Method and means of air conditioning

Claim 3

A method according to claim 1 wherein said operative temperature within said conditioned space is controlled by determining said mean radiant and said air dry bulb temperatures and adjusting said air dry bulb temperature to be less than the operative temperature by the same amount as the mean radiant temperature exceeds said operative temperature.

Claim 4

A method according to claim 1 wherein said mean radiant temperature within said conditioned space is determined and further comprising controlling temperature of supply air to said conditioned space to be sufficiently cool to offset the sensible heat load and the effect of said mean radiant temperature on the thermal comfort of occupants within said and controlling said relative air velocity over occupants to be compatible with the operative temperature required for said thermal comfort.

Claim 5

A method according to claim 1 wherein said dehumidifier comprises a plurality of coil portions, a plurality of coil valves interconnecting said coil portions, a plurality of coil bypass tubes, and a throttle valve, said coil portions, coil valves and coil bypass tubes being in a configuration controllable to vary the effective cooling size of said dehumidifier, said method comprising effecting control of said coil valves to bypass flow selectively from portions of the dehumidifier coil through said coil bypass tubes to reduce the effective cooling capacity of the dehumidifier upon reduction of load, but retain said coolant flow through said coil portions to be the equivalent of between 1 and 2.2 meters per second of coolant.

Claim 6

A method according to claim 4 wherein said air conditioner comprises a fan which causes air flow through said dehumidifier, said method comprising limiting said air flow to be sufficiently low that humidity ratio within said conditioned space does not exceed thirteen grams of water per kilogram of dry air, but is not less than four grams per kilogram.

Claim 7

A method according to claim 4 wherein said air conditioner comprises a fan which causes air flow through a plurality of rows of said dehumidifier coil, and the configuration of said coil portions is such that said bypass of coil portions is effected while retaining active coil portions over the whole of a path of said air flow through said rows of dehumidifier coil.

Claim 8

A method according to claim 4 wherein the space is conditioned by a constant air volume system comprising effecting said control by initially maintaining supply air temperature and dehumidifier capacity constant and resetting said air dry bulb temperature in the conditioned space, until the temperature in said conditioned space approaches limits of said narrow comfort zone, and then effecting said control of said coil valves to vary size of said dehumidifier.

Claim 9

A method according to claim 1 further comprising determining volume flow rate of air through said conditioned space, globe thermometer temperature in relevant portions of said conditioned space, and ambient temperature, computing operative temperature, comparing said computed operative temperature with a temperature in said narrow comfort target zone, and effecting adjustment of one at least of (a), (b) and (c) of the steps of claim 1 as required to maintain said space within said narrow comfort target zone.

Claim 10

A method according to claim 1 further comprising determining volume flow rate of air through said conditioned space, globe thermometer temperature in relevant portions of said conditioned space where said globe temperature differs from said air temperature, ambient air temperature, at least one of relative humidity, dew point and humidity ratio in said conditioned space, computing the thermal energy balance for at least one occupant of said space to determine the equilibrium air temperature at which said occupants would be in thermal equilibrium with the environment of said space, and adjusting said air temperature to said equilibrium value while maintaining at least one of humidity ratio between 4.2 and 12 grams of water per kilogram of dry air and relative humidity between 30 and 60 percent.

Claim 11

A method according to claim 1 further comprising effecting said control so that the conditions in said conditioned space require the ratio of air flow in a variable air volume system for fifty percent of the peak sensible heat load to that for said peak sensible heat load to be not less than 0.65.

Claim 16

A method according to claim 12 further comprising calculating the change in sensible heat load in the conditioned space due to the changes in the transmitted heat load and changes in the rates of heat removed from equipment and occupants within said space consequent upon said changes in temperature and relative humidity within said space and employing said calculations in determining the optimum strategy by which said changes are effected.

Claim 17

A method according to claim 13 further effecting change in relative air velocity to maintain the conditioned space within said tolerance band.

Claim 18

A method according to claim 13 further comprising recording both said interrogated and computed data.

Claim 19

A method according to claim 13 wherein said computed balance between net metabolic heat generation by the occupant and the rate at which it is exchanged with the surroundings within said conditioned space is computed from the equation derived by P. O. Fanger and known as the comfort equation and published in the ASHRAE Fundamentals Handbook, 1989, and said tolerance in said balance is evaluated from the condition that the quantity known as the Predicted Mean Vote and published in said ASHRAE handbook shall not be less than -0.5 or greater than +0.5.

Claim 20

An air conditioner according to claim 13 wherein said electronic controller is programmed to reduce the velocity of air flow through a face of a dehumidifier to not more than 0.5 meters per second and to cause coolant to flow through the tubes of at least part of said dehumidifier at a velocity of not less than 1.0 meters per second and not more than 2.2 meters per second for at least part of a period during which said conditioned space is not occupied, such procedure allowing the humidity ratio of the air to reduce to a minimum value without inhibition and thus to dry all deposits of water from the air distribution system and to reduce the moisture content of the building fabric and furnishings within said conditioned space.

Claim 21

An air conditioner for cooling a conditioned space within a relatively narrow comfort target zone as depicted on a psychrometric type chart, itself generally within a relatively broad standard comfort zone, the factors determining said target zone including the heat transfer resistance of occupants'0 clothing and level of physical activity, comprising: a dehumidifier having a plurality of coil portions, a fan located to propel air flow through said coil portions, temperature sensing means comprising a thermometer arranged to ascertain at least one of mean radiant temperature and operative temperature in said conditioned space, humidity sensing means in said conditioned space, and: (a) air control means controlling relative air velocity within occupied regions of said space to lie between 0.05 and 0.30 meters per second, but said air not to exceed a velocity of three meters per second through a face of an air conditioner dehumidifier, (b) temperature control means controlling the temperature of supply air to said space, and dry bulb air temperature within said space, (c) coolant control valve means controlling effective size of said dehumidifier while maintaining coolant velocity through said dehumidifier to between the equivalent of 1 and 2.2 meters per second, and (d) humidity control means coupled to said humidity sensor and to at least one of said temperature control means and coolant control valves to control humidity ratio in said conditioned space to be between four and thirteen grams of water vapour per kilogram of dry air by varying at least one of leaving temperature of the supply air from, effective size of, and coolant flow velocity said dehumidifier when said humidity ratio approaches said four grams per kilogram.

Claim 22

An air conditioner for cooling a conditioned space within a relatively narrow comfort target zone as depicted on a psychrometric type chart, itself generally within a relatively broad standard comfort zone, the factors determining said target zone including the heat transfer resistance of occupants'0 clothing and level of physical activity, comprising: a dehumidifier having a plurality of coil portions, a fan located to propel air flow through said coil portions, temperature sensing means comprising a thermometer arranged to ascertain at least one of mean radiant temperature and operative temperature in said conditioned space, humidity sensing means in said conditioned space, and: (a) air control means controlling relative air velocity within occupied regions of said space to lie between 0.05 and 0.30 meters per second, but said air not to exceed a velocity of three meters per second through a face of an air conditioner dehumidifier, (b) temperature control means controlling the temperature of supply air to said space, and dry bulb air temperature within said space, (c) coolant control valve means controlling effective size of said dehumidifier while maintaining coolant velocity through said dehumidifier to between the equivalent of 1 and 2.2 meters per second, and (d) humidity control means coupled to said humidity sensor and to at least one of said temperature control means and coolant control valves to control humidity ratio in said conditioned space to be between four and thirteen grams of water vapour per kilogram of dry air by varying at least one of leaving temperature of the supply air from, effective size of, and coolant flow velocity said dehumidifier when said humidity ratio approaches said four grams per kilogram.

Claim 23

An air conditioner according to claim 18 wherein said temperature sensing means comprise dry bulb thermometers in supply air to and return air from said conditioned space, and further comprising air flow rate sensing means, ambient air temperature sensing means, and an electronic controller interconnecting said sensing means and control means to effect control of said relative air velocity, dry bulb temperature in said space, supply air temperature, effective dehumidifier size and minimum and maximum humidity in said space.

Claim 24

An air conditioner according to claim 19 wherein said air control means comprises dampers located between said dehumidifier and said conditioned space, and motors coupled to said dampers to control air flow therethrough, and said electronic controller limits relative air velocity to between 0.05 and 0.30 meters per second through the conditioned space.

Claim 25

An air conditioner according to claim 19 wherein said temperature control means comprises said coolant control valve means and said electronic controller varies the number of active coil portions of said dehumidifier to retain coolant velocity through said active coils between 1 and 2.2 meters per second.

Claim 26

An air conditioner according to claim 19 wherein said controller increases the leaving temperature of the supply air when the humidity ratio drops to four grams of water vapour per kilogram of dry air.

Claim 27

An air conditioner according to claim 19 wherein said air control means comprises fan speed control means effected through communication between said air flow control means and said electronic control means.

Claim 28

An air conditioner according to claim 18 wherein said control means are components of an air handling unit, and said air conditioned space comprises a plurality of separate zones, comprising further said sensing means in each of at least some of said zones, and communication means between said further sensing means and said air handling unit.

Claim 29

An air conditioner according to claim 19 wherein the fan and air control means co-operate to deliver ventilation air to said conditioned space at the rate of not less than 7.5 liters of ventilation air per person said ventilation air being that portion f the supply air drawn from outside the building and mixed with recirculated air prior to its passing through the dehumidifier.