RU2682237C1 - Individual heating unit of sub-atmospheric heating system - Google Patents

Individual heating unit of sub-atmospheric heating system Download PDF

Info

Publication number
RU2682237C1
RU2682237C1 RU2018113745A RU2018113745A RU2682237C1 RU 2682237 C1 RU2682237 C1 RU 2682237C1 RU 2018113745 A RU2018113745 A RU 2018113745A RU 2018113745 A RU2018113745 A RU 2018113745A RU 2682237 C1 RU2682237 C1 RU 2682237C1
Authority
RU
Russia
Prior art keywords
steam
condensate
vacuum
water
return
Prior art date
Application number
RU2018113745A
Other languages
Russian (ru)
Inventor
Любовь Викторовна Хан
Игорь Ву-Юнович Ван
Антон Викторович Хан
Виктор Константинович Хан
Original Assignee
Любовь Викторовна Хан
Игорь Ву-Юнович Ван
Антон Викторович Хан
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Любовь Викторовна Хан, Игорь Ву-Юнович Ван, Антон Викторович Хан filed Critical Любовь Викторовна Хан
Priority to RU2018113745A priority Critical patent/RU2682237C1/en
Application granted granted Critical
Publication of RU2682237C1 publication Critical patent/RU2682237C1/en

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24DDOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D1/00Steam central heating systems

Abstract

FIELD: heat supply.SUBSTANCE: invention relates to the field of heat supply. Individual heating unit with independent heating system, connected to centralized heat supply system, is intended for the steam production in medium with negative pressure (vacuum) for sub-atmospheric (vacuum-steam with the negative pressure controlled depth) heating systems mounted in residential, public, industrial buildings and structures. Individual heating unit of sub-atmospheric heating system includes subsystems: the intermediate (primary) heat carrier, the superheated water intake and flow metering, secondary heat carrier, the steam production, the individual heating unit of piping and equipment inner cavity evacuation together with the facility rooms heating system, condensate return from the rooms heating system to the grid water return pipeline, at that, the condensate evacuation and return subsystems operate independently and in periodic mode.EFFECT: proposed IHU allows to implement both the steam temperature quantitative control, and central qualitative one; consumes minimum amount of grid water for steam generation; to minimize the electric energy consumption by the condensate evacuation and return subsystems.1 cl, 1 dwg

Description

The invention relates to the field of heat supply, namely to energy-saving technologies. An individual heating unit (ITP) with an independent (closed) heating system, connected to a centralized heat supply system (CHP, central heating station, district boiler room, etc.), is designed to produce steam in an environment with vacuum (vacuum) for sub-atmospheric (vacuum-steam with an adjustable depth of rarefaction) of heating systems mounted in residential, public, industrial buildings and structures, greenhouses, livestock farms, etc. The invention can be used both in construction and in the reconstruction of heat supply systems by means of ITP devices at the peripheral points of the system, i.e. on the thermal inputs of the heating systems of the premises of objects. In ITP, there is a primary and secondary circulation circuit, hydraulically separated by a distribution manifold for supplying superheated water and a collector for collecting return water and condensate from the heating system of the premises.

The primary coolant (superheated water or high-pressure steam condensate) from the boiler room or CHP is supplied to the central heat point (CCP), where it enters the heat exchanger, this is the main circuit. An additional circuit is the ITP system coupled with the facility’s heating system, where the secondary coolant — steam generated in a steam generator in a vacuum (rarefaction) environment as a result of secondary boiling, receives thermal energy from superheated water from heating networks and transfers it with a high rate of molar transfer in the medium vacuum to the heating devices of the premises of the facility, where during condensation the steam gives up all the heat accumulated in itself. Steam production by adapting the ITP to a centralized heat supply system is possible if, at the same time, the circuit diagram of the heating unit is multifunctional and includes: a subsystem for collecting and recording the flow rate of the primary (intermediate) coolant for the subatmospheric heating system - superheated water from heating networks; a coolant production subsystem - steam (secondary coolant); ITP vacuum subsystem in conjunction with the facility premises heating system; a subsystem for returning return water from a subsystem for the production of steam and condensate from a room heating system into a return water pipe of heating networks through a collector for collecting return water and condensate. The proposed ITP allows both quantitative control of steam temperature (by controlling the flow rate of superheated water) and central quality by creating various vacuum depths (rarefaction) from 0.01 MPa to 0.09 MPa with a range of operating steam temperatures from 96 ° C to 45 ° C . This ITP consumes the minimum amount of network water to create steam produced in a vacuum environment, the amount of which is 1.314 times less than the required amount of network water for the ITP of a traditional water heating system to transfer the same heat flow. The consumption of electric energy by the vacuum and condensate return subsystems to the collector for collecting return water and condensate is also minimal, because the operation of the pumping equipment of these subsystems is periodic. The system of the heating station is simple, reliable and safe in operation, not difficult to maintain and repair. According to the requirements of regulatory and technical documents for the placement of a heat point, the proposed ITP can be separate, attached and built into the basement of the facility.

Individual heat points with adaptation to existing centralized heat supply points for the production and provision of steam subatmospheric heating systems (vacuum - steam with adjustable depth of vacuum) objects in international practice today does not exist.

Given the above circumstance, to disclose the essence of this invention, we take for opposed analogues boiler rooms of autonomous vacuum-steam heating systems and ITP for water heating systems, taking into account that in our case the source of thermal energy is not a steam boiler, but a steam generator for producing steam in a vacuum environment .

A known vacuum-steam system, which includes: a boiler with a steam collector, heating devices connected by taps with a steam pipe, a condensate drain with a condensate pipe and a device for creating a vacuum (RF Patent No. 2195608, F24D 1/00 of 12/27/2002). This system is characterized by high metal consumption and a high probability of loss of tightness. The system does not provide a scheme for the implementation of central quantitative and central quality control of the temperature of the steam and the explosion safety of the boiler.

A known installation for heating with vacuum steam (the source is a publication posted on the Internet, site: ngpedia.ru/id427980pl.html "Vacuum-steam system. Large encyclopedia of oil and gas"). The installation includes: a steam boiler, a distribution line, risers for supplying steam, heating appliances, risers for condensate drainage, a filter, a vacuum pump, an air separator. The disadvantage of this system is a continuously operating vacuum pump connected in series through an air separator to a steam boiler, consuming a significant amount of electricity. There is a high likelihood of cavitation due to the fact that the pump in this system pumps out steam and hot condensate in addition to air, the air trap at the moment of air removal to the atmosphere inefficiently returns condensate to the steam boiler if there is excess pressure in it, and when the absolute pressure in the boiler is less atmospheric, there is a high probability of absorption of outside air into the boiler. The boiler explosion protection system is not provided.

The closest analogue is the well-known vacuum-steam system (the source PN Kamenev, AN Skanavi, VN Bogoslovsky “Heating and ventilation, part 1” Moscow, Stroyizdat, 1975), the device circuit of which includes : steam boiler, steam condensate piping with heating devices, steam traps, condensate tank, system parameter control device, liquid ring pump for creating vacuum and condensate pumping. The disadvantages of this system are the high probability of loss of tightness through the sealing devices of the vacuum liquid ring pump, as well as the inability to regulate the pressure of the various vacuum values with the membrane regulator, because when using this regulator, turning the pump on and off will be for only one specific value of the given vacuum, for another value of the vacuum, the controller will need to be readjusted. If the vacuum ring pump is switched off for an indefinite time, the flow of condensate to the boiler will be stopped, as the pump is connected to the boiler in series. The pump must run continuously while consuming a significant amount of electricity. The restriction on the arrangement of a heating unit with a steam boiler is only in the basement due to the restriction of the return of condensate to the boiler when the steam is backpressured to the pressure in the discharge line of the vacuum pump.

The objective of the invention is the creation of ITP with efficient use of primary coolant (superheated water from the heating and heating plants, boiler room, etc.) with a temperature schedule for the supply of network water in a wide range of 150/70, 130/70, as well as 90/70 with a minimum vacuum power consumption water ring pump and a condensate transfer pump, the use of low-cost materials, reliable and safe operation, the creation of conditions for convenient installation and commissioning with a breakdown of the system into test subsystems (as in our case), to ensure e ease of maintenance and operation.

The technical result is achieved in that the heat flux is transferred in a vacuum-steam manner, based on superconductivity of heat energy with a high heat flux transfer coefficient using a steam generator (secondary boiling steam in a vacuum environment) to consumers via a closed and closed circulation piping system (steam pipelines and condensate lines).

The use of a vacuum-steam method of heat transfer allows to reduce energy consumption by reducing losses (heat engineering, in hydraulic resistance, etc.) in a rarefied environment, for transferring thermal energy to the room heating system. To ensure the transportation of the coolant - steam with a low temperature, low-cost materials (low-carbon steel pipes, metal-plastic pipes, conventional fittings, steam valves, etc.) are applicable. All this is due to the introduction into the system of a periodically working vacuum ring pump with an automatic control system for the depth of vacuum using an electric contact pressure gauge (PGS), depending on the state of the system (degree of tightness) and the specified vacuum parameters. Thus, the regulation of the depth of rarefaction also allows for central quality control of the steam temperature - one of the main requirements of regulatory and technical documents for the operation of heating systems and heating units. The introduction of the level controller (ACS) and the solenoid valve for supplying superheated water to the steam generator of the steam production subsystem allows the steam generator to be charged with the calculated, strictly metered amount of the intermediate coolant - superheated water, which eliminates over-consumption of network water and ensures explosion safety of the steam generator, introducing the controller for the consumption of superheated water in the composition of the generator heater allows for a stable vaporization process at a constant initial temperature re of the intermediate heat carrier (without cooling). The introduction of a level gauge column with conductometric sensors into the condensate collection tank and a level controller (ACS) allowed the condensate transfer pump to operate in periodic mode, which also significantly increases the level of energy efficiency of the ITP. In the case of introducing an outside air temperature controller into the automation system and ensuring its joint operation with the control and management unit (BA) of the operation of a vacuum liquid ring pump (BBH), it will become possible to automatically operate the ITP according to a weather-dependent schedule, which is another reserve for a significant increase in individual energy efficiency heat point.

In FIG. The diagram of an individual heat point of a sub-atmospheric heating system is shown.

An individual heating unit consists (see Fig.) Of: 1. Subsystems for the collection and metering of the flow rate of the intermediate (primary) coolant - superheated water from the network hot water supply pipe (T1) from a district heating source (TPP, boiler room, central heating station, etc.) and which includes: a superheated water flow meter 1, a valve 2, a valve 3, a superheated water distribution manifold 4 with a drain valve 5 and equipped with a pressure gauge (TG).

2. Subsystems for the production of a secondary coolant — steam generated as a result of secondary boiling in a vacuum (vacuum) environment and which includes: a steam generator of evacuated steam 6, which is a thermally insulated tank, inside of which a heater 7 is installed, which serves to maintain a stable initial temperature of the incoming superheated water from heating networks from "cooling" in the process of vaporization, supplied periodically for the formation of evacuated steam; pipeline 8 for supplying superheated water from the distribution manifold of superheated water to the heater; superheated water flow controller 9; return water return pipe 10, comprising a valve 11 and a check valve 12; a collector for collecting return water and condensate 13, which includes a drain valve 14 and a manometric thermometer (TG); a valve 15, by means of which a distribution manifold is connected to the return network water pipe (T2); level gauge column 16 with conductometric sensors for monitoring the water level inside the steam generator and a level controller (ACS); water indicator 17 for visual control of the water level; pipeline 18 for supplying superheated water to the steam generator through valve 19 and controlled by the controller (ACS) solenoid valve 20 in the "normally open" position; steam supply line for evacuated steam 21, connected at one end to the steam generator via valve 22, and the other in the heat input (N1) to the steam line (T7) of the facility premises heating system (residential, public and industrial buildings and structures, greenhouses, livestock farms, etc. .); the steam generator is equipped with a manovacuum meter (PG) and a manometric thermometer (TG), as well as a drain valve 23.

3. The vacuum subsystem of the internal cavity of the piping and ITP equipment, as well as the heating system of the premises, with an adjustable vacuum depth, including: vacuum water ring pump (BBH) 24, which includes a valve 25, a pipe 26 for supplying water to the pump for education water ring, air evacuation pipe 27, air removal pipe from BBH 28, (BA) - automatic control unit for periodic operation of BBH; air separator 29, in which the solenoid valve 30 is in the "normally closed" position, through which air is removed from the ITP system, together with a room heating system, into the atmosphere, water indicator 31, ball valve 32, drain valve 33.

4. The condensate return subsystem from the space heating system to the return water network pipeline (T2), including: the condensate transfer pump 34, which includes valves 35 and 37, the condensate return pipeline 36, connected to the collector for collecting return water and condensate, in the composition of which check valve 38; condensate collection tank 39, which includes a level gauge column 40 with a water indicator 41, a ball valve 42, a drain valve 43, an electric contact pressure gauge (PGS) to control the set, required value of the vacuum during operation and a gauge thermometer (TG); connected through a valve 44 to the condensate collection tank, a condensate return pipe 45, including a mud collector 46, a strainer 47, in turn, the pipe is connected in the heat input (N2) to the central condensate pipe of the space heating system (T8).

Before starting to work, we will carry out preliminary preparation of the ITP system: bring the valves 2 and 15 to the “closed” position; turn valves 3, 5, 14, 23, 25, 33, 43 and ball valves 32, 42 into the closed position; turn valves 11, 19, 22, 35, 37 and 44 into the "open" position; fill the air separator 29 with the softened water to the nominal operating level as indicated by the water indicator 31, for this purpose connect the sleeve to the valve 33, put the ball 32 into the open position, open valve 33, fill the air separator to the required level, then bring the valve and ball valve to the position "closed". Disconnect the flexible sleeve.

The launch of the ITP system is as follows:

1. Put power supply systems and automation in the “on” position.

2. Move valve 25 to the “open” position, set the initial value of vacuum on the electrical contact pressure gauge, the absolute value of which is P abs. = 0.1 bar or P in = 0.9 bar .; turn on the vacuum water ring pump 24, while the electromagnetic valve 30 is triggered, through which air is removed from the internal cavity of the piping and ITP equipment and the heating system of the premises. When the set vacuum value is reached, the electric contact pressure gauge by means of the automatic control and control unit disables the BBH and brings the electromagnetic valve to its original position.

Thus, due to the creation of an independent evacuation subsystem parallel to the condensate return subsystem, the BBH is periodically operated leading to efficient use and energy saving. It should be especially noted that while ensuring satisfactory tightness of all detachable connections of the ITP and the space heating system, at the same predetermined vacuum level, the BBH is switched on for a long period of time (as the leakage is lost), and if the pump is turned on, the period work at the same time short-term. Ensuring tightness is regulated by the normative and technical documentation and is carried out by conducting leak tests with a test medium of 99% air + 1% helium, and a helium leak detector is used to search for leaks. Leak tests are carried out at the commissioning stage.

3. We will supply superheated water from the network water pipeline (T1) to the superheated water distribution manifold 4, for which we bring the valve 2 and valve 3 to the “open” position in the intake and metering subsystem of water, while water enters the steam generator through line 18 for the production of evacuated steam 6, where when a specified water level is reached, controlled by conductometric sensors of the level column 16, the level controller (ACS) will bring the solenoid valve 20 to the "closed" position. Superheated water under vacuum created in the system with a value of P in = 0.7 bar is converted to steam, with an increase in excess pressure to P abs. = 0.7 bar, the steam temperature will be 89.5 ° C. Formed steam from the steam generator through the pipeline 21 enters the steam pipeline (T7) of the space heating system. In the process of steam formation, superheated water in the steam generator loses part of its energy, leading to a drop in temperature. To maintain the initial temperature of the water, for the stable implementation of the steam formation process with the given steam parameters, the steam heater 7 is used. The superheated water enters the heater with a calculated fixed flow rate using the water flow controller 9, the return water is returned through pipeline 10, valve 11 and non-return valve 12 to the collector collection of return water and condensate from the condensate return subsystem, namely from the condensate collection tank. The working level of the intermediate coolant - superheated water in the steam generator is continuously maintained by the level controller (ACS) in conjunction with conductometric sensors of the gauge column 16, a water indicator 17 is used to visually control the water level. When the lower limit water level is reached by the electric signal from the controller, the electromagnetic valve 20, while supplying a new portion of superheated water to the steam generator.

4. Condensate is returned to the return water collector by the condensate return subsystem.

The condensate coming from the heating system of the premises through the central condensate toprod (T8), after being cleaned of mechanical impurities in the sump (rough filter) 46, the strainer 47 through pipe 45, flows through valve 44 to the condensate collection tank 39. When the level is reached condensate in the tank of the upper maximum permissible level controller (ACS), which responds to the signals of conductometric sensors of the gauge column 40, connects the condensate pump 34, which through valve 37, the check valve 38 p duct 36 sends the condensate collector 13. Further, through the valve 15 return water mixed with the condensate goes to the return water pipe network (T8). It should be noted that the temperature of the condensate does not exceed 40 ° C due to the presence of a low vacuum in the condensate line and the condensate collecting tank, a pressure gauge (TG) is available for visual monitoring of this temperature, which affects the degree of thermal performance of steam heating systems. The temperature of the mixed water in the collector for collecting reverse water and condensate does not exceed 70 ° C.

To assess the performance of an individual heating unit for a sub-atmospheric heating system, we present a brief comparative analysis of the consumption of hot network water (superheated water from a central heating station or condensate from a steam boiler) ITP for a water heating system and ITP of the invention:

1. Determine the flow rate of superheated network water in the ITP with an elevator unit for a water heating system with the initial data: with the required heat capacity of the local heating system to compensate for the heat loss of the building Q = 400000 kcal / kg, with the temperature of the network water t 1 = 150 ° C, cooled t 2 = 70 ° C, with the temperature of the water in the heating system of the premises t 3 = 95 ° C, the heat capacity of water c = 1.0 kcal / (kg × ° C).

We calculate: G 1 - hot water flow from the elevator nozzle to create the necessary ejection and water heating in the heating system of the object, G 1 = 400000 / 1,0 × (150-70) = 5000 kg / h .; G 3 - the total amount of water circulating in the heating system, G 3 = 400000 / 1.0 × (95-70) = 16000 kg / h; G 2 - flow rate of water mixed from the return pipe of the heating system, G 2 = 16000-5000 = 11000 kg / h.

2. Let us determine the flow rate of superheated network water in the ITP of the sub-atmospheric heating system if: the capacity of the local heating system is Q = 400000 kcal / kg, the temperature of the resulting steam in a vacuum is 95 ° C, the temperature of the network superheated water is 150 ° C with an enthalpy of 152.8 kcal / kg, condensate enthalpy is 29.9 kcal / kg at a condensate temperature of 30 ° C in the condensate collection tank (experimental data obtained from testing an industrial prototype of a sub-atmospheric heating system), latent heat of vaporization of secondary boiling steam obtained in vacuum at excess ohm pressure in the vapor space heating system reaching P abs. = 0.9 bar (final value of overpressure), equal to 541.3 kcal / kg.

We calculate: the required secondary boiling steam flow rate with a temperature of 95 ° C for heating this facility with the heat output indicated above, the steam flow rate will be 400000 / 541.3 = 738.96 kg / h; the amount of steam of secondary boiling generated from the total amount of incoming network water in,% of steam = [(152.8-29.9) / 541.3] × 100 = 22.7%; the consumption of network water to form the required amount of steam to provide the required heat capacity will be equal to 738.96 / 0.227 = 3255.33 kg / h. Here it is required to take into account the amount of network water consumed by the steam heater and equal to 550 kg / h (data for heat exchangers - heaters). Thus, the total amount consumed by the network water steam generator will be equal to 3805.33 kg / h.

From the condensate collecting tank 39, condensate with a temperature of 30 ° C is sent to the collector for collecting the return water 13, where it is mixed with the return water from the heater 7. Next, the mixed water with a temperature of 70 ° C is transported to the return network water pipe (T2).

So, the ITP of the sub-atmospheric heating system consumes 5000-3805.33 = 1194.67 kg / h less than the network superheated water or 5000 / 3805.33 = 1.314 times less thermal energy than the ITP of a water heating system.

The above noted advantage of the ITP of the sub-atmospheric heating system is due to the fact that in the steam generator there is a direct conversion of hot water to steam in a vacuum environment, and the stable process of vaporization is provided by the superheated water heater from cooling.

A feature of the ITP of the sub-atmospheric heating system is that it is divided into independently operating condensate return subsystems and vacuum subsystems with automatic control and management of creating different vacuum values, which allow for high-quality temperature control in the heating system with a wide enough range of vacuum depth control with absolute pressures from 0.1 bar to 0.9 bar, the temperature difference of the coolant is from 96 ° C to 45.45 ° C, which corresponds to etstvuet standards of hygiene and sanitation as well as the temperature drop and allows the use of metal-plastic pipes, pipe fittings made of plastics materials prone lowest degree of corrosion. The heating system is easy to maintain, safe to operate and provides reliable, uninterrupted operation of the entire heat supply system.

Claims (2)

1. An individual heating unit of a sub-atmospheric heating system containing subsystems: collecting and accounting for the flow rate of the intermediate (primary) coolant - superheated water, production of the secondary coolant - steam, evacuation of the internal cavity of the piping and ITP equipment, coupled with a heating system of the premises, return of condensate from the system heating the premises into the return pipe of network water, characterized in that the subsystems for evacuation and condensate return work independently and in a periodic mode.
2. An individual heat point according to claim 1, characterized in that the steam generator for producing steam in a vacuum environment is equipped with a steam heater, a level gauge with conductivity sensors and a level controller, the vacuum subsystem is equipped with an automatic control unit for controlling the operation of the vacuum ring pump to create an adjustable vacuum depth , the condensate return subsystem is equipped with a level gauge with conductometric sensors for monitoring the level of the intermediate coolant and control level lehr to control periodic operation of the pumping condensate pump.
RU2018113745A 2018-04-16 2018-04-16 Individual heating unit of sub-atmospheric heating system RU2682237C1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
RU2018113745A RU2682237C1 (en) 2018-04-16 2018-04-16 Individual heating unit of sub-atmospheric heating system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
RU2018113745A RU2682237C1 (en) 2018-04-16 2018-04-16 Individual heating unit of sub-atmospheric heating system
PCT/RU2018/000663 WO2019203684A1 (en) 2018-04-16 2018-10-09 Individual heating substation of a sub-atmospheric heating system

Publications (1)

Publication Number Publication Date
RU2682237C1 true RU2682237C1 (en) 2019-03-15

Family

ID=65806102

Family Applications (1)

Application Number Title Priority Date Filing Date
RU2018113745A RU2682237C1 (en) 2018-04-16 2018-04-16 Individual heating unit of sub-atmospheric heating system

Country Status (2)

Country Link
RU (1) RU2682237C1 (en)
WO (1) WO2019203684A1 (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2016354C1 (en) * 1991-06-03 1994-07-15 Калининградский технический институт рыбной промышленности и хозяйства Two-circuit steam heating system
RU2195608C1 (en) * 2001-04-16 2002-12-27 Казанская государственная архитектурно-строительная академия Vacuum-steam heating system
US20140034743A1 (en) * 2010-02-18 2014-02-06 Igor Zhadanovsky Vapor vacuum heating systems and integration with condensing vacuum boilers
UA89954U (en) * 2013-10-25 2014-05-12 Харьковский Национальный Университет Имени В.Н. Каразина Autonomous steam-vacuum heating system with cyclic self-consistent heat mode
RU2592191C2 (en) * 2014-09-30 2016-07-20 Любовь Викторовна Хан Vacuum steam heating system
RU2631555C2 (en) * 2016-02-24 2017-09-25 Антон Викторович Хан Vacuum and steam heating system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2016354C1 (en) * 1991-06-03 1994-07-15 Калининградский технический институт рыбной промышленности и хозяйства Two-circuit steam heating system
RU2195608C1 (en) * 2001-04-16 2002-12-27 Казанская государственная архитектурно-строительная академия Vacuum-steam heating system
US20140034743A1 (en) * 2010-02-18 2014-02-06 Igor Zhadanovsky Vapor vacuum heating systems and integration with condensing vacuum boilers
UA89954U (en) * 2013-10-25 2014-05-12 Харьковский Национальный Университет Имени В.Н. Каразина Autonomous steam-vacuum heating system with cyclic self-consistent heat mode
RU2592191C2 (en) * 2014-09-30 2016-07-20 Любовь Викторовна Хан Vacuum steam heating system
RU2631555C2 (en) * 2016-02-24 2017-09-25 Антон Викторович Хан Vacuum and steam heating system

Also Published As

Publication number Publication date
WO2019203684A1 (en) 2019-10-24

Similar Documents

Publication Publication Date Title
US20040108096A1 (en) Geothermal loopless exchanger
CN102460024B (en) District energy sharing system
KR101040693B1 (en) The central heating and hot water supply systems for saving energy
US6837303B2 (en) Internal water tank solar heat exchanger
US20060213637A1 (en) Geothermal aqueduct network
US20110198406A1 (en) Vapor/vacuum heating system
CN101886831A (en) Integrated heat-supply and energy-saving system
LT2010018A (en) Centralized heat and hot water supply system
US20130037236A1 (en) Geothermal facility with thermal recharging of the subsoil
CN203687391U (en) Full-automatic panel solar energy centralized hot-water supply system for high altitude areas
CN202332313U (en) Essential service water system of nuclear power station
US9027846B2 (en) Vacuum sustaining heating systems and methods
CN102155818B (en) Low-temperature floor radiation heating and refrigerating system device
CN201513995U (en) Refrigerating system capable of utilizing ground temperature to provide cooling for buildings through floor warming system
CN2594756Y (en) Automatic heat exchanger set
CN101761108A (en) Non-negative pressure cold and hot water mixed supply system for domestic use
CN202485208U (en) Energy-saving double-water-tank constant-temperature continuous water supply system
CN204301356U (en) Energy-saving device for residual heat and residual pressure recovery of circulating cooling water system of sugar factory
GB2542223A (en) Thermal energy network
CN203771537U (en) Wall heating system
CN2750244Y (en) Solar heat pump water heater
US20120298204A1 (en) Energy saving system and method for heating water
CN102494365B (en) Control method of heat supply secondary pipe network distributed balance control system
CN201637192U (en) Solar integrated device capable of heating, cooling and supplying hot water
RU108561U1 (en) Ecological and energy-saving system of cold and heat supply of family house