Control in combination with thermostatically responsive assembly

Abstract: A control assembly in combination with a thermostatically responsive apparatus. In a preferred mode the principles of the present invention are applied to an infra-red heating system of the type including burner assemblies (12, 12′) connected in series by a heating pipe (14), the assemblies being further connected by heating pipes (14) to a vacuum pump (40). The pump (40) is driven by a variable-speed electric motor (42) which is responsive to a thermostat (16) which may initiate, through control panel (15), operation of the burner assemblies. The burning rate of the burner assemblies is controlled by varying the speed of the electric motor and this is accomplished by the control assembly (44) which is responsive to indoor and outdoor temperature sensing devices (48, 50). The control assembly is initially programmed with climatic data which is correlated with operational speeds of the pump to give desired thermal operational characteristics of the burners at differing temperature ranges.

Description: The present invention relates generally to a thermostatically responsive assembly used for maintaining the temperature within an enclosed space, this invention being illustrated embodied in an infra-red heating system of the type having burner assemblies and radiant heating pipes interconnecting the burner assemblies with a variable-speed vacuum pump. The rate of heating is controlled by a control assembly responsive to indoor and outdoor temperatures, the heating rate of the burner assemblies being varied in accordance with a program stored within the memory of the control assembly which is in turn responsive to climatic data, indoor and outdoor temperatures, and thermostat settings. Thermostatically controlled space-heating and cooling systems are well known in the art. Typical examples are hot-water baseboard heating systems, forced-air cooling systems, and infra-red heating systems. In general, virtually all space-heating and cooling systems in use today have a constant thermal output, which output is selected to provide maximum heating or cooling on those days where the extreme temperature is reached for that area. Most systems which are constructed in the above manner have inherent disadvantages when extremes of temperature are not present. For example, if the system is designed for a temperature differential of 44°C (80°F) (21°C/70°F indoor temperature and a -23°C (-10°F) outdoor temperature), and if there is only a 17°C (30°F) difference between the desired temperature inside and the actual temperature outside (4°C/40°F) the system will tend to overshoot, have poor thermal response, have substantially oversized capacity, and poor thermal efficiencies. When heating an enclosure with a radiant-heating system, such as the type sold under the trade name Co-Ray-Vac by Roberts-Gordon, Inc. of Buffalo, New York, it should be recognized that the greatest heating efficiencies are achieved when the unit is operating at design capacity. Thus, in the example given above, the Co-Ray-Vac system when installed in accordance with design specifications, is fully condensing at -23°C (-10°F) outside temperature. However, when operating at 4°C (40°F) outside temperature, although the system will still be fully condensing, it will tend to overshoot when heating, it will have substantially oversized capacity, and will inherently have poor fuel utilization efficiencies due to short cycles and large temperature swings. It should also be apparent that with such a system that there are constructional costs incidental to having the system fully condensing at design temperatures, where the system is most fuel efficient. However, the condensing radiant pipe or tail pipe, while needed to be of a greater length when the system is operating at its maximum temperature extreme, need not be so long when the system is operating at a temperature considerably less than the extreme. In summary, it should be noted that such systems, when designed to maximum temperature ranges, operate most efficiently only during a very small fraction of the time and also require greater capital costs of installation. It is an object of the present invention to provide a control assembly in combination with a thermostatically responsive assembly used for maintaining the temperature within an enclosed space at a desired temperature setting, the thermostatically responsive assembly having a variable thermal output during its operation, and the control assembly being capable of comparing the indoor and outdoor temperatures and causing the thermostatically responsive assembly to operate at thermal outputs proportional to the actual differences between indoor and outdoor temperatures whereby greater thermal efficiencies may be achieved over a range of conditions with a lower capital investment. The present invention is defined in the appended claims. Advantages of this invention will be more apparent from a consideration of the following detailed description taken in conjunction with the accompanying drawings in which one preferred form of this invention is illustrated. FIG. 1 is a partially schematic view illustrating how the principles of this invention may be applied to an infra-red heating system. FIG. 2 is a schematic layout of an alternate design of an infra-red heating system to which the principles of the present invention may be applied. FIG. 3 is a table showing climate design data. FIG. 4 is a graph showing the climate design data set forth in FIG. 3. Detailed Description The control assembly for the present invention is illustrated in FIGs. 1 and 2 in conjunction with a space-heating system of the infra-red type. Thus, a building 10 is partially shown in FIG. 1, and the space within the building is the enclosed space which is to be heated. The infra-red space-heating system illustrated in FIG. 1 includes burner assemblies 12, which burner assemblies are coupled to radiant heating pipes indicated generally at 14. More than a single burner assembly is shown in FIG. 1, the second burner assembly being identical to the first burner but being indicated at 12′. It should the noted at this point that a single burner assembly can be connected to the heating pipes 14, or a plurality of burner assemblies such as burner assemblies 12 and 12′, may be connected to the heating pipes 14 in series. In addition, as indicated in FIG. 2 burner pipes 14 may be connected to each other in parallel as well as in series. Each of the burner assemblies 12 is a thermostatically responsive unit and to this end each of the burner units is coupled to a control panel 15 which is also coupled to a thermostat 16. When the temperature within the building 10 drops below the setting of the thermostat 16 a signal will be initiated by the control panel to cause of the operation of the burner assemblies in a manner which will be more fully described below. Each of the burner assemblies 12 and 12′ includes a combustion chamber 17 which has a generally cylindrical cross-sectional configuration, there being a burner head 18 disposed within the combustion chamber. Fluid control means, indicated generally at 19 (or 19′), are provided for initiating a flow of combustible gases to the burner 18 and are mounted within a housing or enclosure 20. Each of the fluid control means 19 includes a combustible gas supply including a zero-pressure regulator 22, a control valve 24, and a restrictor or orifice 26. An air line joins the gas line downstream of the orifice 26, the air line also being provided with an orifice 28 and an air filter 30, which filter may be mounted on the exterior of the housing 20. If the solenoid-controlled valve 24 is switched to an open position, as shown in FIG. 1, and if a vacuum is drawn at the burner 18, a mixture of air and gas will be drawn through the burner 18, which mixture will have the same proportion to one another at all vacuums. Thus, if the vacuum within chamber 17 is increased the flow of air and gas will be increased thereby increasing the fueling or burning rate. This form of construction of a burner head and fluid control means is well known in the art and is commercially available from Roberts-Gordon under the trade name Co-Ray-Vac and is also illustrated in U.S. Patent 3,394,886. The heating pipes 14 are coupled to the combustion chamber 17 by couplings 32. The heating pipes include radiant pipes 34 which extend between the burner assemblies 12 and 12′ and which also extend away from the last burner assembly 12 in the series. The last radiant pipe 34 in the series is coupled to a tail pipe or condensate pipe 36 by a further coupling 38 which may be provided with a suitable damper. The end of the tail pipe furthest away from the burner assembly 12 is in turn coupled to the inlet of a vacuum pump 40, which vacuum pump discharges gases to the exterior of the building. While not shown, the vacuum pump has associated therewith a condensate collector. The system described up to this point is commercially available under the trade name of Co-Ray-Vac from Roberts-Gordon, Inc. in Buffalo, New York. These systems may be configured to differing buildings and when built in accordance with design specifications they are fully condensing systems at the maximum rated heating load. Thus, while the gases passing through the radiant pipes 34 are above the boiling point of water, as the gases pass through the tail pipes 36 the temperature falls below the boiling point of water to permit the water vapor to condense. Accordingly, the tail pipes are typically lined with a porcelainized material to prevent these pipes from rusting. In prior art designs the burners are typically operated at their rated capacity by drawing a vacuum thereon equal to 6.35 cms (2.5 inches) of water on the end vent of that burner furthest away from the pump 40, the end vent being illustrated at 41 in FIG. 1. Thus, the damper in coupling 38 will normally be so positioned that a vacuum equivalent to 6.35 cms (2.5 inches) of water will be drawn at the end vent 41 during operation of the pump. This will be the case whether or not the space-heating system is designed as in FIG. 1 with just a single line or whether there are plural lines as in FIG. 2. In prior art designs the pump has been driven at a single speed. However, it has been recognized that by varying the speed of the pump it is possible to vary the thermal output of each of the burner assemblies 12. Thus if a vacuum is drawn at end vent 41 equal to 6.35 cms (2.25 inches) of water the infra-red heating system will be caused to be operated at approximately 90 percent of its rated capacity. For example, if the burner assembly 12 (or 12′) is rated at 14.1 kW (50,000 Btus per hour), it will have that output at 5.72 cms (2.5 inches) of vacuum at the end vent 41. However, if the vacuum pressure at end vent 41 is only 5.72 cms, (2.25 inches) of water then the output will be reduced from 14.7 kW (50,000 Btus) to 13.2 kW (45,000 Btus per hour), because there will be a lower fueling rate as less air and less gas will be introduced into the burner assembly. Existing systems are designed so that they can heat a building satisfactorily 99 percent of the time in accordance with standard ASHRAE procedures. Thus a heating system is designed to provide maximum heating for an outside temperature which is reached in only one day out of 100. Thus, most of the time the heating capacity designed into a system is not fully utilized. This causes inefficiencies in operation and temperature swings within a building when the system is only operating now and then. It has been additionally recognized that when the output speed of the pump is varied to draw proportionately smaller vacuums, the burner assemblies will have lower thermal outputs, leading to greater thermal efficiencies in operation. In addition, because of the greater efficiencies in operation of lower vacuums (or outputs) it is also possible to reduce the capital costs of such a system since they need not be designed for the most extreme days. Thus, a system can be designed which is only fully condensing 90 percent of the time but which will operate at much higher efficiencies when the differences between indoor and outdoor temperatures are not extreme by reducing the thermal output of the burner assembly. Therefore, in accordance with these principles, a variable-speed electric motor 42 is provided for driving the pump 40 and an operational control means 44 for controlling the thermal output is also provided, which operational control means is coupled on its output side to an electric motor speed control module 46 and on its input side to indoor and outdoor temperature sensing devices 48 and 50. The operational control means 44 includes a microprocessor and it is coupled with the motor speed control 46 in such a manner that the operational speed of the motor 42 can be varied to establish various end vent vacuums dependent upon climatic data programmed into the control means 44. The characteristics of the present invention can be more fully understood from the following discussion of the manner in which a system of the present invention is designed and started up. Initially, an engineer will determine the heat loss for the enclosed space, say the entire space within the building 10, by using standard ASHRAE procedures and considering the lowest design temperature (99 percent occurrence level temperature; that is, the temperature which occurs only 1 percent of the heating season). As can be seen from the data set forth in FIGs. 3 and 4 which are specific for the Los Angeles, California, heating season of December, January, and February, the lowest design temperature would be approximately 5°C (41°F). The engineer would next choose a burner or burners having the desired thermal output based upon the desired temperature to which the building is to be heated on the coldest days, for example 21°C (70°F). The system lay-out would then be designed using the required number of burners to satisfy the heat loss based upon the previous considerations. The engineer will next determine programming check points to be used in the installation to set up the program of the operational control means 44. The check points will be the difference between indoor and outdoor temperatures (the indoor temperature less the outdoor temperature) at 99 percent, 90 percent, 80 percent, 70 percent, and 60 percent occurrence levels. As can be see from FIG. 4 the graph these check points will occur at 7°C (45°F), 9°C (49°F), 11°C (51°F), and 12°C (53°F), respectively. Thus, at 5°C (41°F) there will be a 16°C (29°F) temperature difference, at 7°C (45°F) there will be a 14°C (25°F) difference, at 9°C (49°F) a 12°C (21°F) difference, at 11°C (51°F) a 11°C (19°F) difference, and at 12°C (53°F) a 9°C (17°F) difference. The engineer is now ready to start up the system. Initially, all of the burner assemblies will be energized by raising the thermostat 16 to a suitable level. When this occurs, the control panel will initially cause the motor 42 to operate to purge the system. Then, after a limited period of time, the valves 24 will open and the burners 18 will be ignited in a manner well known to those skilled in the art. During the initial start up, the entire system will be allowed to come to an equilibrium which will take approximately 30 to 45 minutes. At this point in time the pump speed 40 will be adjusted to its maximum level. This is done by adjusting control knob 52 of the operational control means which will in turn, acting through control lines 54 adjust the electric motor speed control module in such a manner that the speed of the pump 40 is increased to its maximum rate. The system will now be balanced out by using the dampers in couplings 38 so that each branch end vent will draw 6.35 cms (2.5 inches) water column. After the system has been balanced to provide 6.35 cms (2.5 inches) of water column vacuum at each branch end vent it is now necessary to program the operational control means. This is done by pressing the program button 56 in the operational control means 44. Initially, the stage one indicator 58 lights to indicate that programming is in process. One hundred percent delta T (16°C/29°F in the Los Angeles example) will now be dialed in by control knob 60, the delta T being shown in indicator panel 62 which may consist of standard light emitting diodes. After the 100 percent delta T has been dialed in the program button 56 is again pressed. At this time the 100 percent speed capacity has been stored with the 100 percent delta T input data. When the program button is pressed the second time the stage two indicator 64 lights. The manual speed control knob 52 will be adjusted to give a 5.72 cms (2.25 inches) end vent vacuum and a 90 percent delta T will be dialed in by control knob 60, this being 14°C (25°F) in the Los Angeles example. The program button 56 will again be pressed causing the 90 percent speed capacity and the 90 percent delta T input data to be stored and also to commence stage three programming which will be indicated by light 66. The manual speed control will now be adjusted to a 4.45 cms (1.75 inch) end vent vacuum and the 80 percent delta T (12°C/21°F in the Los Angeles example) will now be dialed in. When the program button 56 is again pressed the fourth light 68 will come on to indicate that the fourth stage should be programmed, the third stage programming having been stored in memory. To continue with the Los Angeles example, during the fourth stage a 70 percent vacuum of 3.18 cms (1.25 inches) water column is dialed in through control knob 52 and the 70 percent capacity delta T of 11°C (19°F) is stored in memory. During the fifth stage a 60 percent of 1.9 cms (0.75 inches) water column is adjusted through control knob 52 and the 60 percent capacity of delta T of 0°C (17°F) is dialed in. The programming is completed after the fifth stage by dialing in the target indoor temperature of 21°C (70°F) in the example given. The program button is then pressed one last time to turn off all stage indicator lights and to set the program. The foregoing programming is required as the algorithm embedded within the microprocessor is not empirically capable of setting the motor speed control as the vacuum drawn on the end vent is dependent upon the overall layout of the system and is not directly proportional to pump speed. In any event, the microprocessor utilizes the following algorithm: where SP = indoor ambient control set point (target temp.) t i = instantaneous indoor temperature t o = instantaneous outdoor temperature t act = instantaneous building envelope differential temperature = (t i - t o ) K = constant F = correlation function of (SP t o ) V = function signal (output from control) determining vacuum pump operating speed NOTE: Correlation function (F) is determined via programming of the control means with datum points specific to an application site's climate history. The functional signal V will determine the firing capacity of the burner. For example, again using the Los Angeles climate data, when the indoor temperature is 18°C (65°F) and the outdoor temperature is 5°C (41°F), with K being equal to 1, the signal to function processor is equal to 1.2 times F or a firing capacity of 100 percent. If the indoor temperature is an actual 21°C (69°F) and the outdoor temperature is 9°C (49°F) the firing capacity will be approximately 84 percent. If the indoor is 21°C (69°F) and the outdoor is 12°C (53°F) the firing capacity will be approximately 63 percent. If the indoor temperature is an actual 20°C (68°F) and the outdoor temperature is an actual 14°C (58°F) the firing capacity will be at 72 percent. In this connection it should be noted that the minimum firing rate programmed into the microprocessor will be a 60 percent firing rate and this is subjectively determined based upon the system so that undue stress areas will not be created when firing at too low a rate.

Claims: A radiant-heating system of the type having a burner assembly (12,12′) for burning combustible gas and air, heating pipes (14), and thermostatically operated control means (15) for initiating a control signal, the burner assembly including a combustion chamber (17), a burner head (18) disposed within the combustion chamber, and fluid control means (19) for supplying air and combustible gas to the burner head (18) in response to the control signal, the heating pipes (14) extending away from the combustion chamber (17) and the products of combustion being conveyed through the heating pipes, the heating pipes including a radiant pipe (34) coupled to the combustion chamber and a tail pipe (36) coupled to the radiant pipe; characterized in that: the fluid control means (19) is operable to supply combined air and combustible gas to the burner head (18) in response to both the control signal and a variable below-ambient pressure in the combustion chamber (17), the volume of both the air and the combustible gas, and hence the fueling rate within the combustion chamber, varying in proportion to the variable pressure differential between ambient and the below-ambient pressure, and in that the radiant-heating system further comprises: a variable-speed vacuum pump assembly (40,42,46) coupled to the tail pipe and capable of operating at varying speeds to vary the below ambient pressure and hence the fueling rate within the combustion chamber, the pump assembly including a pump (40), and a variable-speed drive (42,46); and a control assembly (44,48,50) for varying the operating speed of the vacuum pump assembly (40,42,46) to thereby vary the fueling rate of the burner assembly when the operation of the burner assembly has been initiated. The radiant-heating system as set forth in claim 1 wherein a plurality of burner assemblies (12,12′) are provided, which burner assemblies are coupled to each other in series by radiant pipes (34) which extend from one combustion chamber to another, and wherein the tail pipe (36) is coupled at one end to the last radiant pipe in series and at the other end to the variable-speed vacuum pump (40). The radiant-heating system as set forth in claim 1 wherein the control assembly (44,48,50) for varying the operating speed of the vacuum pump assembly includes inside and outside air temperature measuring devices (48,50), and operational control means (44) for matching the actual heating requirement to the heat load on a nearly instant basis by responding to the calculated air temperature difference between the air temperature measured inside the space being heated and the temperature measurement of outside air. The radiant-heating system as set forth in claim 3 wherein the operational control means (44) is provided with climate design data. The radiant-heating system as set forth in claim 4 wherein the climate design data is in the form of design temperature profiles which establish intermediate operational speeds of the vacuum pump to in turn create differing below ambient pressures within the heating pipes and the combustion chamber so that differing fuel rates may be achieved whereby greater thermal efficiencies may be achieved over a range of conditions with a lower capital investment. The radiant-heating system as set forth in claim 3, wherein the operational control means is a programmable device which initiates a signal to the variable speed drive (42,46) dependent upon the temperature difference between indoor and outdoor temperatures and the thermostat set point designed into the system. The combination as set forth in claim 6 wherein the operational control means is initially programmed with climate design data and a desired temperature for the space being heated. The combination as set forth in claim 7 wherein the climate design data programmed into the operational control means includes the maximum temperature difference between the desired temperature for the enclosed space and the extreme temperature encountered outside of the enclosed space during only 1 percent of season. The radiant-heating system as set forth in claim 1 wherein the variable-speed drive (42,46) is further characterized by a variable-speed electric motor (42), and an electric motor speed control module (46); wherein the thermostatically operated control means is further characterized by a thermostat, and a control panel (15) connected to the thermostat for initiating power flow to the electric motor speed control module (46) and a control signal to the fluid control means (19) upon receipt of a signal from the thermostat; and wherein the control assembly (44,48,50) further includes indoor and outdoor temperature measuring devices (48,50), and operational control means (44) for comparing the indoor and outdoor temperatures and causing the electric motor speed control module (46) to cause the variable-speed electric motor (42) to operate at a speed selected by the operational control means to provide a thermal output of the burner unit proportional to the actual differences between outdoor and indoor temperatures whereby the radiant-heating system provides for greater thermal efficiencies over a range of temperatures at a lower capital investment.

Inventors: SEEL TIMOTHY P, SEEL, TIMOTHY P.
Applicants: ROBERTS GORDON INC A DELAWARE, ROBERTS-GORDON, INC. (A DELAWARE CORPORATION)
Application year: 1991
Main classification: F23N1
IPC codes: F23N5, G05D23, F23N1, F24D5