US3890936A - Hot water generator for shock testing fabricated piping components - Google Patents

Hot water generator for shock testing fabricated piping components Download PDF

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Publication number
US3890936A
US3890936A US437249A US43724974A US3890936A US 3890936 A US3890936 A US 3890936A US 437249 A US437249 A US 437249A US 43724974 A US43724974 A US 43724974A US 3890936 A US3890936 A US 3890936A
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United States
Prior art keywords
fuel
coil
air
temperature
hot water
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Expired - Lifetime
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US437249A
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English (en)
Inventor
Michael J Mcinerney
Robert T Brady
Alvia E Phillips
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Mark IV Transportation Products Corp
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Vapor Corp
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Publication date
Application filed by Vapor Corp filed Critical Vapor Corp
Priority to US437249A priority Critical patent/US3890936A/en
Priority to US05/505,654 priority patent/US3942355A/en
Priority to CA217,467A priority patent/CA1021648A/fr
Priority to CH79075A priority patent/CH590435A5/xx
Priority to FR7502446A priority patent/FR2259326B1/fr
Priority to DE19752503411 priority patent/DE2503411A1/de
Priority to GB52098/74A priority patent/GB1503308A/en
Priority to GB25406/77A priority patent/GB1503309A/en
Application granted granted Critical
Publication of US3890936A publication Critical patent/US3890936A/en
Priority to CA280,480A priority patent/CA1049287A/fr
Assigned to MARK IV TRANSPORTATION PRODUCTS CORPORATION, A CORP. OF DELAWARE reassignment MARK IV TRANSPORTATION PRODUCTS CORPORATION, A CORP. OF DELAWARE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: VAPOR CORPORATION, A CORP. OF DELAWARE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
    • F24H1/43—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes helically or spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/10—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium
    • F24H1/12—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium
    • F24H1/14—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form
    • F24H1/16—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form helically or spirally coiled
    • F24H1/165—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form helically or spirally coiled using fluid fuel

Definitions

  • ABSTRACT A hot water generator capable of producing a maximum rate of water temperature increase without generation of vapors including a heat exchanger in the form of an annularly shaped helical coil through which the water to be heated is pumped and which is connected to a piping system including a load and a combustor for rapidly providing increased combustion which is controlled in response to the temperature of the water at the outlet of the coil so that the heater can produce a maximum rate of water temperature rise without causing boiling and generating vapors in the coil.
  • the method concerns the shock testing of piping components by producing nearly theoretical maximum heat flux rate very quickly.
  • This invention relates in general to hot water generators and more particularly to a hot water generator operating at high temperatures so the heat exchanger of the generator will produce a maximum rate of heat absorption and therefore temperature rise without nucleation.
  • hot water generators have operated well below the maximum heat release obtainable because of heat exchange and pressure control systems which would result in generating transient pockets of vapor. some of which might become superheated. Pressure transients produced by these vapor pockets generate hamrncr" or load pressure transients in the heat exchanger portion of the generator which is objectionable in damage caused to the heat exchanger and audible noise emitted. superheated vapor pockets localize overheating of heat exchanging surfaces that result in decreased life. Vaporization of water causes film temperatures at sufficient high levels which may produce scaling and/or corrosion. Accordingly, it is important that the water heated by the generator never enter the vapor phase.
  • the present invention utilizes a heat exchanger structure and a combustor similar to that shown in the aforementioned US. Pat. No. 3,282,257, together with a unique control system for obtaining the maximum rate of water temperature increase without generation of vapor pockets.
  • the system of the invention can operate to heat water from a temperature of about 562 F. and a pressure of about 2282 psig to a temperature of about 627 F. and a pressure of about 2266 psig in about 50 seconds.
  • This allows the maximum heat flux to be absorbed by the heat exchange structure without moving into the area of nucleate or more advanced stages of boiling corresponding to the pressure involved.
  • the hot water generator of the invention is capable of shock testing high performance fabricated piping components such as valves, regulators, heat exchangers and the like, by subjecting a component to a rapid water temperature rise without nucleation or the generation of vapor pockets.
  • the controls for operating the generator to obtain the rapid temperature rise in the water heated includes a temperature controller monitoring the outlet tempermore of the water heated by the generator and producing a signal for operating a high speed air fuel actuator to provide the maximum permissible combustion rate capable of being handled by the heat exchanger structure of the generator without generating vapor pockets in the water being heated.
  • a blower generating combustion air for the combustor has its output controlled by a damper connected to the actuator.
  • a fuel metering valve delivering fuel to the combustor is also controlled by the actuator.
  • a 24-to-l turndown ratio ofthe generator permits generation of a wall of water" which produces rapid increases in the water outlet temperature within accurately controlled flow and pressure limits. Turndown ratio is the ratio of the maximum to minimum thermal input of the generator.
  • Another object of this invention is in the provision of a hot water generator and method for shock testing high performance fabricated piping components by subjecting a component to a rapid temperature rise of water without nucleation.
  • Still another object of this invention is in the provision of a high speed hot water generator including controls that are capable of operating the generator to provide the maximum rapid rate of temperature chan without generating vapor pockets in the liquid.
  • a still further object of the invention is in the provision of a hot water generator having a heat exchanger which may be efficiently and inexpensively manufactured and which has long service life where controlled heat input and extraction produces a maximum rate of heat absorption and therefore temperature rise.
  • FIG. 1 is a somewhat diagrammatic and block view of the hot water generator according to the invention together with the controls and water flow loop;
  • FIG. 2 is a somewhat diagrammatic view of a system including a plurality of hot water generators connected in parallel in connection with the shock testing of a piping component;
  • FIG. 3 is a graphical illustration of the maximum allowable water temperature at the hot water generator outlet as a function of outlet pressure for a hot water generator according to the present invention
  • FIG. 4 is a graphical illustration ofthe maximum outlet water pressure and temperature of a hot water generator according to the invention as a function of water flow rate for prevention of boiling in the heat exchanger of the generator;
  • FIG. Si is a typical boiling curve illustrating boiling regimes for hot water generators
  • FIG. 6 is a graphical illustration of the time response plotted against heater water outlet temperature illustrating the low tire to high fire conditions of the generator according to the present invention and the maximum temperature rise without nucleation;
  • FIG. 7 is a graphical illustration showing the steady state of maximum fire rates allowable for operation between low fire outlet heater temperature and maximum allowable outlet temperature without boundary layer boiling;
  • FIG. 8 is a block diagram of the air fuel control system of the generator of the present invention.
  • FIGS. 9. l and I] are graphical illustrations ofoper ations pursuant to a change in the set point temperature of the controller in relation to the control signal, the damper and the temperature of the hot water at the outlet of the heat exchanger;
  • FIGS. l2, l3 and 14 show the relationship during the change in load between the temperature of the hot water coming into the heat exchanger of the generator, the hot water leaving the heat exchanger and the flue gases transferred from the combustor to the heat exchanger.
  • the hot water generator of the invention is diagrammatically illustrated as including a housing enclosing a combustor section 21 and a coil section 22.
  • a choke 23 is provided within the housing between the combustor section and the coil section to direct the flow of gases from the combustor section to the coil section.
  • a coil or heat exchanger in the form of a coil and designated generally by the numeral 24 includes a plurality of watertubes.
  • the coil is annularly shaped and helical in form and wherein the water tubes are arranged in radially arranged layers and longitudinally spaced or arranged rows with an inlet 25 at the outermost layer of watertubes and an outlet 26 at the innermost layer of watertubes.
  • Combustion or flue gases generated in the combustor section 21 flow through the choke 23 into the central area ofthc coil 24 outwardly and through a flue gas outlet 27. While the generator is shown diagram matically, it will be appreciated that this part of the generator is essentially of a type shown in the afore' mentioned U.S. Pat. No. 3,282,257.
  • the helical watertubes define a path for the water which picks up heat from the coil that is absorbed from the flue gases which involves the transfer of heat to the minimum amount of water moving through the coils. it is important that minimum amount of water is involved in the heat transfer process in order to obtain the desired rapid rise in temperature of the water.
  • Combustion gases are generated from an appropriate fossil fuel and air mixture.
  • Fuel may be a natural gas or other suitable fossil fuel which is delivered from a suitable source of supply through a fuel line 30 to the combustor section or the combustion chamber in the combustor section.
  • a metering valve 31 controls the fuel flow in the combustor section.
  • Primary air or combustion air is generated by a blower 32 and delivered through a duct 33 to the com bustor section 21.
  • a damper 34 is provided in the duct to control the air flow through the duct.
  • a small amount of air is bled from the duct 33 ahead of the damper into the fuel line 30 by a bleed line 35 to provide some mixture of air with the fuel that is delivered by the fuel line into the combustor section.
  • This is important in order to provide a high turndown ratio from high fire to low fire. More specifically, it assists in providing about a 24-to-l turndown ratio in order to provide the necessary increase in temperature and obtain the necessary shock testing in connection with the shock testing of fabricated components according to the invention.
  • a high speed air fuel actuator 38 is mechanically coupled to the metering valve 3! and the damper 34 for controlling the operation thereof and therefore the air fuel flow into the combustion section 2].
  • This actuator receives a signal from a temperature controller 39 of a suitable type which responds to a set point indicator 40 and the temperature of the hot water at the outlet 26 of the heat exchanger 24 by virtue of a suitable temperature measuring instrument 4].
  • a pipe or conduit 45 is connected between the inlet end and outlet end of the coil or heat exchanger 24.
  • a pump 46 is provided in the piping 45 to cause constant flow of water through the entire water path or loop at all times at a desired flow rate. Therefore. forced circulation of water is established through the coil 24.
  • a load 47 is also provided in the pipe 45 for loading the system. As shown, the load is in the form of a heat exchanger but may be of any desirable form although it should be such as to provide a continuous path in the piping 45. In the event that a fabricated component to be shock tested is a heat exchanger. such can be inserted at the load 47 position.
  • a regulator or the like can be mounted in the piping 45 at the posi tion 48 ahead of the load 47 or at the position 49 between the load and the pump 46.
  • the load 47 would be matched with the coil capacity of the generator.
  • a plurality of hot water generators may be connected in parallel. as shown by the hot water gener ators 20A, 20B and 20C. Suitable manifolds at the inlet and outlet will be provided to facilitate the parallel connecting of such generators. While three generators are shown in FIG. 2, it can be appreciated that any number may be connected in parallel depending on the load. it can be appreciated that suitable balancing valves may be provided at the outlets of parallel connected generators so that the same temperature and pressure condi tions of each generator is delivered into the outlet manifold.
  • the generators may use any suitable type of fossil fuel as already mentioned.
  • the water used in the system will be de-aerated, de-mineralized, and perhaps otherwise treated.
  • the air fuel actuator 38 may be of any suitable type which provides a fast enough response which is necessary in order to enable the rapid rise in temperature of the liquid in the heat exchanger of the generator and also to prevent nucleation. For example, if theactuator will provide a full stroking time in two seconds or less, it will be able to provide the necessary quick response needed for the generator of the present invention. The response must be faster than the heat absorption capacity of the heat exchanger of the generator.
  • the typical boiling curve illustrating boiling regimes for hot water generators is shown in FIG. 5.
  • Most hot water systems involve operating in a state of unsteady equilibrium where several of the boiling regimes illustrated in FIG. 5 are traversed. It is preferable that a system operate in the incipient nucleate boiling range indicated at 51 which is just below the nucleate boiling point A, where the most efficient heat transfer is avail able.
  • the system of the present invention operates at point B. Overshoot of the maximum heat rate can move the operation of a system into the unstable boiling regions resulting in damage or destruction of the heat exchange surfaces.
  • the curve of FIG. 5 shows the change in temperature plotted along the horizontal and the heat flow rate along the vertical.
  • the rate of rise in temperature is dictated by the maximum heat flux which can be absorbed by the heat exchanger of the generator without moving into the area of nucleate or more advanced stages of boiling corresponding to the pressures involved.
  • An illustration of the temperature-time response of a generator according to the present invention is shown in FIG. 6 wherein time in seconds is plotted along the horizontal and heater outlet water temperature is plotted along the vertical. As illustrated. the time taken to move from low fire to high fire or one hundred percent firing rate of the generator is about 40 seconds, where the low-fire temperature is 573 F. and the high-fire temperature is about 627 F. Likewise. the rate of drop in temperature is dictated by the maximum heat flux absorbable by the heat exchanger. The trip point A and the normal operating point B are also shown here.
  • the curve in FIG. 3 relates to the maximum allowable water temperature at the outlet of the coil as a function of outlet pressure for the generator of the invention to illustrate what temperature and pressure relationship must be maintained to prevent nucleation.
  • the region on the left side of the curve represents no boundary layer boiling for the coil. while the shaded region on the right side of the curve represents the area to be avoided where coil boundary layer boiling does exist. Accordingly. during temperature rise of the water. the relationship between the temperature and the pressure must be in the region to the left of the curve to prevent boiling.
  • the loci of point A from FIG. 5 is shown for water flow rates from fifty to one hundred percent if the fuel inputs of FIG. 7 are adhered to.
  • the curves shown in FIG. 4 represent the limiting hot Water generator outlet water pressure and temperature as a function of the water flow rate for the prevention of boiling in the coil boundary layer therein.
  • Heater outlet temperature in degrees Farenheit is plotted along the horizontal
  • heater outlet pressure in psia is plotted along the vertical.
  • Numbers 55, 56 and 57 respectively represent 50 percent, 90 percent and I00 percent water flow rates. Regions of no boiling are to the left of the curves, while regions of boiling are to the right of the curves.
  • the steady state maximum temperatures allowable are reached at approximately 2400 psia at temperatures of 630. 638 and 642 F. for the 50, 90 and 100 percent water flow rates. Accordingly, the 2400 psia limitation is indicated as a trip point which is a pressure that must be maintained or exceeded in order to prevent entering the boiling region which is shown in the shaded portion in FIG. 3.
  • the operation of the generator of the present invention involves raising a nominal or residual temperature at low tire and establishment of the water flow rate at a value corresponding to the amount of heat required. This is illustrated in FIG. 7.
  • the curves in FIG. 7 show heat transfer to the water in btus per hour times IO along the horizontal and heater outlet temperature in degrees Farenheit along the vertical. These curves illustrate maximum fuel fire rates allowable for operation between the low fire heater outlet temperature and maximum allowable outlet temperature without boundary layer boiling.
  • the percent water flow curves are shown to he 50, 60, 70, 80, 85, 90, 95, 100.
  • the I00 percent water flow rate represents the maximum heat output of the system.
  • the block diagram of the system shown in FIG. 8 illustrates the temperature control 39 as receiving the set point temperature and delivering a signal to a summing junction which receives a feedback from the temperature of the hot water out (T,,,,) which is taken at the temperature measuring device 41 in the outlet of the heat exchanger 24.
  • the summation of the feedback sig nal and the signal from the temperature controller is delivered to the servo motor or actuator 38 which controls the operation of the gas valve 31 and the damper 34.
  • the operation of the gas valve 31 and the damper 34 results in the weight and temperature of the flue gas in the combustor and the heat exchanger 21, 24.
  • Load 47 which removes heat and therefore determines the temperature of the hot water into the heat exchanger, effects the overall operation of the system.
  • FIGS. 9, l0 and II The response to the change in set point of the temperature controller during an increase in temperature is illustrated in FIGS. 9, l0 and II as plotted against time.
  • the control signal variation of the set point temperature (T,,,) is illustrated as being increased along the full range of temperature increase desired of about 573 to 627 F.
  • the temperature and weight of the flue gases (T and W,,,) are shown in FIG. l0 in relation to the damper and valve operation.
  • the rise in the temperature of the hot water out (T of the heat exchanger is illustrated in FIG. ll.
  • Note the dead zone 68 which is also illustrated at 69 in FIG. 6.
  • the change in load of the heat exchanger indicated by a decrease in temperature is illustrated with the relationship between the hot water temperature into the heat exchanger, the hot water temperature out of the heat exchanger, and the temperature and weight of the flue gases in the combustor and heat exchanger sections is shown in FlGS. l2, l3 and 14.
  • the hot water generator ofthe invention may be utilized in the method of shock testing of high performance piping components wherein it is desired to produce maximum heat flux rate without nucleation so as to provide a hot water generator with a heat exchanger of long service life
  • a hot water generator having a high turndown ratio for rapidly increasing the temperature of hot water to a point of substantially theoretical maximum heat absorption and temperature rise without nucleation.
  • said generator comprising a housing defining connected substantially cylindrical coil and combustor sections.
  • an annularly shaped helical coil axially aligned in the coil section having a plurality of longitudinally arranged rows and radially arranged layers of watertubes with an open central area for receiving combustion gases and defining a water flow path, an inlet at the outermost layer of said watertubes, an outlet at the innermost layer of said watertubes, piping outside the generator connected between the inlet and outlet of the coil to define therewith a continuous closed loop water flow path, a load in the piping, a pump in the piping causing a constant water flow in the flow path such that the pressure maintained will limit the water temperature to just below the nucleate boiling point, a flue gas outlet in the coil section outward of the coil, a fuel and air induction system including a fossil fuel burner
  • a duct connecting the blower to the combustor section and having a damper for controlling combustion air, a combustion air bleed line ahead of the damper for continually bleeding a small amount of air directly into the fuel line downstream of the valve to maintain combustion stability at low fire, a choke in the housing between the combustor section and the coil section directing combustion gases from the combustor section to the central area of the coil, a fast response air-fuel actuator connected to the fuel valve and air damper for quickly providing the necessary air fuel supply, and control means operating said actuator in response to a set point temperature input and the input of a temperature measuring device at the outlet of said coil to control fuel and air flow change from low tire to high fire and produce a maximum rate of water temperature increase without nucleation.
  • a hot water generator having a high turndown ratio for rapidly increasing the temperature of hot water to a point of substantially theoretical maximum heat absorption and temperature rise without nucleation, said generator comprising a housing defining connected substantially cylindrical coil and combustor sections, an annularly shaped helical coil in the coil section with an open central area for receiving combustion gases and defining a water flow path.
  • a fuel and air induction system including fuel and air controls coacting to deliver the proper mixture of fuel and air to the combustor section
  • said fuel and air induction system including a fuel line delivering fuel to the combustor section, a combustion air line delivering combustion air to the combustor section, and means continually bleeding air directly into the fuel line to maintain stable combustion in the combustor section at minimum fire conditions, a fast response actuator for said fuel and air controls, and a temperature controller providing operating signals to the actuator in response to a set point temperature and the water temperature at the coil outlet to operate the fuel and air controls and cause a rapid rate of temperature rise in the outlet water temperature without nucleation.
  • a hot water generator having a housing defining connected substantially cylindrical coil and combustor sections, an annularly shaped helical coil axially aligned in the coil section with an open central area for receiving combustion gases and defining a water flow path, an inlet and an outlet for said coil, piping outside the generator connected between the inlet and outlet of the coil to define therewith a continuous closed loop water flow path, a load in the piping, a pump in the piping causing a constant water flow in the flow path, a fuel and air induction system including a fuel burner delivering fuel to the combustor section and a blower for producing and delivering combustion air to the combustor section, a fuel line having a fuel metering valve therein and connected to the burner to deliver fuel thereto, a duct connecting the blower to the combustor section and having means therein for controlling the amount of combustion air to the combustor section, the improvement in means for maintaining stable combustion in the combustor section at minimum air-fuel openings comprising

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
US437249A 1974-01-28 1974-01-28 Hot water generator for shock testing fabricated piping components Expired - Lifetime US3890936A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US437249A US3890936A (en) 1974-01-28 1974-01-28 Hot water generator for shock testing fabricated piping components
US05/505,654 US3942355A (en) 1974-01-28 1974-09-13 Hot water generator and method for shock testing fabricated piping components
CA217,467A CA1021648A (fr) 1974-01-28 1975-01-07 Chauffe-eau et methode d'essai de resistance aux chocs pour la tuyauterie constitutive
CH79075A CH590435A5 (fr) 1974-01-28 1975-01-23
FR7502446A FR2259326B1 (fr) 1974-01-28 1975-01-27
DE19752503411 DE2503411A1 (de) 1974-01-28 1975-01-28 Heisswassererzeuger und verfahren zur schockpruefung von rohrleitungs- fertigteilen unter verwendung eines heisswassererzeugers
GB52098/74A GB1503308A (en) 1974-01-28 1975-01-28 Hot water generator
GB25406/77A GB1503309A (en) 1974-01-28 1975-01-28 Shock testing fabricated piping components
CA280,480A CA1049287A (fr) 1974-01-28 1977-06-14 Generateur d'eau chaude et methode d'essai de resistance aux chocs d'elements de tuyauterie faconnes

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US437249A US3890936A (en) 1974-01-28 1974-01-28 Hot water generator for shock testing fabricated piping components

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US05/505,654 Division US3942355A (en) 1974-01-28 1974-09-13 Hot water generator and method for shock testing fabricated piping components

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US3890936A true US3890936A (en) 1975-06-24

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US (1) US3890936A (fr)
CA (1) CA1021648A (fr)
CH (1) CH590435A5 (fr)
DE (1) DE2503411A1 (fr)
FR (1) FR2259326B1 (fr)
GB (2) GB1503309A (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4147301A (en) * 1977-04-13 1979-04-03 Halma Wayne G Heating system
US4455969A (en) * 1979-03-14 1984-06-26 The British Petroleum Company Limited Fluidized bed combustor
US4737101A (en) * 1984-03-08 1988-04-12 Davair Heating Limited Oil burner
US4768947A (en) * 1986-10-16 1988-09-06 Rinnai Corporation Burner apparatus
US5109807A (en) * 1990-05-15 1992-05-05 Gas Research Institute High output mini hydronic heater
US5222942A (en) * 1988-04-08 1993-06-29 Mohandes Bader Syringe, specifically for use in medicine
US5555850A (en) * 1994-05-13 1996-09-17 Morris F. Garcia Method and apparatus for heating liquid
CN102331439A (zh) * 2011-09-29 2012-01-25 王加龙 冷却器散热性能试验装置
CN108132198A (zh) * 2018-01-30 2018-06-08 重庆大学 一种不同环境模块间的超高温陶瓷往复热冲击试验装置
US10024572B1 (en) 2012-12-20 2018-07-17 Htp, Inc. Heat exchanger
US10605465B2 (en) * 2015-10-28 2020-03-31 Robertshaw Controls Company System and method for using alternative energy source for hot water heater storage tank

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2325986A (en) * 1997-06-06 1998-12-09 Scott Gibbin Ltd Exhaust manifold test rig

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US1615482A (en) * 1926-06-21 1927-01-25 Brown Instr Co Tube oil-heater control
US2056519A (en) * 1934-05-25 1936-10-06 Westinghouse Electric & Mfg Co Forced flow steam generator
US2081948A (en) * 1936-04-16 1937-06-01 Michel Friedrich Steam generator
US2717581A (en) * 1951-06-06 1955-09-13 Theodoric B Edwards Automatically controlled water heater
US3282257A (en) * 1963-06-05 1966-11-01 Vapor Corp Fluid heating apparatus
US3672808A (en) * 1970-10-15 1972-06-27 Japan Furnace Ind Co Ltd Method and apparatus of continuous steam-atomizing fuel combustion for boiler furnace

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1615482A (en) * 1926-06-21 1927-01-25 Brown Instr Co Tube oil-heater control
US2056519A (en) * 1934-05-25 1936-10-06 Westinghouse Electric & Mfg Co Forced flow steam generator
US2081948A (en) * 1936-04-16 1937-06-01 Michel Friedrich Steam generator
US2717581A (en) * 1951-06-06 1955-09-13 Theodoric B Edwards Automatically controlled water heater
US3282257A (en) * 1963-06-05 1966-11-01 Vapor Corp Fluid heating apparatus
US3672808A (en) * 1970-10-15 1972-06-27 Japan Furnace Ind Co Ltd Method and apparatus of continuous steam-atomizing fuel combustion for boiler furnace

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4147301A (en) * 1977-04-13 1979-04-03 Halma Wayne G Heating system
US4455969A (en) * 1979-03-14 1984-06-26 The British Petroleum Company Limited Fluidized bed combustor
US4737101A (en) * 1984-03-08 1988-04-12 Davair Heating Limited Oil burner
US4768947A (en) * 1986-10-16 1988-09-06 Rinnai Corporation Burner apparatus
US5222942A (en) * 1988-04-08 1993-06-29 Mohandes Bader Syringe, specifically for use in medicine
US5109807A (en) * 1990-05-15 1992-05-05 Gas Research Institute High output mini hydronic heater
US5555850A (en) * 1994-05-13 1996-09-17 Morris F. Garcia Method and apparatus for heating liquid
CN102331439A (zh) * 2011-09-29 2012-01-25 王加龙 冷却器散热性能试验装置
US10024572B1 (en) 2012-12-20 2018-07-17 Htp, Inc. Heat exchanger
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CN108132198A (zh) * 2018-01-30 2018-06-08 重庆大学 一种不同环境模块间的超高温陶瓷往复热冲击试验装置
CN108132198B (zh) * 2018-01-30 2020-08-07 重庆大学 一种不同环境模块间的超高温陶瓷往复热冲击试验装置

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GB1503308A (en) 1978-03-08
FR2259326A1 (fr) 1975-08-22
CH590435A5 (fr) 1977-08-15
DE2503411A1 (de) 1975-07-31
FR2259326B1 (fr) 1980-07-18
CA1021648A (fr) 1977-11-29
GB1503309A (en) 1978-03-08

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