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EP3830499B1 - Circuit frigorifique - Google Patents

Circuit frigorifique Download PDF

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Publication number
EP3830499B1
EP3830499B1 EP18750160.6A EP18750160A EP3830499B1 EP 3830499 B1 EP3830499 B1 EP 3830499B1 EP 18750160 A EP18750160 A EP 18750160A EP 3830499 B1 EP3830499 B1 EP 3830499B1
Authority
EP
European Patent Office
Prior art keywords
expansion
mass flow
pressure
unit
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.)
Active
Application number
EP18750160.6A
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German (de)
English (en)
Other versions
EP3830499A1 (fr
Inventor
Oliver Javerschek
Julian KARBINER
Jörg Nickl
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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Publication of EP3830499A1 publication Critical patent/EP3830499A1/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
    • 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 method for operating 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 exits at a pressure connection, at least one high-pressure side heat-emitting heat exchanger with an inlet to which the refrigerant circuit supplies the compressor mass flow, and with an outlet from which a cooled total mass flow of refrigerant exits, at least one expansion unit, comprising an expansion compression unit having an expander and a compressor stage, which expands an expansion mass flow of the total mass flow, guided from the refrigerant circuit in the direction of the suction connection of the refrigerant compressor, 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 of the expansion pressure mass flow expanded by the expansion unit, and to which the refrigerant circuit, after leaving the Cooling
  • the emergency operating unit is designed is that it detects an expansion fault of the expansion compression unit, that the emergency operation unit has a control which transfers the emergency operation unit from the inactive state to the active state and that the emergency operation unit is designed such that it in the event of a fault, in particular an expansion fault, 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 emergency expansion mass flow the bypass line supplies to the refrigerant circuit for forwarding to the cooling stage.
  • the advantage of the solution according to the invention is that the emergency operating unit according to the invention solves the problem that in the event of an expansion fault in the expansion unit, in particular the expansion compression unit, the refrigerant circuit is no longer functional or only functional to a very limited extent, so that it cannot provide sufficient cooling capacity to the cooling unit and thus the cooling capacity provided by the refrigerant circuit during normal operation is lost, which would lead to considerable damage, for example, in refrigerant circuits for cooling systems, for example for temperature-sensitive goods.
  • bypass line of the emergency operation 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.
  • bypass line does not necessarily have to flow directly into the expansion line, but can also flow into the refrigerant circuit upstream of the expansion line, for example, provided that it is ensured that the emergency expansion mass flow is thereby indirectly fed to the expansion line.
  • bypass line supplies the emergency expansion mass flow to a line of the refrigerant circuit which, during normal operation of the refrigerant circuit, carries the expansion pressure mass flow present at expansion pressure.
  • the solution according to the invention provides that the emergency operation unit detects an expansion fault of the expansion compression unit.
  • Such an expansion disturbance can be detected, for example, by the expansion element itself.
  • the emergency operation unit detects a high pressure of the total mass flow or the expansion mass flow before it enters the expander.
  • an advantageous solution provides that the emergency operation 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 at expansion pressure.
  • the emergency operation unit 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 level of the pressure difference is exceeded, thus generating the emergency expansion mass flow.
  • the emergency operation unit detects a high pressure of the total mass flow or the expansion mass flow in terms of its absolute value before it enters the expander.
  • a pressure sensor is provided.
  • the emergency operation unit compares the high pressure of the total mass flow or the expansion mass flow with a reference high pressure before it enters the expander.
  • a transition of the emergency operating unit from the inactive state to the active state can be advantageously realized in the solution according to the invention if the emergency operating unit has a control which transfers the emergency operating unit from the inactive state to the active state.
  • Such a control system 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 switching off the expansion compression unit.
  • An advantageous solution provides that the shutdown element of the emergency operation unit is arranged either before an expander inlet or after an expander outlet, so that it is primarily possible to switch 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 operation unit, which establishes a direct or indirect connection between an expansion element for generating the subcooling mass flow of the expansion unit and an expansion pressure output connection of the expansion unit.
  • This solution has the advantage that an expansion element that is already present in the expansion unit for generating a subcooling mass flow can be used by the emergency operation unit to generate the emergency expansion mass flow instead of the subcooling mass flow, so that no additional expansion element is required.
  • the switching element can be controlled by the control of the emergency operation unit.
  • the switching element is a switching valve.
  • the switching element is a 3/2-way valve, which connects either the bypass line or an expander outlet to the expansion pressure outlet connection.
  • a 3/2-way valve also serves 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.
  • Another advantageous solution provides for a pulsation damper unit to be 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 of refrigerant is formed and that the gas bubble absorbs pulsations via a pulsation transmission line leading to a line of the refrigerant circuit and is able to dampen them.
  • the gas bubble is located above a refrigerant bath and, in particular, in this case, liquid refrigerant is present in the pulsation transmission line, which transfers the pulsations into the refrigerant bath of liquid refrigerant.
  • the pulsation damper unit is provided with a heater to maintain the gas bubble of refrigerant, so that even in the case of subcritical operation of the refrigerant circuit, it can be ensured that the gas bubble dampening the pulsations is always present in the pulsation damper unit in sufficient size.
  • the pulsation damper unit in particular its damper housing, is heated by coupling the heating with a heat transport circuit, which extracts heat in the refrigerant circuit to a pressure in the range of high-pressure compressed refrigerant.
  • a pulsation damper unit has a damper housing with a piston movable therein and two chambers adjacent to the piston on opposite sides and separated from each other by the piston, and that a gas bubble made of refrigerant forms in at least one of the chambers.
  • the piston also serves to exert a dampening effect at least through the gas bubble that forms in at least one of the chambers.
  • the piston itself in the damper housing is additionally loaded by elastic elements, for example springs, which hold the piston in an initial position, from which the piston can then move against the force of the elastic elements to dampen pulsations.
  • elastic elements for example springs
  • each of the chambers is connected to different streams of refrigerant-carrying lines of the refrigerant circuit by means of a pulsation transmission line.
  • such a pulsation damper unit serves in particular to dampen pulsations by using a connection between different flows of refrigerant-carrying lines, which may also be at different pressure levels, to dampen pulsations in one of the two lines or in both of these lines, whereby these lines remain decoupled by the piston,
  • a pulsation in one of the lines can be transmitted in a dampened manner to the other of the lines and thus, in addition to the piston itself, a damping effect occurs through the coupling of the different flows of refrigerant-carrying lines.
  • one pulsation transmission line is directly or indirectly connected to an inlet of the heat-emitting heat exchanger and the other pulsation transmission line is directly or indirectly connected to an outlet 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 between the expansion unit and the cooling stage, in whose bath a liquid phase of the refrigerant collects and in whose gas volume above the bath a gas phase of the refrigerant collects.
  • the liquid phase of the cooling stage is preferably fed to the expansion device thereof.
  • the intermediate pressure receiver has the advantage that additional subcooling can be achieved by the refrigerant kept at intermediate pressure in the intermediate pressure receiver.
  • an additional mass flow is discharged from the gas volume of the intermediate pressure collector.
  • Such an additional mass flow can be supplied in particular via an expansion device of the suction pressure line.
  • the additional mass flow expanded by the expansion device additionally subcools a main mass flow led to the cooling stage in a heat exchanger, so that the main mass flow can be cooled even further.
  • an intermediate pressure collector and an expansion element for controlling the additional mass flow discharged from the intermediate pressure collector also creates the possibility of regulating an intermediate pressure in the intermediate pressure collector to a specific pressure value by means of an intermediate pressure control that controls the expansion element.
  • the intermediate pressure control controlling the expansion device determines the pressure and/or temperature of the total mass flow in the high-pressure discharge line as well as the size of the inlet pressure of the compressor stage and controls the intermediate pressure in such a way that a predetermined value of the inlet pressure is established that is suitable for these measured variables.
  • the pressure value to which the intermediate pressure in the intermediate pressure collector is regulated by the intermediate pressure control is determined from a base value, for example a value in the range of 30 bar to 45 bar in the case of CO 2 as a refrigerant, and additional values with amounts, for example in the range of 0.5 bar to 7 bar in the case of CO 2 as a refrigerant.
  • This solution has the advantage that additional efficiency increases are possible by adjusting the intermediate pressure and, for example, also due to the feedback on the expansion unit, in particular on the inlet pressure of the compressor stage.
  • the size of the additional values depends on the high pressure values that occur when the high pressure is regulated.
  • the additional values are planned to be higher at high pressure values than at low high pressure values.
  • the additional values are smaller at high high pressure values than at low high pressure values.
  • the amounts of the surcharge values are in the above-mentioned range of 0.5 bar to 7 bar.
  • expansion unit itself, except that it comprises an expansion-compression unit with an expander and a compressor stage.
  • an electrically operating control which controls at least one of the following variables such as: an ambient temperature, a Temperature of the mass flow of the refrigerant supplied to the expansion unit and/or the expander stage and an inlet pressure of the compressor stage are recorded and, in accordance with this temperature and/or, if applicable, this inlet pressure of the compressor stage, an inlet pressure of the expansion unit or the expander stage - and thus indirectly the high pressure of the total mass flow - and/or, if applicable, an inlet pressure of the compressor stage is set by controlling the subcooling mass flow by means of the expansion element electrically controlled by the control.
  • the mass flow flowing to the expander stage and relevant for the inlet pressure of the expansion unit or the expansion compression unit is adjusted exclusively by controlling the subcooling mass flow by means of the expansion device controlled by the control, so that when the mass flow expands in the expander stage, maximum energy is recovered, which can be used to compress the subcooling mass flow in the compressor stage, so that at the same time optimal subcooling of the expanded mass flow takes place before its expansion.
  • the expansion element comprises an electrically driven servo motor.
  • One solution is for the control system to measure the ambient temperature and/or the temperature of the mass flow of the refrigerant before inlet of the subcooling unit and/or before it enters the expander by means of a sensor.
  • Another solution that comprehensively records the temperature of the mass flow of the refrigerant provides for measuring the temperature of the mass flow of the refrigerant with a sensor before it enters the subcooling unit and before it enters the expander.
  • control system detects the ambient temperature by means of a sensor and takes this into account alone or, where appropriate, in combination with the temperature of the mass flow of the refrigerant before it enters the subcooling unit and/or before it enters the expander for the control of the expansion device.
  • control is an electronic control comprising a processor which electrically controls the expansion element by means of a control program, since with a processor the diverse correlations between the measured temperature and the subcooling mass flow to be controlled by the expansion element can be realized in a simple manner.
  • this design of the control system makes it possible to always control the expansion element in such a way that the subcooling mass flow exits the subcooling unit in a superheated state, thus preventing partially liquid refrigerant in the subcooling mass flow from escaping from the subcooling unit and being fed to the expansion stage.
  • a sensor connected to the control system is provided in a connecting line between the subcooling unit and the compressor stage in order to detect an inlet pressure of the compressor stage, for example when it is to be controlled.
  • control program is designed in particular in such a way that it comprises either an algorithm for determining the control of the expansion element or a stored correlation table which correlates the setting of the expansion element with the measured temperature of the supplied mass flow.
  • a particularly advantageous solution provides that the branch is arranged between the subcooling unit and the expansion-compression unit and, after the subcooling unit, the subcooling mass flow branches off from the total mass flow.
  • This solution is particularly advantageous for subcritical heat dissipation and allows for greater subcooling.
  • this solution has the advantage that pulsations emanating from the expansion compression unit are dampened by the supply line leading away from the branch with the expansion element.
  • the subcooling unit can be designed in different ways.
  • the subcooling unit is designed as a heat exchanger unit and cools the mass flow of the refrigerant flowing to the expander stage by the subcooling mass flow guided through it in countercurrent.
  • the subcooling unit is designed as a collecting container in which a bath of liquid refrigerant of the subcooling mass flow is formed, which cools an element leading the mass flow of the refrigerant flowing to the expander stage through the bath, wherein a gas volume is formed above the bath, from which the gaseous subcooling mass flow is discharged.
  • This solution has the advantage that, on the one hand, the mass flow passing through the element is optimally subcooled and, on the other hand, by removing the subcooling mass flow from the gas volume, it can be ensured 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.
  • Such a mechanical functional coupling means that the energy generated in the expander is transferred directly to the compressor stage via a mechanical connection.
  • 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 subcooling mass flow compressed by the compressor stage.
  • the expander and the compressor stage can be formed by suitable types of rotary-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 is freely movable 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 is movable.
  • the free pistons are preferably movable in a coupled manner.
  • a first free piston in the respective piston chamber separates a first expansion chamber and a first compression chamber from one another. Furthermore, it is advantageously provided that 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 to each other in the piston chambers and are movable.
  • the first piston chamber is 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.
  • an advantageous solution provides that a coupling element coupling the free pistons extends through the separating body and is movable relative to it, in particular in a sealed manner.
  • the coupling element is designed in such a way that it extends through the expansion chambers to the respective free piston.
  • Such a slide valve system is designed, for example, as a change-over slide valve, so that in one slide valve position the refrigerant flows into one expansion chamber and flows out of the other expansion chamber and in the other slide valve 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 adjusted.
  • Such a slide drive can be carried out 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 can be controlled by a pressure difference between an expander inlet and an expander outlet.
  • the slide drive is 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 so 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 a device base on which the subcooling unit and the expansion compression unit are arranged.
  • control unit is also arranged on the device base.
  • a high-pressure outlet connection is arranged on the device base, via which the compressed subcooling mass flow flows out when the expansion unit is installed.
  • a further advantageous solution provides that heat exchanger connection units are provided on the device base, with which several high-pressure side heat exchangers can be connected.
  • each of the heat exchanger connection units is designed in such a way that it has a three-way valve and a bypass for the respective heat exchanger, so that the three-way valve makes it possible to control the flow through the respective heat exchanger.
  • At least one of the heat exchanger connection units is connected to a high-pressure side heat exchanger that releases heat to the ambient air.
  • phase separator is arranged following the cooling stage, the gas phase of which is fed to the refrigerant compressor from a suction pressure line.
  • phase separator has the advantage that it prevents liquid refrigerant from being fed to the refrigerant compressor for compression.
  • cooling stage has at least one expansion element, so that it is possible to set the desired pressure in the cooling stage.
  • a first embodiment of a refrigeration system 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, which for example comprises at least one refrigerant compressor.
  • the refrigerant compressor unit 12 has a suction connection 14 and a pressure connection 16, wherein refrigerant compressed to high pressure PH1 is usually present at the pressure connection 16.
  • high-pressure compressed refrigerant means that the refrigerant has the highest pressure present in the refrigerant circuit.
  • a high-pressure line 18 leads a compressor mass flow V compressed by the refrigerant compressor unit 12 to high pressure PH1 to an inlet 24 of a high-pressure side heat-emitting heat exchanger, designated as a whole by 22, which emits heat in particular to the ambient air and thus cools the refrigerant, so that at an outlet 26 of the high-pressure side heat exchanger 22 there is a total mass flow G of refrigerant cooled by the high-pressure side heat exchanger 22, which is supplied by a refrigerant at a high pressure PH2, which is slightly lower than the high pressure PH1 due to the heat exchanger 22, is fed to a high-pressure regulating expansion unit 32, designated as a whole by 32, which has a high-pressure inlet connection 34 connected to the high-pressure line 28, an expansion pressure outlet connection 36 and a high-pressure outlet connection 38.
  • the expansion pressure outlet connection 36 which is at an expansion pressure PE, is connected to an expansion line 42, which in the Fig. 1 illustrated simplest embodiment 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.
  • phase separator 72 is connected downstream of the heat-absorbing heat exchanger 64, which is arranged in a suction pressure line 74 that leads from the cooling stage 62 to the suction connection 14 of the refrigerant compressor unit 12 and prevents liquid refrigerant from being sucked in by the refrigerant compressor unit 12 at the suction connection 14.
  • an expansion pressure mass flow EPM at expansion pressure PE thus flows 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 rather the total mass flow G is divided in the expansion unit 32 into an expansion mass flow EM and a subcooling mass flow UM, which is discharged from the expansion unit 32 at the high-pressure outlet connection 38 at a return pressure PR as a subcooling return mass flow URM of a return line 78 and is fed from there to the compressor mass flow V before it enters the heat-emitting high-pressure side heat exchanger 22.
  • the refrigerant circuits 10 described below are all preferably designed for carbon dioxide, i.e. CO2, or ammonia, so that under common ambient conditions a transcritical cycle is usually present, in which only before the expansion of the refrigerant is carried out by the expansion unit 32, for example by means of the heat exchanger 22, the refrigerant is cooled to a temperature which corresponds to isotherms running above the dew and boiling line or saturation curve, so that there is no liquefaction of the refrigerant.
  • CO2 carbon dioxide
  • ammonia ammonia
  • the first embodiment of the expansion unit 32 comprises, as in Fig. 2 shown enlarged, an expansion system 30 which has a device base designated as a whole by 82, on which the high pressure inlet connection 34, the expansion pressure outlet connection 36 and the high pressure outlet connection 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 rigidly coupled to one another.
  • the expansion compression unit 84 includes an expander inlet 92 and an expander outlet 94 connected to the expansion pressure output port 36, as well as a compressor inlet 96 and a compressor outlet 98, which in turn is connected to the high pressure output port 38.
  • a subcooling unit 102 is arranged on the device base 82, which in the first embodiment is designed as a countercurrent heat exchanger and has an inlet 104 and an outlet 106 for the mass flow to be cooled, in particular in this case the total mass flow G, as well as an inlet 112 and an outlet 114 for the subcooling mass flow UM guided as a countercurrent through the heat exchanger.
  • the subcooling mass flow UM is branched off in the expansion system 30 at a branch 116 from the subcooled total mass flow G exiting at the outlet 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 is passed through a shut-off device 124 and a valve 125 connected to an actuator 123.
  • the subcooling mass flow UM in the supply line 126, in which the subcooling mass flow UM is expanded to a pressure PU and is then fed to the inlet 112 of the subcooling unit 102, wherein the subcooling mass flow UM in the subcooling unit 102 subcools the total mass flow G flowing from the inlet 104 to the outlet 106 in countercurrent and is fed from the outlet 114 to the compressor inlet 96 by means of a connecting line 128.
  • 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 leads to a compression of the subcooling 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 PH1 in the high pressure line 18, so that the subcooling return mass flow URM can be fed from the high pressure output connection 38 via a high pressure return line 78 to the compressor mass flow V.
  • a controller 132 is provided in the expansion system 30, which on the one hand, for example with a sensor 134, which is in particular a temperature sensor, detects the temperature of the mass flow of the refrigerant before its expansion in the expansion stage 86 and, for example, controls the expansion element 122 according to this temperature by means of the actuator 123.
  • a sensor 134 which is in particular a temperature sensor
  • the senor 134 is arranged, for example, between the branch 116 and the expander stage 86 as sensor 134 1 .
  • control is assigned a sensor 135 with which it is able to detect the inlet pressure EP.
  • the senor 134 can also be used as sensor 134z between the high-pressure inlet connection 34 and the subcooling unit 102.
  • the sensor 134 as sensor 134s measures the ambient temperature, which significantly influences the temperature of the total mass flow G of the refrigerant at the outlet 26 of the heat exchanger 22, in particular due to the ambient air flowing through the heat exchanger 22.
  • the controller 132 can, for example, operate autonomously, so that the controller is part of the expansion system 30 installed as an independent unit in the refrigerant circuit.
  • control 132 is coupled to an external controller 138, which - as in Fig. 1 shown - alternatively or in addition to the sensors 134, the temperature of the total mass flow G in the high-pressure compartment 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 controller 132.
  • the expansion element 122 serves to control the subcooling mass flow UM and thereby to regulate the high pressure PH2 at the high pressure inlet connection 34 and thus also the high pressure PH2 in the high pressure discharge line 28 according to a relationship specified by the controller 132 and/or the external controller 138, in particular stored therein as a file or algorithm, depending on the respectively measured temperature of the refrigerant and thus depending on the possibilities for cooling the refrigerant located on the high pressure PH2, for example depending on the ambient temperature present for cooling in the heat exchanger 22.
  • the controller 132 and/or the external regulator 138 comprise, for example, a processor and a memory in which an algorithm or a correlation table is stored, by means of which a correlation between the settings of the expansion element 122 and the measured temperatures is stored, so that the settings of the expansion element 122, made by the actuator 123 controlled by the controller 132, lead to the high pressure PH2 corresponding to the temperature being set at the high pressure inlet connection 34 and/or at the inlet 104 of the subcooling unit 102 and/or at the expander inlet 92.
  • the regulation of the high pressure PH2 by controlling the subcooling mass flow UM is possible because the mechanical functional coupling of the expander 86 with the compressor stage 88 means that the expansion mass flow EM is directly correlated with the subcooling mass flow UM according to a fixed volume ratio, so that the expansion mass flow EM can be specified by specifying the subcooling mass flow UM.
  • 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 high pressure PH2 is controlled such that in the subcooling unit 102 the temperature of the total mass flow G on the hot side, i.e. at the inlet 104, is only a few Kelvin, for example less than 4 Kelvin, even better less than 3 Kelvin, in particular one to two Kelvin, above the temperature of the subcooling mass flow UM at the outlet 114 of the subcooling unit 102 in order to essentially completely evaporate the refrigerant in the subcooling mass flow U.
  • a sensor connected to the controller 132 is provided in particular in the connecting line 128.
  • controller 132 and/or 138 it is also possible to use the controller 132 and/or 138 to detect the inlet pressure EP by means of the sensor 135 and to regulate it to a suitable value corresponding to the variables such as pressure and/or temperature of the total mass flow G and the size of the inlet pressure EP, wherein the suitable values for the said variables are stored, for example, in the controller 132 and/or 138.
  • 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 separate piston chambers 144 and 146 are arranged, wherein a movable free piston 152, 154 is arranged in each piston chamber.
  • 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, when the first expansion chamber 162 has a maximum volume, 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 piston 154 is positioned 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 the volume of the first expansion chamber 162 when it is subjected to the high pressure at the expander inlet 92 leads to a compression of refrigerant of the subcooling mass flow U in the first compression chamber 166, simultaneously to a displacement of the refrigerant in the second compression chamber 168 in the direction of the expander outlet 94 and to a suction of refrigerant in the second compression chamber 168 via the compressor inlet 96.
  • first free piston 152 and the second free piston 154 are arranged coaxially to one another and move in piston chambers 144 and 146 which are also arranged coaxially to one another and are separated from one another by a separating body 148, wherein the separating body 148 is sealed by a coupling element 172 which couples the movement of the two free pistons 152 and 154.
  • the coupling element 172 can be designed as a coupling rod which passes through the separating body 158 and moves with the free pistons 152, 154, which rod rests freely on the free pistons 152 and 154, i.e. is not firmly connected to them.
  • supply lines 182 are provided which extend from the compressor inlet 96 and lead to the inlet valves 184 and 186 associated with 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 associated with the compression chambers 166 and 168, respectively, to the compressor outlet 98.
  • An alternating connection between the expander inlet 92 and the expander outlet 94 with the expansion chambers 162 and 164 is made via a slide system 202 which is piston position controlled.
  • the slide system 202 comprises a controller 203 which uses position sensors 204 and 206 to detect the positions of the free pistons 152 and 154, respectively, and uses an electric drive 207 to control a changeover slide, designated as a whole by 208, which has two slide positions and, in one slide position, connects the expander inlet 92 to the expansion chamber 162 and the expander outlet 94 to 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 controller 203 which uses position sensors 204 and 206 to detect the positions of the free pistons 152 and 154, respectively, and uses an electric drive 207 to control a changeover slide, designated as a whole by 208, which has two slide positions and, in one slide position, connects the expander inlet 92 to the expansion chamber 162 and the expander outlet 94 to the expansion chamber 164, and in the other slide position, connects the expander inlet to the expansion chamber 164 and
  • a pressure control of the changeover slide 208 is provided, wherein the drive 207' has a pressure-driven cylinder with a piston 205, which is controlled by an auxiliary slide 209 alternately acted upon on the one hand by the pressure at the expander inlet 92 and on the other hand by the pressure at the expander outlet 94 or vice versa, wherein the auxiliary slide 209 is also designed as a changeover slide and whose slide positions are determined by mechanical detection of the positions of the free pistons 152 and 154 in their end positions facing the separating body 148.
  • the high pressure PH1 and PH2 would rise to a level that would cause damage to the heat exchanger 22 and/or the refrigerant compressor 12.
  • the refrigerant circuit 10 is provided with an emergency operation unit 230 which prevents this case.
  • a first embodiment of an emergency operation 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 inlet 92 and expander outlet 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 supplied to the expansion line 42 through the expansion element in the bypass line 234, which can then absorb heat in the cooling unit 62, so that the refrigerant circuit 10 can continue to run in emergency operation ( Fig. 1 and Fig. 2 ).
  • the emergency operation expansion mass flow NEPM is selected such that a minimum cooling capacity is available at the cooling unit 62.
  • a pulsation damper 260 is preferably connected to parts of the refrigerant circuit 10 adjacent to the expander stage 86, for example to the expansion line 42, which comprises a damper housing 262 enclosing a damper chamber 264, in which, at least in a subcritical operating state, a bubble 266 of gaseous refrigerant forms above a refrigerant bath 268 of liquid refrigerant, wherein the refrigerant bath 268 is connected, for example, to the expansion line 42 via a pulsation transmission line 272.
  • the bubble 264 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 with a heater 274 in the area surrounding the bubble 266, which supplies heat from the return line 78 to the damper housing 262 via a heat transport circuit 276 to maintain the bubble 266 of vaporous refrigerant.
  • a second embodiment of the emergency operation unit 230' is not part of the expansion system 30, as described in connection with the first embodiment of the refrigerant circuit 10 according to the invention, but is a unit independent of the expansion system 30, wherein the expansion element 232 designed as a pressure relief valve is arranged in the bypass line 234', which in this case connects the high-pressure line 28 to the expansion line 42 and is thus connected in parallel to the entire expansion unit 32 ( Fig. 5 ).
  • the first 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 connected in parallel to the expander stage 86 and a shut-off element 236 arranged in front of the expander inlet 92, so that When the expansion element 232 is opened, it is possible to shut off the expander stage 86 and thus the entire expansion compression unit 84 via the shut-off valve 236, so that only the emergency operation 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 subcooling return mass flow URM flows to the high-pressure line 18 via the high-pressure output connection 38 and the return line 78.
  • an emergency operation control 238, which uses a sensor 242 to detect the high pressure PH2 present in the refrigerant circuit 10 upstream of the expander stage 86, for example the high pressure between the outlet 106 of the subcooling unit 102 and the expander inlet 92 ( Fig. 6 ).
  • 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 connected in parallel to the expander stage 86 with the shut-off element 236, which is arranged following the expander outlet 94.
  • control 238 is provided on the one hand for controlling the expansion element 232 and the shut-off element 236.
  • the emergency operation unit 230 ⁇ comprises the expansion element 237 and the shut-off element 236.
  • the shut-off element 236 is arranged in front of the expander inlet 92 in order to deactivate the expander stage 86 by interrupting the expansion mass flow EM flowing into the expander stage 86, while the bypass line 234 ⁇ connects the supply line 126, into which the subcooling mass flow UM enters after flowing through the expansion element 122, and the expansion pressure output connection 36.
  • a further shut-off element 237 is provided in the bypass line 234 ⁇ , while the expansion element 122 provided for the expansion of the subcooling mass flow UM also serves as an expansion element for the emergency operating unit 230 ⁇ and therefore determines the emergency expansion mass flow NEPM, which is led to the expansion pressure output connection 36, bypassing the expander 86.
  • the emergency operation control 238 which controls the shut-off elements 236 and 237 when the sensor 242 detects an undesirable increase in the high pressure PH2.
  • the emergency expansion unit 230 ⁇ ′ is also formed by the bypass line 234'''' with the shut-off element 237, while the shut-off element 236 is arranged immediately following the expander outlet 94, so 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.
  • the pulsation transmission line 272 also opens into this bypass line, which is led to a pulsation damper 260 that is designed in the same way as described in connection with the first embodiment, wherein in this case the heat transport circuit 276 is also 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.
  • the expansion system 30 is provided with the emergency operation unit 230 ⁇ ′ according to the sixth embodiment, so that in this regard, reference can be made in full to the explanations for the sixth embodiment.
  • a pulsation damper unit 280 is provided between the high-pressure inlet connection 34 and the high-pressure outlet connection 38, which has a damper housing 282 in which a piston 284 is arranged, which separates a first chamber 286 arranged in the damper housing 282 from a second chamber 288, wherein, for example, the first chamber 282 is connected to the high-pressure inlet connection 34 via a first pulsation transmission line 292 and the second chamber 288 is connected to the high-pressure outlet 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 by transmitting the pulsations through the piston, wherein the piston 284 is preferably mounted between two spring-elastic damping elements 296 and 298 which are arranged in the chambers 286 and 288, respectively.
  • An eighth embodiment of an emergency operation unit 230′′′′′′′, shown in Fig. 11 and Fig. 12 is 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-way valve 235 which is able to either connect the expander outlet 94 to the expansion pressure outlet connection 36 and close the bypass line 234′′′′′′′ or to connect the bypass line 234′′′′′′ to the expansion pressure outlet connection 36 and close the expander outlet 94, wherein the 3/2-way valve 235 is also controlled by the controller 238, which, for example, detects 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 subcooling 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 subcooling unit 102 and thus the subcooling mass flow UM is branched off from the total mass flow G before flowing through the subcooling unit 102, wherein in the same way as in the preceding embodiments the shut-off element 124 and the expansion element 122 are provided, which are arranged between the branch 116′′′ and the inlet 112 for the counterflow flowing through the subcooling unit 102.
  • This embodiment of the expansion unit 32′′′ is also controlled by the controller 132 in the same way as in the first embodiment.
  • This fourth embodiment can also be provided with emergency operating units, for example with an emergency operating unit 230 according to the first embodiment, and the expansion element 232, designed as a pressure relief valve.
  • the expansion unit 32′′′ can also be provided with emergency operating units 230', 230", 230′′′, 230 ⁇ , 230 ⁇ ′, 230′′′′′′ and 230′′′′′′′ and/or with pulsation damper units 260, 280, as described in connection with the preceding embodiments of the refrigerant circuit 10, so that reference is made in this regard to the preceding statements on these emergency operating units.
  • a third embodiment of a refrigerant circuit 10 shown in Fig. 14 , those elements which are identical to those of the first embodiment are provided with the same reference numerals, so that with regard to the description, reference can be made in full to the statements made on these in connection with the first embodiment.
  • the third embodiment is provided with the third embodiment of the emergency operating unit 230", with regard to which reference is made to the above explanations of this third embodiment.
  • the expansion line 42 does not lead 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 via a liquid line 48 to the cooling stage 62", which in this case not only comprises the heat-absorbing heat exchanger 64, but also a shut-off element 68 and an expansion element 66.
  • 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 supplied to the suction line 74 via an expansion element 54.
  • the intermediate pressure collector 44 makes it possible to divide the expansion mass flow E at expansion pressure PE into a main mass flow H, which is fed to the cooling stage 62" via the liquid line, and a gaseous additional mass flow Z, which is fed to the suction pressure line 74 via the expansion element 54, so that the temperature of the main mass flow H reaching the cooling stage 62" can be adjusted by means of the expansion element 54.
  • a pulsation damper 260 is also assigned to the high-pressure discharge line 28, which in the first embodiment of the refrigerant circuit 10 according to Fig. 1 2 and associated with the expansion line 42, so that with regard to the function of the same, reference can be made in full to the above explanations.
  • the pulsation damper 260 can also be arranged in the area of the expansion unit 32 or even integrated into the expansion system 30.
  • a fourth embodiment of a refrigerant circuit 10''' shown in Fig. 15 which are identical to those of the first and second embodiments are provided with the same reference numerals, so that with regard to the description thereof, reference can be made in full to the statements on the first and second embodiments.
  • the fourth embodiment is provided with the pulsation damper unit 280, which in this embodiment is connected in parallel to 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 designed identically to the pulsation damper unit 280 integrated in the third embodiment of the expansion unit 32" ( Fig. 10 ), so that reference can be made in full to the above statements in this regard.
  • a throttle 302 is provided between the second pulsation transmission line 294 and the high-pressure line 18 in order to obtain an improved damping effect.
  • a refrigerant circuit 10 shown in Fig. 16 , those elements which are identical to those of the first and second embodiments are provided with the same reference numerals, so that with regard to the description thereof, reference can be made in full to the statements on the first and second embodiments.
  • 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 is again guided through a subcooler 58 provided in the liquid line 48, which again subcools the main mass flow H flowing in the liquid line 48.
  • the cooling stage 62′′′ is designed, for example, as a normal cooling stage and a deep-freezing stage 212 is additionally provided, which has a heat-absorbing heat exchanger 214 as well as a shutdown element 218 and an expansion element 216.
  • the refrigerant expanded in the deep-freeze stage 212 is fed via a suction pressure line 224 to a deep-freeze compressor unit 222, which compresses the refrigerant again 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 provided in the suction pressure line 224 of the deep-freeze compressor unit 212, which subcools the refrigerant supplied to the deep-freeze stage 212 via the liquid line 48 again before it enters the deep-freeze stage 212, namely by the expanded refrigerant emerging from the deep-freeze stage 212 and guided in the suction pressure line 224.
  • the solution describes the presence of the intermediate pressure collector 44 and also the supply of the additional mass flow Z via the expansion element 54 to the suction pressure line 74 as well as the control of the temperature of the main mass flow H.
  • This control of the temperature of the main mass flow H comprises the control 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 efficiency of the refrigerant circuit can be increased 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 can also be optimized with regard to the achievable COP, i.e. the ratio of cooling capacity to the mechanical power used, in particular in summer operation, and with regard to the extension of the functional operation of the expansion compression unit, in particular in winter operation, by additional operating state-dependent control of the intermediate pressure PM, which affects the inlet pressure EP of the compressor stage 88 due to the volume ratios of the expansion compression unit 84.
  • achievable COP i.e. the ratio of cooling capacity to the mechanical power used, in particular in summer operation
  • the extension of the functional operation of the expansion compression unit in particular in winter operation
  • the intermediate pressure PM is controlled by means of the intermediate pressure control 55 and the expansion element 54 to a pressure value which results on the one hand from a basic value which is usually set once and from additional values to this basic value which vary depending on the operating state.
  • the base 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 set as the base value, and the additional values for CO2 as a refrigerant have amounts in the range of 0.5 bar to 7 bar.
  • the surcharge values could be fixed values from the range of surcharge values provided for them, but it is particularly advantageous if the surcharge values vary within this range depending on the operating condition.
  • a differentiation is preferably made between summer operation and winter operation, with the surcharge values having positive values for summer operation and negative values for winter operation, so that the values, for example, for CO2 as a refrigerant are in the range of 0.5 bar to 7 bar for summer operation and in the range of -0.5 bar to -7 bar for winter operation.
  • the size of the additional values depends on the values within the control range of the high pressure PH2 and therefore varies depending on the values of the high pressure PH2.
  • the surcharge values are larger at high values of high pressure than at low values of high pressure.
  • additional values in the range of +0.5 bar to +3 bar result if the high pressure PH2 has values in the range of 75 bar to 80 bar, and additional values in the range of +3 bar to +7 bar if the high pressure PH2 has values in the range greater than 80 bar, preferably values greater than 80 bar to 120 bar.
  • the additional values for winter operation are, for example, in the range of -0.5 bar to -3 bar, provided that the high pressure PH2 is in the range of 55 bar to 65 bar, and the additional values are in the range of -3 bar to -5 bar, provided that the high pressure PH2 is in the range of less than 50 bar to 40 bar.
  • the base value is preferably always the same.
  • the inlet pressure EP at the compressor stage 88 increases and thus the subcooling mass flow UM and thus the subcooler capacity of the subcooling unit 102 is increased, so that the COP also increases.
  • the inlet pressure EP at the compressor stage 88 also decreases.
  • the pressure difference at the expander stage 86 is increased and thus the functional range of the expansion compression unit 84 is also increased.
  • the 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 size of the inlet pressure EP of the compressor stage 88 and controls the intermediate pressure PM depending thereon in order to regulate to a predetermined value of the inlet pressure EP suitable for the detected variables and stored, for example, in the intermediate pressure control 55.
  • 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 can be achieved 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 by controlling the speed of the compressor.
  • a power control which can be achieved 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 by controlling the speed of the compressor.

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Claims (16)

  1. Procédé destiné à faire fonctionner un circuit frigorifique (10), comprenant au moins un compresseur de fluide frigorigène (12), lequel comprime à haute pression (PH1) du fluide frigorigène amené sur un raccord d'aspiration (14) de telle sorte qu'un flux massique de compresseur (V), comprimé à haute pression (PH1), du fluide frigorigène sort sur un raccord de pression, au moins un échangeur de chaleur (22) côté haute pression libérant de la chaleur avec une entrée (24), à laquelle le circuit frigorifique (10) amène le flux massique de compresseur (V), et avec une sortie (26), de laquelle un flux massique total (G) refroidi de fluide frigorigène sort,
    au moins une unité d'expansion (32), comprenant une unité d'expansion et de compression (84) présentant un étage d'expanseur (86) et un étage de compresseur (88), laquelle expanse un flux massique d'expansion (EM), guidé par le circuit frigorifique (10) en direction du raccord d'aspiration (14) du compresseur de fluide frigorigène (14), du flux massique total (G) de haute pression (PH2) en partant d'une pression d'expansion (PE), et au moins un étage de refroidissement (62) avec au moins un échangeur de chaleur (64) d'absorption de chaleur, auquel le circuit frigorifique (10) amène un flux massique principal (H) compris par le flux massique de pression d'expansion (EM) expansé par l'unité d'expansion (32), et
    que le circuit frigorifique (10) amène, après qu'il a quitté l'étage de refroidissement (62), au raccord d'aspiration (14) du compresseur de fluide frigorigène (12),
    dans lequel est disposée dans le circuit frigorifique (10) une unité de fonctionnement de secours (230), laquelle comprend une conduite de contournement (234) contournant l'unité d'expansion et de compression (84) et à laquelle au moins un élément d'expansion (232, 122) est associé de manière fonctionnelle, caractérisé en ce que l'unité de fonctionnement de secours (230) est réalisée de telle sorte qu'elle détecte une anomalie d'expansion de l'unité d'expansion et de compression (84), que l'unité de fonctionnement de secours (230) présente une commande (238), qui transfère l'unité de fonctionnement de secours (230) de l'état inactif dans l'état actif, et que l'unité de fonctionnement de secours (230) est réalisée de telle sorte qu'elle passe, dans le cas d'une anomalie, en particulier d'une anomalie d'expansion, de l'unité d'expansion et de compression (84) d'un état inactif dans un état actif, dans lequel celle-ci génère, par expansion du fluide frigorigène sou haute pression au moyen de l'élément d'expansion (232, 122) un flux massique d'expansion de secours (NEPM), pour faire fonctionner l'étage de refroidissement (62), que la conduite de contournement (234) amène au circuit frigorifique (10) pour le transfert à l'étage de refroidissement (62).
  2. Procédé selon la revendication 1, caractérisé en ce que la conduite de contournement (234) de l'unité de fonctionnement de secours (230) amène directement ou indirectement le flux massique d'expansion de secours (NEPM) à une conduite d'expansion (42), recevant le flux massique de pression d'expansion (EPM), du circuit frigorifique (10).
  3. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que la conduite de contournement (234) amène le flux massique d'expansion de secours (NEPM) à une conduite du circuit frigorifique (10) guidant, lors du fonctionnement normal du circuit frigorifique (10) le flux massique de pression d'expansion (EPM) présent à une pression d'expansion (PE) .
  4. Procédé (10) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de fonctionnement de secours (230) détecte une haute pression (PH2) du flux massique total (G) sortant de la sortie (26) de l'échangeur de chaleur (22) ou du flux massique d'expansion (EM) avant son entrée dans l'étage d'expanseur (86).
  5. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de fonctionnement de secours (230) détecte une différence e pression entre la haute pression (PH2) du flux massique total (G) ou du flux massique d'expansion (EM) avant son entrée dans l'étage d'expanseur (86) et un tronçon d'acheminement (42), se trouvant à une pression d'expansion (PE), du circuit frigorifique (10).
  6. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de fonctionnement de secours (230) détecte une haute pression du flux massique totale (G) ou du flux massique d'expansion (EM) avant son entrée dans l'étage d'expanseur (86) quant à sa valeur absolue.
  7. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de fonctionnement de secours (230) compare la haute pression du flux massique total (G) ou du flux massique d'expansion (EM) avant son entrée dans l'étage d'expanseur (86) à une haute pression de référence.
  8. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de fonctionnement de secours (230) comprend au moins un élément de désactivation (235, 236, 237) destiné à désactiver l'unité d'expansion et de compression (84), qu'en particulier l'élément de désactivation (235, 236, 237) de l'unité de fonctionnement de secours (230) est disposé soit avant une entrée d'expanseur (92) soit après une sortie d'expanseur (94).
  9. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'est prévu dans la conduite de contournement (234) de l'unité de fonctionnement de secours (230) un élément de commutation (235, 237), lequel établit une liaison directe ou indirecte entre un organe d'expansion (122) pour générer le flux massique de sous-refroidissement (UM) de l'unité d'expansion (32) et un raccord de sortie de pression d'expansion (36) de l'unité d'expansion (32), qu'en particulier l'élément de commutation peut être piloté par la commande (238) de l'unité de fonctionnement de secours (230), qu'en particulier l'élément de commutation est une soupape de commutation, qu'en particulier l'élément de commutation (235) est une soupape à 3/2 voies, laquelle relie soit la conduite de contournement (234) soit une sortie d'expanseur au raccord de sortie de pression d'expansion (36).
  10. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'est disposé entre l'unité d'expansion (32) et l'étage de refroidissement (62) un collecteur de pression intermédiaire (44), dans le bain (46) duquel une phase liquide du fluide frigorigène s'accumule et dans le volume de gaz (52) duquel au-dessus du bain (46) s'accumule la phase gazeuse du fluide frigorigène, qu'en particulier un flux massique supplémentaire (Z) est évacué en particulier du volume de gaz (52) du collecteur de pression intermédiaire (44), qu'en particulier le flux massique supplémentaire (Z) est amené à la conduite de pression d'aspiration (74) par l'intermédiaire d'un organe d'expansion (54), qu'en particulier le flux massique supplémentaire (Z) expansé par l'organe d'expansion (54) refroidit un flux massique principal (H) guidé vers l'étage de refroidissement (62) dans un échangeur de chaleur (58).
  11. Procédé selon la revendication 10, caractérisé en ce qu'une commande de pression intermédiaire (55) pilotant l'organe d'expansion (54) détecte la pression et/ou la température du flux massique total (G) dans la conduite d'évacuation de haute pression (28) ainsi que la pression d'entrée (EP) de l'étage de compresseur (88) et commande la pression intermédiaire (PM) de telle sorte qu'une valeur spécifiée, adaptée pour les grandeurs détectées, de la pression d'entrée (EP) est réglée.
  12. Procédé selon la revendication 10 ou 11, caractérisé en ce qu'est régulée, au moyen d'une commande de pression intermédiaire (55) pilotant l'organe d'expansion (54), une pression intermédiaire (PM) dans le collecteur de pression intermédiaire (44) sur une valeur de pression, qui est déterminée à partir d'une valeur de base, par exemple d'une valeur dans la plage de 30 bar à 45 bar, et de valeurs de majoration avec des montants, par exemple dans la plage de 0,5 bar à 7 bar, par la commande de pression intermédiaire (55), qu'en particulier les valeurs de majoration présentent lors du fonctionnement en état des valeurs positives et, lors du fonctionnement en hiver, des valeurs négatives, qu'en particulier la grandeur des valeurs de majoration dépendant des valeurs, se réglant lors de la régulation de la haute pression de la haute pression, qu'en particulier lors du fonctionnement en état, les valeurs de majoration sont, pour des valeurs élevées de la haute pression (PH2), supérieures à celles en cas de valeurs basses de la haute pression (PH2), qu'en particulier lors du fonctionnement en hiver, les valeurs de majoration sont, dans le cas de valeurs élevées de la haute pression (PH2), inférieures à celles dans le cas de valeurs basses de la haute pression (PH2).
  13. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité d'expansion (32) comprend un système d'expansion (30), lequel présente une unité de sous-refroidissement (102) pour sous-refroidir le flux massique total, amené à l'unité d'expansion (32), du fluide frigorigène, l'unité d'expansion et de compression (84) comprenant l'étage d'expanseur (86) et l'étage de compresseur (88), un embranchement (116), qui fait bifurquer un flux massique de sous-refroidissement (UM) du flux massique total (G) amené à l'unité d'expansion (32) et est relié à une conduite d'arrivée (126), qui guide le flux massique de sous-refroidissement (UM) à une entrée (112) de l'unité de sous-refroidissement (102), présente un organe d'expansion (122, 124) prévu dans la conduite d'arrivée (126), lequel expanse le flux massique de sous-refroidissement (UM) sur une pression de sous-refroidissement (PU), et une conduite de liaison (128), qui amène le flux massique de sous-refroidissement (U) sortant de l'unité de sous-refroidissement (102) à l'étage de compresseur (88), qui comprime à son tour le flux massique de sous-refroidissement (U) sur une haute pression de guidage de retour (PR), qui correspond au moins à une haute pression (PH1) du flux massique de compresseur (V), auquel le flux massique de sous-refroidissement (U) est amené.
  14. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que le circuit frigorifique (10) présente une commande (132, 138) à fonctionnement électrique, laquelle détecte au moins une des grandeurs suivantes comme une température ambiante, une température du flux massique du fluide frigorigène amené à l'unité d'expansion (32) et/ou à l'étage d'expanseur (86) et une pression d'entrée (EP) de l'étage compresseur (88) et règle, conformément à ladite température et/ou éventuellement à ladite pression d'entrée (EP) de l'étage de compresseur (88), une pression d'entrée de l'unité d'expansion (32) ou de l'étage d'expanseur (86) et/ou éventuellement une pression d'entrée (EP) de l'étage de compresseur (88) par la commande du flux massique de sous-refroidissement (UM) au moyen de l'organe d'expansion (122) piloté de manière électrique par la commande (132, 138), qu'en particulier la commande (132, 138) mesure au moyen d'un capteur (134) la température ambiante et/ou la température du flux massique du fluide frigorigène avant une entrée (104) de l'unité de sous-refroidissement (102) et/ou avant une entrée d'expanseur (92), qu'en particulier la commande (132, 138) est une commande (132, 138) électronique comprenant un processeur, qui pilote électriquement l'organe d'expansion (122) au moyen d'un programme de commande, qu'en particulier l'embranchement (116) est disposé entre l'unité de sous-refroidissement (102) et l'unité d'expansion et de compression (84), et fait bifurquer après l'unité de sous-refroidissement (102) le flux massique de sous-refroidissement (U) du flux massique total (G), qu'en particulier l'unité de sous-refroidissement (102) est réalisée en tant qu'échangeur de chaleur et refroidit le flux massique, circulant vers l'expanseur (86), du fluide frigorigène par le flux massique de sous-refroidissement U guidé à contre-courant par celle-ci.
  15. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'étage d'expanseur (86) et l'étage de compresseur (88) de l'unité d'expansion et de compression (84) sont couplés de manière fonctionnelle mécaniquement.
  16. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'étage d'expanseur (86) et l'étage de compresseur (88) sont formés par une machine à pistons libres, dans laquelle au moins un piston libre (152, 154) peut être déplacé librement dans une chambre de piston (144, 146), qu'en particulier l'unité d'expansion et de compression (84) présente deux chambres de piston (144, 146), dans lesquelles respectivement un piston libre (152, 154) peut être déplacé.
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US11421918B2 (en) 2020-07-10 2022-08-23 Energy Recovery, Inc. Refrigeration system with high speed rotary pressure exchanger
US12007154B2 (en) 2021-06-09 2024-06-11 Energy Recovery, Inc. Heat pump systems with pressure exchangers
US12209778B2 (en) 2021-06-09 2025-01-28 Energy Recovery, Inc. Refrigeration and heat pump systems with pressure exchangers
CN113865133B (zh) * 2021-09-17 2022-08-23 珠海格力电器股份有限公司 一种空调系统及其控制方法
WO2024186836A2 (fr) * 2023-03-06 2024-09-12 Energy Recovery, Inc. Systèmes de réfrigération comprenant des échangeurs de pression et leur commande
WO2025085849A1 (fr) * 2023-10-20 2025-04-24 Energy Recovery, Inc. Systèmes comprenant des échangeurs de pression et procédés faisant appel à des échangeurs de pression
US20250146725A1 (en) * 2023-11-02 2025-05-08 Heatcraft Refrigeration Products Llc Refrigeration System with Expander-Assisted Cooling and Methods of Use

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WO2009104375A1 (fr) * 2008-02-20 2009-08-27 パナソニック株式会社 Dispositif de cycle de réfrigération
US8726677B2 (en) * 2009-04-01 2014-05-20 Linum Systems Ltd. Waste heat air conditioning system
WO2010140324A1 (fr) * 2009-06-02 2010-12-09 三菱電機株式会社 Dispositif à cycle de réfrigération
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DE102015214705A1 (de) * 2015-07-31 2017-02-02 Technische Universität Dresden Vorrichtung und Verfahren zum Durchführen eines Kaltdampfprozesses
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EP3830500B1 (fr) 2025-01-08
EP3830499A1 (fr) 2021-06-09

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