branched off by the total mass flow G, the shut-off member 124 and the expansion member 122 being provided in the same way as in the previous exemplary embodiments, which are arranged between the branch 116 '"and the inlet 112 for the countercurrent flowing through the subcooling unit 102 ,
- Controller 132 is controlled in the same way as in the first embodiment.
- This fourth exemplary embodiment can also be used with emergency operating units, for example with an emergency operating unit 230 according to the first
- Pressure relief valve provided.
- the expansion unit 32 '" can also be used with emergency operating units 230',
- the third exemplary embodiment is provided with the third embodiment of the emergency operating unit 230 ′′, with respect to which reference is made to the previous explanations regarding this third embodiment.
- the expansion line 42 does not go directly to the cooling stage 62, but to an intermediate pressure collector 44, in which a bath 46 of liquid refrigerant is formed at expansion pressure PE, from which liquid refrigerant is supplied to the cooling stage 62 ′′ via a liquid line 48, which in FIG in this case not only includes the heat-absorbing heat exchanger 64, but also a shutdown element 68 and an expansion element 66. Furthermore, a gas volume 52 of refrigerant is formed in the intermediate pressure collector 44 above the bath 46, from which an additional mass flow Z is fed to the suction line 74 via an expansion element 54.
- Expansion device 54 is adjustable.
- a pulsation damper 260 is also assigned to the high-pressure lead 28, which corresponds to the pulsation damper 260 shown in the first exemplary embodiment of the refrigerant circuit 10 according to FIG. 1 and assigned to the expansion line 42, so that the function of the same is fully explained in the foregoing this can be referred to.
- the pulsation damper 260 can also be in the area of the
- Expansion unit 32 arranged or even integrated into the expansion system 30.
- FIG. 15 a fourth exemplary embodiment of a refrigerant circuit 10 '' according to the invention, shown in FIG. 15, which are identical to those of the first and second exemplary embodiments, are provided with the same reference numerals, so that the description of the same applies to the contents of the same
- the fourth exemplary embodiment is provided with the pulsation damper unit 280, which in this exemplary embodiment is connected in parallel with the heat exchanger 22 and thus dampens pulsations between the high-pressure line 18 and the high-pressure discharge line 28.
- the pulsation damper unit 280 is of identical design to that integrated into the third exemplary embodiment of the expansion unit 32 ′′
- Pulsation damper unit 280 (FIG. 10), so that full reference can be made to the above statements in this regard.
- a throttle 302 is also provided between the second pulsation transmission line 294 and the high-pressure line 18 in order to obtain an improved damping effect.
- the additional mass flow Z from the gas volume 52 is not fed directly to the suction pressure line 74 via the expansion element 54, but again through an in the
- the cooling stage 62 ′′ is designed, for example, as a normal cooling stage and, in addition, a deep-freezing stage 212 is also provided, which has a heat-absorbing heat exchanger 214 and a shutdown element 218 and an expansion element 216.
- the refrigerant expanded in the freezer stage 212 is fed via a suction pressure line 224 to a freezer compressor unit 222, which compresses the refrigerant to such an extent that it can be fed to the suction pressure line 74 for the refrigerant compressor unit 12 for compression to high pressure.
- a subcooler 226 is preferably also provided in the suction pressure line 224 of the freezer compressor unit 212, which subcooles the refrigerant supplied via the liquid line 48 to the freezer stage 212 again before it enters the freezer stage 212, specifically by means of the exiting from the freezer stage 212 and Expanded refrigerants carried in the suction pressure line 224.
- This regulation of the temperature of the main mass flow H comprises the regulation of an intermediate pressure PM in the intermediate pressure collector 44 by means of the expansion element 54, which in this case can be controlled via an intermediate pressure control 55.
- the high pressure PH2 in the high-pressure discharge line it would be possible, on the one hand, for the high pressure PH2 in the high-pressure discharge line to be operated by means of the controls 132 and / or 138 in accordance with an optimal operation of the expansion unit 32 with the respective one
- the intermediate pressure controller 55 to merely define a constant intermediate pressure PM in the intermediate pressure collector 44.
- the increase in efficiency of the refrigerant circuit can be achieved by the above-mentioned detection of the inlet pressure EP of the compressor stage 88 by means of the controls 132, 138.
- the refrigerant circuit 10 according to the invention can also be operated with regard to the achievable COP, that is to say the ratio of cooling power to the mechanical power used, in particular in summer, and with regard to the expansion of the functional operation of the
- the intermediate pressure PM is regulated, for example, by means of the intermediate pressure controller 55 and the expansion element 54 to a pressure value which, on the one hand, results from a basic value, which is generally defined once, and supplementary values for this basic value which vary depending on the operating state.
- the basic value for CO2 as a refrigerant is in the range of 30 bar to 45 bar, so that a value from this range, for example 35 bar, is specified as the basic value, and the additional values for CO2 as refrigerant are in the range of 0 , 5 bar to 7 bar.
- the surcharge values could in principle be fixed values from the range of surcharge values provided for them, but it is particularly favorable if the surcharge values vary within this range due to the operating state.
- the additional values having positive values in summer operation and negative values in winter operation, so that the values for CO2 as refrigerant in summer operation are in the range from 0.5 bar to 7 bar and at Winter operation is in the range of -0.5 bar to -7 bar.
- the size of the additional values are dependent on the values lying in the control range of the high pressure PH2 and therefore vary depending on the values of the high pressure PH2.
- the additional values are higher for high values of the high pressure than for low values of the high pressure.
- CO2 as a refrigerant during summer operation
- there are additional values in the range from +0.5 bar to +3 bar provided the high pressure PH2 has values in the range from 75 bar to 80 bar
- additional values in the range from +3 bar to +7 bar provided the high pressure PH2 has values in the range greater than 80 bar, preferably values greater than 80 bar to 120 bar.
- an additional value in the range of 3 bar is used for a high pressure PH2 in the range of 80 bar, while an additional value in the range of 5 bar is used for high pressure PH2 in the range of 90 bar.
- the additional values for winter operation are, for example, in the range from -0.5 bar to -3 bar, provided the high pressure PH2 is in the range from 55 bar to 65 bar and the additional values are in the range from -3 bar to -5 bar, provided the high pressure PH2 is below 50 bar to 40 bar.
- an additional value in the range of -3 bar is used for a high pressure PH2 in the range of 60 bar and an additional value in the range of -5 bar is used for high pressure in the range of 50 bar.
- the basic value is preferably always the same.
- the inlet pressure EP changes at the compressor stage 88 and thus a subcooler output of the subcooling unit 102.
- the inlet pressure EP at the compressor stage 88 increases and thus the subcooling mass flow UM and thus the subcooling power of the subcooling unit 102 are increased, so that the COP also increases.
- Intermediate pressure control 55 detects the variables, in particular the temperature and / or the pressure of the total mass flow G in the high pressure discharge line 28 and the variable of the inlet pressure EP of the compressor stage 88, and controls the intermediate pressure PM as a function thereof in order to adjust to a predefined and suitable one for the detected variables, for example in the
- Intermediate pressure controller 55 to regulate stored value of the input pressure EP.
- All compressor units can be any compressor or combination of compressors (parallel, in series, multi-stage).
- one or more of the compressors can be provided with a power control, which is carried out by switching off compressors, by mechanical power control (for example switching off, in particular cyclical switching off of parts (cylinder banks) of a compressor) or
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
Claims
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2018/070919 WO2020025135A1 (de) | 2018-08-01 | 2018-08-01 | Kältemittelkreislauf |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3830499A1 true EP3830499A1 (de) | 2021-06-09 |
Family
ID=63108558
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18750160.6A Pending EP3830499A1 (de) | 2018-08-01 | 2018-08-01 | Kältemittelkreislauf |
EP19746487.8A Pending EP3830500A2 (de) | 2018-08-01 | 2019-08-01 | Kältemittelkreislauf |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19746487.8A Pending EP3830500A2 (de) | 2018-08-01 | 2019-08-01 | Kältemittelkreislauf |
Country Status (2)
Country | Link |
---|---|
EP (2) | EP3830499A1 (de) |
WO (2) | WO2020025135A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN113865133B (zh) * | 2021-09-17 | 2022-08-23 | 珠海格力电器股份有限公司 | 一种空调***及其控制方法 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007111595A1 (en) * | 2006-03-27 | 2007-10-04 | Carrier Corporation | Refrigerating system with parallel staged economizer circuits discharging to interstage pressures of a main compressor |
JP5064517B2 (ja) * | 2008-02-20 | 2012-10-31 | パナソニック株式会社 | 冷凍サイクル装置 |
WO2010113158A1 (en) * | 2009-04-01 | 2010-10-07 | Linum Systems, Ltd. | Waste heat air conditioning system |
JP4837150B2 (ja) * | 2009-06-02 | 2011-12-14 | 三菱電機株式会社 | 冷凍サイクル装置 |
US8327651B2 (en) * | 2009-07-07 | 2012-12-11 | Hamilton Sundstrand Corporation | Transcritical fluid cooling for aerospace applications |
EP2795204B1 (de) * | 2011-12-23 | 2021-03-10 | GEA Bock GmbH | Verdichter |
JP6276000B2 (ja) * | 2013-11-11 | 2018-02-07 | 株式会社前川製作所 | 膨張機一体型圧縮機及び冷凍機並びに冷凍機の運転方法 |
DE102015214705A1 (de) * | 2015-07-31 | 2017-02-02 | Technische Universität Dresden | Vorrichtung und Verfahren zum Durchführen eines Kaltdampfprozesses |
US20170174049A1 (en) * | 2015-12-21 | 2017-06-22 | Ford Global Technologies, Llc | Dynamically controlled vapor compression cooling system with centrifugal compressor |
-
2018
- 2018-08-01 EP EP18750160.6A patent/EP3830499A1/de active Pending
- 2018-08-01 WO PCT/EP2018/070919 patent/WO2020025135A1/de unknown
-
2019
- 2019-08-01 WO PCT/EP2019/070823 patent/WO2020025770A2/de unknown
- 2019-08-01 EP EP19746487.8A patent/EP3830500A2/de active Pending
Also Published As
Publication number | Publication date |
---|---|
WO2020025770A2 (de) | 2020-02-06 |
EP3830500A2 (de) | 2021-06-09 |
WO2020025770A3 (de) | 2020-04-02 |
WO2020025135A1 (de) | 2020-02-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102011118162C5 (de) | Kombinierte Kälteanlage und Wärmepumpe und Verfahren zum Betreiben der Anlage mit funktionsabhängiger Kältemittelverlagerung innerhalb des Kältemittelkreislaufes | |
DE60314559T2 (de) | Verfahren zum Erhöhen der Leistungsfähigkeit einer Dampfverdichtungsanordnung mittels Verdampferheizung | |
EP1914491B1 (de) | Kälteanlage | |
DE102006035784B4 (de) | Kälteanlage für transkritischen Betrieb mit Economiser und Niederdruck-Sammler | |
DE102012208992B4 (de) | Heiz-/Kühlkreislauf für Fahrzeuge, insbesondere für Hybridfahrzeuge oder reine Elektrofahrzeuge | |
WO2009080154A2 (de) | Verfahren zur rückgewinnung einer verlustwärme einer verbrennungskraftmaschine | |
DE10356447A1 (de) | Kältekreislaufvorrichtung | |
EP3595919B1 (de) | Kälteanlage eines fahrzeugs mit einem als kältekreislauf für einen ac-betrieb und als wärmepumpenkreislauf für einen heizbetrieb betreibaren kältemittelkreislauf | |
DE102015112439A1 (de) | Kälteanlage | |
EP3648997A1 (de) | Kälteanlage für ein fahrzeug mit einem einen wärmeübertrager aufweisenden kältemittelkreislauf sowie wärmeübertrager für eine solche kälteanlage | |
DE10347748A1 (de) | Mehrfachzonen-Temperatursteuersystem | |
EP3099985B1 (de) | Kälteanlage | |
EP3574269B1 (de) | Expansionseinheit zum einbau in einen kältemittelkreislauf | |
WO2020025135A1 (de) | Kältemittelkreislauf | |
DE102018112333A1 (de) | Kältemittelkreislauf mit einer Expansions-Kompressions-Vorrichtung sowie Verfahren zum Betreiben des Kältemittelkreislaufs | |
AT522875B1 (de) | Verfahren zur Regelung eines Expansionsventils | |
DE102017101218A1 (de) | Fahrzeuginnenraumluftklimatisierungs- und batteriekühlsystem | |
DE202007017723U1 (de) | Anlage für die Kälte-, Heiz- oder Klimatechnik, insbesondere Kälteanlage | |
DE102007013485B4 (de) | Verfahren zur Regelung einer CO2-Kälteanlage mit zweistufiger Verdichtung | |
DE202006014246U1 (de) | Kaltdampf-Kältemaschine | |
DE102013204188A1 (de) | Kältemittelkreis | |
DE102007045764A1 (de) | Kältemittelkreisvorrichtung und Herstellungsverfahren dafür | |
DE102004042887B3 (de) | Klimaanlage für ein Fahrzeug, insbesondere für ein Kraftfahrzeug | |
DE10338388B3 (de) | Verfahren zur Regelung einer Klimaanlage | |
EP3922930B1 (de) | Verfahren zum betrieb einer kompressionskälteanlage und zugehörige kompressionskälteanlage |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: UNKNOWN |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20210127 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
DAV | Request for validation of the european patent (deleted) | ||
DAX | Request for extension of the european patent (deleted) | ||
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20221103 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230517 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20240305 |