ARRANGEMENT FOR GENERATING HEAT AND COLD

Abstract

An arrangement for generating heat and cold relates to the field of energy production and can be used in gas compression and expansion devices in order to improve the efficiency of gas expansion and compression systems. The arrangement comprises a cascade pressure exchanger, a supply port for low-pressure working fluid, which is connected by a pressurizing device to a source of heat energy, and a discharge port for low-pressure working fluid from the cascade pressure exchanger. A supply port for high-pressure working fluid is connected, via a heat discharge device linked to a heat user, to an outlet of a compressor that compresses working fluid, an inlet of which is connected to the source of heat. A discharge port for high-pressure working fluid is connected, via the beat discharge device linked to a heat user, to the supply port for high-pressure working fluid by means of a circulating fan.

Description

The invention relates to the field of energy, in particular to the field of power engineering, and can be used in gas compression and expansion devices, in expander-compressors, in refrigeration and cryogenic units, in heat pumps, in gas liquefaction plants, in air separation plants, in gas separation plants, in power plants, including steam plants, gas turbine plants and combined cycle plants.

There is a cold generator based on a wave pressure exchanger, made in the form of an expander-compressor of a cryogenic installation. “Results of experimental studies of a cryogenic wave expander-compressor”, A. M. Arkharov and others, Bulletin of the Moscow State Technical University named after N. E. Bauman. Issue “Mechanical engineering”. 2010

The disadvantage of this design is low efficiency, low degree of pressure increase and poor performance, complexity and narrow extent of applicability.

There is an air refrigeration unit of cascade pressure exchange, including cascade pressure exchangers with a drive, purge fans and heat exchangers. “Air refrigeration unit of cascade pressure exchange” A. I. Krainyuk. O. V. Klyus, Zeszyty Naukowe, Akademia Morska w Szczecinie, 2012. 32(104) z. 1 s. 5-11

The disadvantages of this design are low efficiency and poor performance, as well as a narrow extent of applicability.

The technical result achieved in this invention is to increase the efficiency of gas expansion and compression systems based on pressure exchangers, including expander-compressors, as well as to expand the extent of applicability and to simplify the design of refrigeration units and heat pumps, engines and power plants based on them.

The specified technical result is achieved by the fact, that an arrangement for generating heat and cold, containing at least one compressor or fan, at least one heat exchanger, at least one pressure exchanger, as well as regulation, protection, operating, start-up, control systems, differs in that this arrangement contains at least one cascade pressure exchanger, the channels in the rotor of which are built axially (parallel to the shaft), or radially, or diagonally, or axial-radially, with the possibility of periodically overlapping the inlet and outlet openings of the channels of the rotor, as the rotor rotates, by the housing walls and their periodic combination with the low- and high-pressure working fluid supply and discharge ports, while the supply port of the compressible low-pressure working fluid is connected by a pipeline, for example, by means of a pressurization device in the form of a fan or compressor directly, or by means of a heat exchanger, for example, to a source of thermal energy: to a cooled medium, or to the atmosphere, or to a refrigeration, or to a cryogenic chamber, to the liquefied or cooled gas or steam, the low-pressure working fluid discharge port of the cascade pressure exchanger is connected directly or through a heat exchanger to a user of refrigeration, for example, to the atmosphere, or to a refrigeration, or to a cryogenic chamber, to the liquefied or cooled gas and/or steam, the high-pressure working fluid supply port, through a heat removal device, possibly connected to a heat user through a heat exchanger-cooler, possibly with a condensate separator, can be connected to the outlet of the compressing working fluid from the compressor, the inlet of which is connected to a heat source, directly or by means of a heat exchanger, for example, to the atmosphere or to a refrigeration, or to a cryogenic chamber, to the cooled or liquefied gas and/or steam, on the side of heat removal, and the high-pressure working fluid discharge port, for example, through a heat removal device, possibly connected to the heat user through a heat exchanger-cooler, possibly with a condensate separator, is connected, by means of a circulation fan, to the high-pressure working fluid supply port of a cascade pressure exchanger, a part of the ports of which are interconnected by bypass-mass transfer channels built from the side of the low-pressure working fluid supply port or the discharge port, or at least a part of the bypass channels is built from the side of the supply port, and a part of them is built from the low-pressure working fluid discharge port, while the bypass-mass transfer channels of the cascade pressure exchanger, or at least some of them, for example, the high-pressure ones, are built in a heat supply device, for example, in the form of a heat exchanger, connected from the heating side to a source of thermal energy, for example, to the environment or to a refrigeration, or to a cryogenic chamber, or to a cooled gas and/or steam, while the heating medium can be supplied to the heat exchanger from the side of the high-pressure working fluid supply port, and the heating medium can be removed from the side of the low-pressure working fluid supply port of the cascade pressure exchanger.

In addition, the arrangement differs in that in the housing of the pressure exchanger, on the opposite side to at least a part of the bypass-mass transfer channels there are ports connected to each other in pairs by outlet channels built into the heat exchanger with the possibility of supplying heat to the working fluid—gas or steam—filling the outlet channels, while the ports are built with the possibility of periodic alignment, along the direction of rotation of the rotor, with channels built in it in such a way that the first port along the direction of rotation of the rotor is aligned with the channel in the rotor, for example, filled with the working fluid—gas or steam of the highest pressure, with that rotor being blocked on its opposite side by the housing wall, with the possibility of expansion of gas or steam in it into the outlet channel, further connected, in the direction of rotation of the rotor, with a channel in the rotor, with the possibility of displacing the working fluid—gas or steam—in it into the bypass-mass transfer channel, while further, in the direction of rotation of the rotor, at least one more outlet channel can be built.

In addition, the arrangement differs in that the low-pressure working fluid discharge port of the cascade pressure exchanger is connected to a liquefied gas or steam separator, or a mixture of gases or steams through the expansion device, for example, through a throttle valve, possibly after an additional cooler, while the discharge of non-condensed gas or steam or mixture and, for example, the supply of liquefied gas or steam, or a mixture of gases or steams, is connected to the inlet of a low-pressure fan or compressor, the outlet of which is connected to the supply port of the low-pressure working fluid of the pressure exchanger, as well as the release of non-condensed gas or steam, or mixture from the condensate separator and, for example, the supply of liquefied gas or steam, or a mixture of gases or steams, is connected to a compressor of a compressing working fluid, the outlet of which is connected, for example, through a heat exchanger-cooler, to the high-pressure working fluid supply port of the pressure exchanger.

In addition, the arrangement differs in that the low-pressure working fluid discharge port of the pressure exchanger is connected, possibly through a throttle valve, for example after an additional cooler, to a heat exchanger, which can be built in the form of an evaporator with the possibility of removing heat from the cooled medium, for example, liquid, steam or gas, as a result of boiling and evaporation of a refrigerant or a mixture of refrigerants circulating in the arrangement in the form of a working fluid or a mixture of working fluids.

In addition, the arrangement differs in that at least one outlet channel and/or one bypass (mass transfer) channel, starting from the outlet and/or the bypass channel, filled with gas or steam with the highest pressure, or at least a part of the channels is connected in series to the source of the heat supply by means of the counterflow heat exchanger, as the coolant temperature and gas and/or steam pressure in the outlet channels and/or in the bypass-mass transfer channels decrease.

In addition, the arrangement differs in that the heat exchanger with outlet channels and/or bypass channels built into it is connected to a heat source, for example, to the outlet of gas and/or steam from the compressor of the compressing working fluid or to the outlet of gas and/or steam from the high-pressure working fluid discharge port of the cascade pressure exchanger, possibly through a circulation fan, or simultaneously connected to the outlet from the compressor and the high-pressure working fluid discharge port, while the outlet of the cooled gas and/or steam from the heat exchanger with built-in outlet and/or bypass channels is connected to the high-pressure working fluid supply port of the cascade pressure exchanger.

In addition, the arrangement differs in that the heat exchanger with outlet and/or bypass channels built into it is connected to the heat source through an intermediate heat carrier, for example, liquid, while the heat source can be the environment, for example a reservoir or a heat exchanger-cooler.

In addition, the arrangement differs in that as a working fluid it contains a mixture of at least two refrigerants with different temperatures and condensing pressures, while the outlet of the compressing working fluid from the compressor and the outlet of the high-pressure pressure working fluid from the discharge port of the pressure exchanger, for example, through a circulation fan, is connected to at least one heat exchanger-cooler with a low-boiling refrigerant condensate separator, while the outlet of the non-condensed working fluid—readily boiling refrigerant—from the condensate separator is connected to the high-pressure working fluid supply port of the pressure exchanger, and the outlet of the liquefied refrigerant from the condensate separator is connected, for example through an additional cooler, to a throttle valve, the outlet from which is connected to the user of refrigeration, for example, to the heat exchanger of the cooled and/or liquefied gas or steam, and the low-pressure working fluid discharge port of the pressure exchanger is also connected to the user of refrigeration, for example, in a more or less high-temperature part of the cooling heat exchanger of the cooled and/or liquefied gas or steam.

In addition, the arrangement differs in that the outlet of the liquefied refrigerant from the condensate separator connected to the heat exchanger-cooler built in the gas path at the outlet of the working fluid mixture from the high-pressure working fluid discharge port of the pressure exchanger is connected to the expansion device, for example the throttle valve, by means of a pump.

In addition, the arrangement differs in that part of the flow of the working fluid-gas or steam from the compressor of the compressing working fluid, and/or from the high-pressure working fluid discharge port of the pressure exchanger, after at least one heat exchanger-cooler, is connected, for example, through an additional cooler, to a throttle valve, the outlet of which is connected to the user of refrigeration, for example, to the heat exchanger of the cooled and/or liquefied gas or steam, and the low-pressure working fluid discharge port of the pressure exchanger is also connected to the user of refrigeration, for example in a more or less high-temperature part of the same cooling heat exchanger of the cooled and/or liquefied gas or steam.

In addition, the arrangement differs in that the walls of the housing of the cascade pressure exchanger, located between the ports for supplying the working fluid to the channels and discharging the working fluid from the channels built in the rotor, with the said ports built in the housing, are built with the possibility of overlapping the inlet and outlet openings, while the rotor is rotating, with a minimum gap in which labyrinth or contact seals are installed, of at least one channel in a row of the channels of the rotor, meanwhile several rows of channels, at least two rows, can be built in the rotor of the cascade pressure exchanger along its radius.

In addition, the arrangement differs in that the rotor shaft of the pressure exchanger is connected to an engine drive with the ability to control the rotor speed and/or the rotor is built with the possibility of self-rotation, for example, through special nozzles built in separate ports for supplying the working fluid to the channels of the rotor, for example, also with the ability to control the rotor speed, meanwhile the housing of the pressure exchanger can be made hermetic.

In addition, the arrangement differs in that in the walls of the housing of the cascade pressure exchanger, opposite to at least a part of the channels in the rotor which are fully or partially combined with windows on the opposite side, with said windows being connected to bypass-mass transfer channels, with the possibility of increasing the pressure in these channels of the rotor, and possibly partially opposite to the high-pressure working fluid supply port of the cascade pressure exchanger, nozzles are built for injection of the coolant under the pressure into the channels, and they are connected directly or through a pump to the coolant source, for example to a condensate collector of at least one of the condensate separator, while the coolant can be water or at least one of the refrigerants in a liquid state circulating in the arrangement, at least in part of the cycle.

In addition, the arrangement differs in that in the walls of the housing of the cascade pressure exchanger, opposite to at least a part of the channels in the rotor which are fully or partially combined with windows on the opposite side, with said windows being connected to bypass-mass transfer channels, with the possibility of reducing the pressure in these channels of the rotor, nozzles are built for injection of the heating medium under the pressure into the channels, for example, the pre-evaporated and heated liquid, for example water or liquefied refrigerant, and these nozzles are connected, for example, through a pump, to a source of heating liquid, for example, in the form of a reservoir, in the form of a waste heat boiler, in the form of a compressed gas cooler with separation of hot condensate and so on, meanwhile a heating liquid separator, for example for water, can be built at the outlet of the low-pressure working fluid discharge port of the cascade pressure exchanger.

In addition, the arrangement differs in that it contains a cascade of arrangements, connected in series to the heat exchangers: for pre-cooling and/or liquefying and/or sub-cooling of gas and/or steam, as it cools, and these arrangements have, for example, various refrigerants or mixtures of refrigerants as working fluids, for example, at first as gas or a mixture of gases cools or liquefies with a low-boiling refrigerants, and then with more readily boiling ones, while recuperative heat exchangers connected to refrigerant circulation circuits and separators built with the possibility of extracting low-boiling gases from the flow of the cooled mixture of gases can be installed between the cascades.

In addition, the arrangement differs in that the inlet of the compressed working fluid in front of the high-pressure working fluid supply port of the pressure exchanger is built in a heat removal device, for example, in the form of a heat exchanger connected to a source of refrigeration.

The drawings show

FIG. 1. An Arrangement for generating heat and cold as an air refrigeration unit and/or a heat pump. A development drawing of a quasi-isothermal cascade pressure exchanger is shown.

FIG. 2. An Arrangement for generating heat and cold as a hybrid combined cycle refrigeration unit. A development drawing of the cascade pressure exchange is shown.

FIG. 3. An Arrangement for generating heat and cold with three cooling cascades—pre-cooling, liquefaction and sup-cooling of liquefied gas.

FIG. 4. An Arrangement for generating heat and cold as a hybrid combined cycle compression plant for cooling or liquefying gases. A development drawing of a quasi-isothermal cascade pressure exchanger is shown.

FIG. 5. An Arrangement for generating heat and cold as a hybrid combined cycle plant for cooling or liquefying gases. A development drawing of a quasi-isothermal cascade pressure exchanger is shown.

FIG. 6. An Arrangement for generating heat and cold as a gas liquefaction plant. A development drawing of a quasi-isothermal cascade pressure exchanger is shown.

FIG. 7. An Arrangement for generating heat and cold as a refrigeration and/or heat pump unit. A development drawing of a quasi-isothermal cascade pressure exchanger is shown.

The Arrangement for generating heat and cold contains a pressurization (purge) system for a compressible working fluid, for example, in the form of a fan 1 or a low-pressure compressor, and the compressor of the compressing working fluid 2 that are connected to the heat source from the inlet side, while the outlet from the fan 1 is connected to the low-pressure working fluid supply port 3 of the cascade pressure exchanger 4, and the outlet from the compressor of the compressing working fluid 2 is connected, for example through a heat removal device, for example in the form of a heat exchanger-cooler 5, for example with a condensate separator 6 to the high-pressure working fluid supply port 7 of the pressure exchanger 4, the low-pressure working fluid discharge port 8 of the pressure exchanger 4 is connected to the user of refrigeration, the high-pressure working fluid discharge port 9 of the pressure exchanger 4 is connected, for example, through a cooler 5 with a condensate separator 6 and through a circulation fan 10 to the high-pressure working fluid supply port 7 of the pressure exchanger 4, which may contain the ports connected to each other by bypass (mass transfer) channels 11, and possibly by discharge channels 12, while the bypass channels 11 can be built in in the heat exchanger 13, with the possibility of supplying heat to them, it can also contain a device for injecting coolant 14 into the channels of the rotor, pump 15, motor 16, rotor speed control device 17 of the pressure exchanger 4, shut off control valves 18, which may contain a throttle valve 19, liquefied gas separator 20, cooling heat exchanger 21, low-temperature cooling heat exchanger 22, heat supply heat exchanger 23, heat exchanger 24 with the possibility of supplying heat to the discharge channels 12, air filter 25, heat exchanger-recuperator 26, first cooling cascade 27, second cooling cascade 28, third cooling cascade 29, pre-cooling heat exchanger 30.

The arrangement for generating heat and cold works in the following way.

When operating the arrangement as an air refrigeration unit and/or a heat pump (FIG. 1), a compressible gas is supplied to the inlet of the fan 1 of the pressurization system and the compressor of the compressing working fluid 2, in this case air, for example from the cooled room, or from the refrigeration chamber in a refrigerator, or from the atmosphere in a heat pump. Air from fan 1 is divided into two parts. One part of the air is supplied to the heat exchanger 13 with the possibility of supplying heat to the bypass channels 11 and is cooled in it, giving off beat to the air expanding in the bypass channels 11. After that, the air cooled in the heat exchanger 13 is supplied to the user of refrigeration (not shown in the drawing), or into the atmosphere, and the other part of the air from the fan 1 enters the low-pressure working fluid supply port 3 of the cascade pressure exchanger 4 and is compressed in it while rotating the rotor. Another part of the cooled air is compressed in the compressor of the compressing working fluid 2 after compression in which the air is cooled in the heat exchanger-cooler 5, at the same time, water condensate is separated from it in the condensate separator 6, after which air is supplied to the high-pressure working fluid supply port 7 of the cascade pressure exchanger 4. compressing the air in the channels of the rotor and pushing it into the discharge port of the high pressure working fluid 9, after leaving which the air is cooled in the heat exchanger-cooler 5, and in the condensate separator 6 water condensate is separated from it. After that, air, by means of a circulation fan 10, is supplied to the high-pressure working fluid supply port 7 of the cascade pressure exchanger 4 compressing the air in the channels of the rotor. When the rotor of the pressure exchanger rotates 4, the compressing air expands in the channels of the rotor and in bypass channels 11 at the same time, the compressing air cools itself and while expanding, cools the air filling the heat exchanger 13. Further, when the rotor channels are aligned with the discharge port of the low-pressure working fluid 8, cold air is pushed out to the user of refrigeration, for example, in the form of a cooled room, or a refrigeration chamber in a refrigerator, or is released into the atmosphere, for example, in heat pump. At the same time, when the unit is operating as a heat pump, the heat from the heat exchangers-coolers 5 is supplied to the heat user. The supply of heat through the heat exchanger 13 to the air expanding in the bypass channels 11 increases the coefficient of performance of the refrigeration unit, as well as the coefficient of heat conversion in the heat pump, as a result of heat removal from the cooled air in the heat exchanger 13, with the conversion of this heat into the compression work in the cascade pressure exchanger 4. This increases the amount of air compressed in the cascade pressure exchanger 4, accordingly, the efficiency and cooling capacity of the unit increases, and an increase in the air temperature at the outlet of the low-pressure working fluid discharge port 8 reduces excessive air subcooling, which also increases the coefficient of performance of the unit.

The arrangement can use a mixture of at least two working fluids (refrigerants)—low-boiling and readily boiling (FIG. 2). After compressing the mixture of working fluids in the compressor of the compressing working fluid 2 and in the pressure exchanger 4, the mixture of refrigerants is cooled in the heat exchangers-coolers 5, and in the condensate separators 6 the low-boiling refrigerant condensate is separated from the mixture, and this condensate, partially with the help of a pump 15, is supplied into the cooling heat exchanger 21, in which it is additionally cooled, then it enters the throttle valve 19, in which the low-boiling refrigerant expands and is supplied into the cooling heat exchanger 21, where it boils, extracting beat from the user of refrigeration. Meanwhile, the discharge port of the low-pressure working fluid 8 of the pressure exchanger 4 is connected, first, to the low-temperature cooling heat exchanger 22, in which the readily boiling refrigerant is heated, removing heat from the user of refrigeration, after which it is supplied into a less low-temperature cooling exchanger 21, in which the readily boiling refrigerant heats up again, taking heat from the user of refrigeration. Meanwhile, the readily boiling refrigerant can also be additionally cooled before entering the high-pressure working fluid supply port 7, for example in the cooling heat exchanger 21 or in a separate refrigeration machine (not shown in the drawings). The refrigerants heated in the cooling heat exchanger 21, in the gaseous state, enter the inlet of the fan 1 and the compressor of the compressing working fluid 2, and the cycle is repeated.

The arrangement for generating heat and cold may contain several, for example, three cooling cascades (FIG. 3). As a result, in the first cooling cascade 27 and in the second cooling cascade 28, compressor 2 compresses, for example, methane as a working fluid and refrigerant. At the same time, in the first cooling cascade 27, the refrigerant methane, circulating in the cascade pressure exchanger 4, cools the gas in the pre-cooling heat exchanger 30. In the second cooling cascade, the refrigerant methane cools the gas in the cooling heat exchanger 21, in which the cooled gas is cooled and, for example, liquefied. The third cooling cascade 29 uses, for example, nitrogen as a refrigerant, which cools or sub-cools the gas in a low-temperature heat exchanger 22.

When using the arrangement for generating heat and cold unit as a hybrid combined cycle compression unit for cooling or liquefying gases (FIG. 4), the unit can use a mixture of at least two working fluids (refrigerants), low-boiling and readily boiling (for example, ethane and methane). After the mixture of working fluids is compressed in the compressor of the compressing working fluid 2 and in the cascade pressure exchanger 4, the mixture of refrigerants is cooled in the heat exchangers coolers 5, and in the condensate separators 6, the low-boiling refrigerant condensate is separated from the mixture. After that, the readily boiling refrigerant is supplied to the high-pressure working fluid supply port 7 of the (cascade) pressure exchanger, and a liquefied low-boiling refrigerant, for example, partially with the help of a pump 15, is supplied into the heat exchanger 13 with the possibility of supplying heat to the bypass channels 11, in which it is additionally cooled, then enters the throttle valve 19, in which the low-boiling refrigerant is expanded and supplied into the low-temperature cooling heat exchanger 22, where it boils, removing heat from the cooled and/or liquefied gas (the user of refrigeration). Wherein, this discharge port of the low-pressure working fluid 8 of the pressure exchanger 4 is connected, for example, in a higher-temperature part to the low-temperature cooling heat exchanger 22, in which the readily boiling refrigerant is heated, removing heat from the user of refrigeration, after which the mixture of refrigerants is supplied into a less low-temperature cooling heat exchanger 21, in which the mixture of refrigerants heats up again, removing heat from the cooled gas (the user of refrigeration). Low-boiling fractions can be separated from the cooled essence cooled in the heat exchanger 21, for example, raw natural gas, before it is supplied into the low-temperature heat exchanger 22. Further, the refrigerants heated in the cooling heat exchanger 21, in the gaseous state, enter the inlets of the fan 1 and the compressor of the compressing working fluid 2, and the cycle is repeated.

In the arrangement option, as a hybrid combined cycle compression plant for cooling (liquefying) gases (FIG. 5), the entire volume of the mixture of refrigerants enters into the heat exchanger 13 with the possibility of supplying heat to the bypass channels 11 and is cooled in it. Meanwhile, a part of the mixture compressed in the compressor of the compressing working fluid 2 can be pre-cooled in the heat exchanger-cooler 5. At the outlet of the heat exchanger 13 with the possibility of supplying heat to bypass channels 11, the refrigerant mixture is supplied into the condensate separator 6, in which a readily boiling refrigerant is separated from it and is supplied to the high-pressure working fluid supply port 7 of the cascade pressure exchanger 4, and the low-boiling refrigerant is supplied into the low-temperature heat exchanger 22, additionally cooled in it and enters the throttle valve 19, through which it expands into a low-temperature heat exchanger 22. In addition, a liquefied low-boiling refrigerant, such as isobutane, isopentane or propane or mixtures thereof, is injected through the coolant injection device into the channels of the rotor 14, reducing the flow of working fluids through the compressor of the compressing working fluid 2. The low-boiling refrigerant evaporated in the low-temperature heat exchanger 22 is supplied to the less low-temperature heat exchanger 21, in which the readily boiling refrigerant is also supplied from the discharge port of the low-pressure working fluid 8 of the cascade pressure exchanger 4. After that, the cycle is repeated.

When operating the arrangement as a gas liquefaction unit (FIG. 6), liquefied gas is supplied to the inlet of the fan 1 and the compressor of the compressing working fluid 2. After compression, part of the gas is cooled in the heat exchanger-cooler 5, and a part can be cooled in the heat exchanger 13 with the possibility of supplying heat to the bypass channels 11, after which the compressed gas is supplied to the high-pressure working fluid supply port 7 of the cascade pressure exchanger 4 and expands in it. Before this, low-boiling fractions can be removed from the gas in the condensate separator (not shown in the drawings). After expansion in the cascade pressure exchanger 4, the two-phase medium can be directly supplied into the liquefied gas separator 20, meanwhile, the channels in the rotor can be built diagonally to the shaft (not shown in the drawings). The gas leaving the discharge port 8 of the working fluid can be additionally pre-cooled, then the gas expands in the throttle valve 19, from which the two-phase medium is supplied to the separator of liquefied gas 20, from where the liquefied gas is supplied to the user, and the non-condensed gas again enters the inlet of the fan 1 of the pressurization system (or low pressure compressor) and the compressor of the compressing working fluid 2, after which the cycle is repeated.

A arrangement, for example, in the form of a refrigeration or heat pump unit (FIG. 7), may contain ports in the case of a cascade pressure exchanger 4 on the opposite side of at least parts of the bypass channels 11, and these ports are connected in pairs by outlet channels 12 built in in a heat exchanger with the possibility of supplying heat to the outlet channels 24, to the gas and/or steam filling the outlet channels 12, meanwhile, during the rotation of the rotor, the first port after the discharge port of the high-pressure working fluid 9, along the rotation of the rotor, is aligned with the channel (channels) in rotor, for example, filled with gas or steam of the highest pressure and blocked by the housing wall on the opposite side, while the gas or steam in it expands into the outlet channel 12, heats up in the heat exchanger 24 with the possibility of supplying heat to the outlet channels 12 and displaces gas or steam from the rotor channel connected to the bypass channel 11. The gas or steam compressed in the cascade pressure exchanger 4 is cooled during the compression process by means of a coolant injection device 14 into the rotor channels, then it is cooled in the heat exchanger-cooler 5 connected to the heat user, and the gas or steam compressed in the compressing gas compressor 2 is cooled in the heat exchanger-cooler 5, also giving off heat to a heat user, for example in a heat pump. At the same time, a part of the cooled medium is cooled in the heat exchanger 13 with the possibility of supplying heat to the bypass channels 11 and in the heat exchanger 24 with the possibility of supplying heat to the outlet channels 12, increasing the efficiency and productivity of the installation. The gas or steam expanded in the cascade pressure exchanger is supplied from the low-pressure working fluid discharge port 8 to the heat supply heat exchanger 23, where it is supplied with heat from the cooled medium, after which the gas or steam is again supplied to the inputs of the fan 1 of the pressurization system and the compressor of the compressing working fluid 2. Meanwhile, each bypass channel 11, or a part of the channels 11, and, possibly, at least a part of the outlet channels 12, for example, by means of a countercurrent heat exchanger 13 and a heat exchanger 24, can be connected in series, as the temperature of the heat carrier and the pressure of gas or steam in the bypass 11 and outlet 12 channels to a heat supply source, for example from the cooled medium.

In the walls of the housing of the cascade pressure exchanger 4, opposite to the channels in the rotor which are fully or partially combined with windows on the opposite side, with said windows being connected to bypass (mass transfer) channels 11, with the possibility of reducing the pressure in these channels of the rotor, nozzles can be built for injection of the heating medium under the pressure into the channels, for example, in the form of a pre-evaporated liquid, such as water, and these nozzles are connected, for example, through a pump, to a source of heating liquid (not shown in the drawings). At the same time, the pre-evaporated heating liquid gives off heat to gas or steam, and, possibly, additionally compresses it in the channels of the rotor of the cascade pressure exchanger 4 in the process of its expansion (quasi-isothermal process), which increases the power and efficiency of the installation.

The use of this invention will allow the development of highly efficient installations for generating heat and cold, including refrigeration and cryogenic installations, heat pumps, heating and air conditioning systems, air separation plants, installations for the liquefaction of various gases, as well as highly efficient devices for compressing and expanding gas, etc.

Claims

1. An arrangement for generating heat and cold, containing at least one compressor or fan, at least one heat exchanger, at least one pressure exchanger, as well as regulation, protection, operating, start-up, control systems, wherein the at least one cascade pressure exchanger is contained, the channels in the rotor of which are built axially-parallel to the shaft, or radially, or diagonally, or axial-radially, with the possibility of periodically overlapping the inlet and outlet openings of the channels of the rotor, as the rotor rotates, by the housing walls and their periodic combination with the low-pressure and high-pressure working fluid supply and discharge ports, while the supply port of the compressible low-pressure working fluid is connected by a pipeline, for example, by means of a pressurization device in the form of a fan or compressor directly, or by means of a heat exchanger, for example, to a source of thermal energy: to a cooled medium, or to the atmosphere, or to a refrigeration, or to a cryogenic chamber, to the liquefied or cooled gas or steam, the low-pressure working fluid discharge port of the cascade pressure exchanger is connected directly or through a heat exchanger to a user of refrigeration, for example, to the atmosphere, or to a refrigeration, or to a cryogenic chamber, to the liquefied or cooled gas and/or steam, the high-pressure working fluid supply port, through a heat removal device, possibly connected to a heat user through a heat exchanger-cooler, possibly with a condensate separator, can be connected to the outlet of the compressing working fluid from the compressor, the inlet of which is connected to a heat source, directly or by means of a heat exchanger, for example, to the atmosphere or to a refrigeration, or to a cryogenic chamber, to the cooled or liquefied gas and/or steam, on the side of heat removal, and the high-pressure working fluid discharge port, for example, through a heat removal device, possibly connected to the heat user through a heat exchanger-cooler, possibly with a condensate separator, is connected, by means of a circulation fan, to the high-pressure working fluid supply port of a cascade pressure exchanger, a part of the ports of which are interconnected by bypass-mass transfer channels built from the side of the low-pressure working fluid supply port or the discharge port, or at least a part of the bypass channels is built from the side of the supply port, and a part of them is built from the low-pressure working fluid discharge port, while the bypass-mass transfer channels of the cascade pressure exchanger, or at least some of them, for example, the high-pressure ones, are built in a beat supply device, for example, in the form of a heat exchanger, connected from the heating side to a source of thermal energy, for example, to the environment or to a refrigeration, or to a cryogenic chamber, or to a cooled gas and/or steam, while the heating medium can be supplied to the heat exchanger from the side of the high-pressure working fluid supply port, and the heating medium can be removed from the side of the low-pressure working fluid supply port of the cascade pressure exchanger.

2. The arrangement according to the claim 1, wherein the in the housing of the pressure exchanger, on the opposite side to at least a part of the bypass-mass transfer channels there are ports connected to each other in pairs by outlet channels built into the heat exchanger with the possibility of supplying heat to the working fluid—gas or steam—filling the outlet channels, while the ports are built with the possibility of periodic alignment, along the direction of rotation of the rotor, with channels built in it in such a way that the first port along the direction of rotation of the rotor is aligned with the channel in the rotor, for example, filled with the working fluid—gas or steam of the highest pressure, with that rotor being blocked on its opposite side by the housing wall, with the possibility of expansion of gas or steam in it into the outlet channel, further connected, in the direction of rotation of the rotor, with a channel in the rotor, with the possibility of displacing the working fluid—gas or steam—in it into the bypass-mass transfer channel, while further, in the direction of rotation of the rotor, at least one more outlet channel can be built.

3. The arrangement according to the claim 1, wherein the low-pressure working fluid discharge port of the cascade pressure exchanger is connected to a liquefied gas or steam separator, or a mixture of gases or steams through the expansion device, for example, through a throttle valve, possibly after an additional cooler, while the discharge of non-condensed gas or steam or mixture and, for example, the supply of liquefied gas or steam, or a mixture of gases or steams, is connected to the inlet of a low-pressure fan or compressor, the outlet of which is connected to the supply port of the low-pressure working fluid of the pressure exchanger, as well as the release of non-condensed gas or steam, or mixture from the condensate separator and, for example, the supply of liquefied gas or steam, or a mixture of gases or steams, is connected to a compressor of a compressing working fluid, the outlet of which is connected, for example, through a heat exchanger-cooler, to the high-pressure working fluid supply port of the pressure exchanger.

4. The arrangement according to the claim 1, wherein the low-pressure working fluid discharge port of the pressure exchanger is connected, possibly through a throttle valve, for example after an additional cooler, to a heat exchanger, which can be built in the form of an evaporator with the possibility of removing heat from the cooled medium, for example, liquid, steam or gas, as a result of boiling and evaporation of a refrigerant or a mixture of refrigerants circulating in the arrangement in the form of a working fluid or a mixture of working fluids.

5. The arrangement according to the claim 1, wherein at least one outlet channel and/or one bypass-mass transfer channel, starting from the outlet and/or the bypass channel, filled with gas or steam with the highest pressure, or at least a part of the channels is connected in series to the source of the heat supply by means of the counterflow heat exchanger, as the coolant temperature and gas and/or steam pressure in the outlet channels and/or in the bypass-mass transfer channels decrease.

6. The arrangement according to the claim 1, wherein the heat exchanger with outlet channels and/or bypass channels built into it is connected to a heat source, for example, to the outlet of gas and/or steam from the compressor of the compressing working fluid or to the outlet of gas and/or steam from the high-pressure working fluid discharge port of the cascade pressure exchanger, possibly through a circulation fan, or simultaneously connected to the outlet from the compressor and the high-pressure working fluid discharge port, while the outlet of the cooled gas and/or steam from the heat exchanger with built-in outlet and/or bypass channels is connected to the high-pressure working fluid supply port of the cascade pressure exchanger.

7. The arrangement according to the claim 1, wherein the heat exchanger with outlet and/or bypass channels built into it is connected to the heat source through an intermediate heat carrier, for example, liquid, while the heat source can be the environment, for example a reservoir or a heat exchanger-cooler.

8. The arrangement according to the claim 1, wherein the as a working fluid a mixture of at least two refrigerants with different temperatures and condensing pressures is contained, while the outlet of the compressing working fluid from the compressor and the outlet of the high-pressure pressure working fluid from the discharge port of the pressure exchanger, for example, through a circulation fan, is connected to at least one heat exchanger-cooler with a low-boiling refrigerant condensate separator, while the outlet of the non-condensed working fluid—readily boiling refrigerant—from the condensate separator is connected to the high-pressure working fluid supply port of the pressure exchanger, and the outlet of the liquefied refrigerant from the condensate separator is connected, for example through an additional cooler, to a throttle valve, the outlet from which is connected to the user of refrigeration, for example, to the heat exchanger of the cooled and/or liquefied gas or steam, and the low-pressure working fluid discharge port of the pressure exchanger is also connected to the user of refrigeration, for example, in a more or less high-temperature part of the cooling heat exchanger of the cooled and/or liquefied gas or steam,

9. The arrangement according to the claim 1, wherein the outlet of the liquefied refrigerant from the condensate separator connected to the heat exchanger-cooler built in in the gas path at the outlet of the working fluid mixture from the high-pressure working fluid discharge port of the pressure exchanger is connected to the expansion device, for example the throttle valve, by means of a pump.

10. The arrangement according to the claim 1, wherein the a part of the flow of the working fluid, gas or steam from the compressor of the compressing working fluid, and/or from the high-pressure working fluid discharge port of the pressure exchanger, after at least one heat exchanger-cooler, is connected, for example, through an additional cooler, to a throttle valve, the outlet of which is connected to the user of refrigeration, for example, to the heat exchanger of the cooled and/or liquefied gas or steam, and the low-pressure working fluid discharge port of the pressure exchanger is also connected to the user of refrigeration, for example in a more or less high-temperature part of the same cooling heat exchanger of the cooled and/or liquefied gas or steam.

11. The arrangement according to the claim 1, wherein the walls of the housing of the cascade pressure exchanger, located between the ports for supplying the working fluid to the channels and discharging the working fluid from the channels built in the rotor, with the said ports built in the housing, are built with the possibility of overlapping the inlet and outlet openings, while the rotor is rotating, with a minimum gap in which labyrinth or contact seals are installed, of at least one channel in a row of the channels of the rotor, meanwhile several rows of channels, at least two rows, can be built in the rotor of the cascade pressure exchanger along its radius

12. The arrangement according to the claim 1, wherein the rotor shaft of the pressure exchanger is connected to an engine drive with the ability to control the rotor speed and/or the rotor is built with the possibility of self-rotation, for example, through special nozzles built in separate ports for supplying the working fluid to the channels of the rotor, for example, also with the ability to control the rotor speed, meanwhile the housing of the pressure exchanger can be made hermetic.

13. The arrangement according to the claim 1, wherein the in the walls of the housing of the cascade pressure exchanger, opposite to at least a part of the channels in the rotor which are fully or partially combined with windows on the opposite side, with said windows being connected to bypass-mass transfer channels, with the possibility of increasing the pressure in these channels of the rotor, and possibly partially opposite to the high-pressure working fluid supply port of the cascade pressure exchanger, nozzles are built for injection of the coolant under the pressure into the channels, and they are connected directly or through a pump to the coolant source, for example to a condensate collector of at least one of the condensate separator, while the coolant can be water or at least one of the refrigerants in a liquid state circulating in the arrangement, at least in part of the cycle.

14. The arrangement according to the claim 1, wherein the in the walls of the housing of the cascade pressure exchanger, opposite to at least a part of the channels in the rotor which are fully or partially combined with windows on the opposite side, with said windows being connected to bypass-mass transfer channels, with the possibility of reducing the pressure in these channels of the rotor, nozzles are built for injection of the heating medium under the pressure into the channels, for example, the pre-evaporated and heated liquid, for example water or liquefied refrigerant, and these nozzles are connected, for example, through a pump, to a source of heating liquid, for example, in the form of a reservoir, in the form of a waste heat boiler, in the form of a compressed gas cooler with separation of hot condensate and so on, meanwhile a heating liquid separator, for example for water, can be built at the outlet of the low-pressure working fluid discharge port of the cascade pressure exchanger.

15. The arrangement according to the claim 1, wherein the a cascade of arrangements is contained, connected in series to the heat exchangers: for pre-cooling and/or liquefying and/or sub-cooling of gas and/or steam, as it cools, and these arrangements have, for example, various refrigerants or mixtures of refrigerants as working fluids, for example, at first as gas or a mixture of gases cools or liquefies with a low-boiling refrigerants, and then with more readily boiling ones, while recuperative heat exchangers connected to refrigerant circulation circuits and separators built with the possibility of extracting low-boiling gases from the flow of the cooled mixture of gases can be installed between the cascades.

16. The arrangement according to the claim 1, wherein the inlet of the compressed working fluid in front of the high-pressure working fluid supply port of the pressure exchanger is built in a heat removal device, for example, in the form of a heat exchanger connected to a source of refrigeration.