Air conditioning systems for at least two rooms using a single outdoor unit.

(54) Title: AIR CONDITIONING SYSTEMS FOR AT LEAST TWO ROOMS USING A SINGLE EXTERIOR.

(54) Title: AIR CONDITIONING SYSTEMS FOR AT LEAST TWO ROOMS USING A SINGLE OUTDOOR UNIT.

(57) Summary

A highly efficient air conditioning system to condition a plurality of rooms within a building interior, the air conditioning system includes: two separate rooms within a construction, a single outdoor unit, a refrigerant flow path that includes a plurality of refrigerant lines having a common refrigerant flow path portion and at least two divergent flow path portions, a first divergent flow path where the first evaporator of the second evaporator are parallel to each other; at least one regulating device and at least a first interior air conditioner placed inside and that provides cooling to the first room and a second interior air conditioner placed inside and that provides cooling to a second room. The compressor is unable to simultaneously supply the first evaporator and the second evaporator in full cooling capacity.

(57) Abstract

A high-efficiency air conditioning system for conditioning a plurality of rooms within an interior of a building, the air conditioning system including: two separate rooms within a building, a single outdoor unit a refrigerant flow pathway that includes a plurality of refrigerant conduits having a common refrigerant flow path portion and at least two divergent flow path portions, a first divergent flow path where the first evaporator and second evaporator are in parallel with one another; at least one throttling device and at least a first indoor air handling unit positioned within and providing cooling to the first room and a second indoor air handling unit positioned within and providing cooling to a second room. The compressor is incapable of simultaneously supplying both the first evaporator and the second evaporator at their full cooling capacity.

AIR CONDITIONING SYSTEMS FOR AT LEAST TWO ROOMS

THAT USE A UNIQUE EXTERIOR

DESCRIPTION OF THE INVENTION

Air conditioning systems for construction, housing or historically used conditioners for individual room structures have a standard vapor compression cooling system to cool an interior volume of a construction structure containing walls and / or ceilings.

A traditional home or construction air conditioning system is shown schematically in Figure 1. As shown there, the air conditioning system typically includes an outdoor positioned machine compartment housing mounted on a base platform where the housing contains a single outlet, a single inlet compressor, a condenser, and a thermal expansion device. These traditional systems also typically include a fan associated with a condenser, the size of which depends on several factors. For complete housing / construction systems, where the compressor and condenser must provide high cooling capacity, the systems are sized to match the thermal load and are typically large. The refrigerant fluid lines supply the refrigerant through a steam compression system and supply the refrigerant fluid that passed through the compressor, condenser, and regulator device to a single evaporator that operates on a single evaporator pressure located within a air passage within the construction structure. The air passage may be an air duct, air vents from a room air conditioning system, or a portion of the interior ventilation machine and heating air conditioning compartment located within the construction structure. Typically, the evaporator is placed inside the building heating ventilation and air conditioning machine compartment. The air passage typically has an air circulation fan associated with it to distribute air through the building frame or into a portion of the building frame. The air circulation fan supplies the air through the only evaporator where it cools and the cold air distributed to the volume of the indoor air to be cooled. The air is returned to the evaporator. Typically, a building structure can have an outside air inlet / path that allows outside air to enter, typically passively enter, the building structure from outside the building structure directly into the air passage or into air from the building structure where the outside air is then circulated within the building structure.

While that system cools the interior of the construction structure, it typically does not allow for temperature and humidity regulation of the interior of a construction structure. When using this traditional air conditioner, moisture is removed based on the temperature of the single evaporator. A person within the interior volume of the construction structure may wish

<td>that moisture is removed more</td><td colspan="2">or less</td><td>of the</td><td colspan="2">air inside the</td>

<td>construction structure of</td><td>the</td><td>than</td><td>I know</td><td>It allows</td><td>for such</td>

<td>single evaporator systems. One other aspect</td><td>of</td><td>the</td><td colspan="2">Present</td><td>description</td>

it generally includes a high-efficiency air conditioning system to condition a plurality of rooms within a building interior. The air conditioning system typically includes: two separate rooms within a building; a single outdoor unit comprising: a compressor, a condenser, and a condenser fan associated with the condenser that moves air to cool the condenser;

a refrigerant refrigerant refrigerant flow path comprised of a plurality of conduits of which have a common flow path portion and at least two divergent flow path portions, a first divergent flow path supplying refrigerant to a first evaporator configured to operate at a first evaporator pressure and a second diverging flow path supplying refrigerant to a second evaporator so that the first evaporator and the second evaporator are in parallel each; at least one regulating device where a single regulating device is placed along a common flow path where a single regulating device is used and a first regulating device is placed along the first diverging flow path and a second device Regulator is placed along the second diverging flow path where two or more regulating devices are employed; and at least a first indoor air conditioner placed inside and providing cooling to a first room and a second indoor air conditioner placed inside and providing cooling to a second room. The first indoor air conditioner typically includes the first evaporator and a fan configured to supply cooling to the first room, and the second indoor air conditioner typically includes the second evaporator and a fan configured to supply cooling to the second room. The compressor is unable to simultaneously supply the first evaporator and the second evaporator in full cooling capacity.

Still another aspect of the present invention typically includes the high efficiency air conditioning system for conditioning a plurality of rooms within a building interior that includes two separate rooms within a building; a single outdoor unit comprising: a housing with a compressor, a condenser, a condenser fan placed inside the housing where the condenser fan associates with the condenser and is configured to move air to cool the condenser and the compressor is either a double suction compressor or a single suction compressor with a switch mechanism placed externally or within a compressor housing that allows two or more fluid intake ducts to feed a single suction port to the. single suction compressor. The compressor can be sized and configured to supply the first indoor air conditioner and the second indoor air conditioner on an equal or proportional basis to the demand for a given cooling level or dehumidification level at two different suction pressures.

a zone

The system further generally includes a coolant flow path consisting of a plurality of coolant lines having a common coolant flow path and at least two divergent flow path portions, a first divergent flow path supplying the refrigerant to a first evaporator that can be configured to operate at a first evaporator pressure and a second diverging flow path supplying refrigerant to a second evaporator that can be configured to operate at a second evaporator pressure such as the first evaporator and the second evaporator that are parallel to each other; at least one regulating device where the regulating device is placed along the common flow path when a single regulating device is used and a first regulating device is placed along the first diverging flow path and a second regulating device is placed along the second diverging path when two or more regulating devices are used; at least a first interior air conditioner placed inside a first room and a second air conditioner placed inside a second room. The first indoor air conditioner typically includes the first evaporator and a fan, and the second indoor air conditioner typically includes the second evaporator and a fan. The compressor is unable to simultaneously supply the first evaporator and the second evaporator in their full cooling capacity; and where the plurality of refrigerant lines that make up the refrigerant flow path are free of any check valve.

Still another aspect of the present disclosure generally includes a method of using an air conditioning system of the present disclosure to sequentially supply refrigerant to the first evaporator through the first divergent flow path or the second evaporator through the second divergent flow path and the compressor to independently provide cooling capacity of the first evaporator or the second evaporator. The methods of the present disclosure may also include the first evaporator and second evaporator stage which are disjointed evaporators and the compressor is a double suction compressor with a first suction port operably connected to the first evaporator and a second discharge port. suction operably connected to the second evaporator by independently regulating temperature and humidity within the zone associated with the first evaporator and the zone associated with the second evaporator.

These and other features, advantages, and objects of the present disclosure will be further understood and appreciated by those skilled in the art by reference to the following specification, claims, and accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

The above summary, as well as the following detailed description of the description, will be better understood upon reading in conjunction with the accompanying drawings. For the purpose of illustration of the disclosure, certain currently preferred aspects are shown in the drawings. It should be understood, however, that the description is not limited to the precise provisions and instruments shown. Drawings are not necessarily to scale, but relative special relationships are shown and drawings may be to scale especially where indicated. As such, in the description or as may be apparent to those skilled in the art, certain features and the description may be exaggerated in scale or shown schematically in the interest of clarity and conciseness.

Figure 1 is a schematic view of the traditional air conditioning system employing a single evaporator operating at a single evaporation pressure and a single inlet and single outlet compressor;

Figure 2 is a schematic view of an air conditioning system for a construction structure according to one aspect of the present disclosure employing a double suction compressor and two evaporators operating at different evaporation temperatures;

Figure 3 is a schematic view of an air conditioning system for a building structure according to one aspect of the present disclosure employing a double suction compressor and two evaporators operating at two different operating temperatures with an evaporator treating the air taken in from the outside air and then into the air passage of the air conditioning system;

Figure 4 is a schematic view of an air conditioning system for a construction structure in accordance with one aspect of the present disclosure employing a dual suction compressor, variable temperature evaporators operating at two independent evaporation temperatures and one proportional double suction valve;

Figure 5 is a detailed schematic view of the air conditioning system of Figure 4 having a double suction valve, dual variable expansion devices, and variable temperature evaporators serving in different volumes within the same construction structure;

Figure 6 is a schematic view of an air conditioning system for a construction structure in accordance with one aspect of the present disclosure employing a single suction compressor, a proportional fluid refrigerant control valve, dual variable expansion devices. , and dual variable temperature evaporators serving in different spaces within a structure such as a home;

Figure 7 is a schematic view of a central air conditioning system for a building structure in accordance with one aspect of the present disclosure employing a single indoor unit serving multiple indoor air conditioners;

Figure 8 is a schematic view of a traditional central air conditioning system for a construction structure employing a single outdoor unit serving a single air conditioner;

Figure 9 is a schematic view of a traditional central air conditioning system for a construction structure employing dual outdoor units that independently serve their separate indoor air conditioners;

Figure 10a is a thermodynamic cycle of a double suction and double discharge compressor containing the treatment system that can be used in connection methods to improve the efficiency of the air conditioning system in accordance with one aspect of the present description;

Figure 10b is a thermodynamic cycle of a double discharge compressor containing the air treatment system that can be used in connection methods to improve the efficiency of the air conditioning system in accordance with one aspect of the present description;

Figure 11 shows a compressor according to an aspect of the present description showing double suction;

Figure 12 shows another aspect of a single-suction compressor employing a three-way valve inside the compressor or outside the compressor housing (the housing shown by the dashed line) in accordance with an aspect of the present description that allows suction double;

Figure 13 shows another aspect of a compressor employing two solenoid valves inside the compressor or outside the compressor housing (the housing shown by the dashed line) in accordance with an aspect of the present disclosure showing double suction;

<td>the</td><td>Figure</td><td>14 to</td><td>is</td><td>a sight</td><td>schematic</td><td>of a</td>

<td>compressor</td><td>download</td><td colspan="2">Double of</td><td>suction;</td><td></td><td></td>

<td>the</td><td>Figure</td><td>14b</td><td>is</td><td>a sight</td><td>schematic</td><td>of a</td>

single discharge compressor with a dual discharge switching mechanism;

Figure 15 is a schematic view of a double discharge compressor containing the air conditioning system of the type described in the thermodynamic cycle of Figure 4b according to one aspect of the present description;

Figure 16 is a schematic view of a double suction and double discharge compressor containing the air conditioning system of the type described in the thermodynamic cycle of Figure 4b in accordance with an aspect of the present description;

Figure 17a is a schematic side view of an evaporator system in accordance with one aspect of the present disclosure employing evaporator coils that operate at different temperatures and interface with common fins;

Figure 17b is a schematic elevated side view of the evaporator of Figure 17a;

Figure 18a is a schematic side view of an evaporator system in accordance with one aspect of the present disclosure employing evaporator coils operating at different temperatures that are disconnected by having fins on an evaporator constructed and aligned to feed the flow of air in the fins of the low temperature evaporator;

Figure 18b is an elevated schematic side view of the evaporator of Figure 18a;

Figure 19 is a schematic view of an air conditioning system for a construction structure in accordance with an aspect of the present disclosure employing a cooling reduction mode having a parallel expansion device and two two-way solenoid valves. ;

Figure 20 is a schematic diagram showing the cooling rate of an air conditioning system using a maintenance / normal stage and a cooling reduction stage;

Figure 21 is a thermodynamic cycle of an air conditioning system using a maintenance / normal stage and a cooling down stage that can be used in conjunction with methods to improve the efficiency of the air conditioning system in accordance with an aspect of the present description;

Figure 22 is a schematic view of another aspect of the present disclosure showing an updated air conditioning thermal storage system;

Figure 23 is a schematic view of another aspect of the present disclosure showing an updated air conditioning thermal storage system;

Figure 24 is a schematic view of a split air conditioning system in accordance with another aspect of the present description;

Figure 25 is another schematic view of a single outdoor air conditioning system in accordance with another aspect of the present description;

Figure 2 6 is a schematic view of a wall mounted dual air conditioning system in accordance with another aspect of the present description for serving two areas within a single room;

Figure 27 is a schematic view of a floor mounted double split air conditioning system in accordance with another aspect of the present disclosure to serve two zones within a single room;

Figure 27A is a schematic view of a floor mounted double split air conditioning system in accordance with an aspect of the present disclosure where the indoor unit on the right side has a fan that nine a higher volume of air than the indoor unit on the left side, this forms a large volume of air conditioning on the right side of the room;

Figure 27B is a schematic view of a floor mounted double split air conditioning system in accordance with an aspect of the present description where the indoor unit on the right side has a fan that has a similar volume of air as the indoor unit. on the left side, therefore forms substantially equivalent air conditioning zones on the left and right side of the room;

Figure 27C is a schematic view of a floor mounted double split air conditioning system in accordance with an aspect of the present disclosure where the indoor unit on the left side has a fan that is nine high volume of air than the indoor unit on the right side, therefore forms a large volume of air conditioning on the left side of the room;

Figure 28 is a cross sectional view of a wall mounted split air conditioning unit taken along line XXVIII-XXVIII;

Figure 29 is a cross sectional view of a floor mounted split air conditioning unit taken along line XXIX-XXIX;

Figure 30 is a perspective view of a wall mounted split air conditioning system in accordance with another aspect of the present disclosure;

Figure 31 is a cross sectional view of a wall mounted split air conditioning unit taken along line XXXI-XXXI;

Figure 32 is a schematic view of a single wall mounted split air conditioning system in accordance with another aspect of the present disclosure to serve two zones within a single room with two evaporator systems within the same housing;

Figure 33 is a schematic view of a single wall mounted split air conditioning system in accordance with another aspect of the present disclosure to serve two zones within a single room;

Figure 34 is a schematic view of a proportional refrigerant flow dividing valve in accordance with the aspect illustrated in Figure 33;

Figure 35 is a schematic view of a floor mounted single partition unit air conditioning system in accordance with another aspect of the present disclosure to serve two zones within a single room; and Figure 36 is a schematic flow diagram illustrating a method of operating an air conditioning system that uses a single speed compressor and two variable temperature evaporators.

Before the subject description is described below, it should be understood that the description is not limited to the particular aspects of the description described below, since variations of the particular aspects can be made and still fall within the scope of the appended claims. It should also be understood that the terminology used is for the purpose of describing particular aspects, and is not intended to be limiting. Rather, the scope of the present disclosure will be established by the appended claims.

Where it provides a range of values, it is understood that each intervention value, to the tenth part of the unit of the lower limit, unless the context clearly indicates otherwise, between the upper and lower limit of this range, and any other value established intervention in this established margin, is covered within the description. The upper and lower limits of these sticky margins can be included independently in smaller margins, and also be covered within the description, subject to any limits specifically excluded in the established margin. Where the established range includes one or both of the limits, the ranges that exclude one or both of these included limits are also included in the description.

In this specification and in the appended claims, the singular forms one, one and the include plural references unless the context clearly indicates otherwise.

The present disclosure is generally directed toward more efficient air conditioning systems 110, improved for construction structures 2. Air conditioning systems 110 relative to building structure air conditioning systems 110 that treat air within all or a portion of the interior of a building structure. The systems discussed herein can be used as complete construction treatment systems, one-room air conditioning systems, such as those regularly used by hotels, and all intermediate dimensioned systems. Conceivably, the systems can be used to treat only a portion of a single room. In various aspects, as illustrated in Figures 2635, the air conditioning system 110 can also be used to treat different areas 54, 56 within a single room 52. In such an aspect, an occupant of one side of a room 52 could adjust the temperature within a first zone 54 comprising a portion of room 52 in a first temperature, and a second occupant located in a second zone 56 of that Room 52 can maintain that second zone 56 at the same temperature, a higher temperature, a lower temperature, depending on the preference of the occupants within the various zones 54, 56 of room 52. Essentially, systems can be scaled as desired to work to treat any volume of internal space within a building or room structure as desired.

As shown in Figure 2, air conditioning systems 110 in accordance with various aspects of the present description for building structures or individual rooms use a steam compression cooling system to cool an interior volume of a building structure 2 employing a double suction compressor 116 (Figure 2), a double suction double discharge compressor 117 (Figure 16) or a double discharge compressor 119 (Figure 24) As shown in Figure 2, the air conditioning system 110 typically includes an externally mounted machine compartment housing 112 mounted on a base platform 114 where housing 112 contains a double suction compressor 116, a condenser 118, and a number of thermal expansion devices 120 that typically match the number of evaporators in the system. In several ways, the capacitor can be mounted on an exterior wall of a structure, such as a high-rise home or hotel. The air conditioning systems 110 of the present disclosure also typically include one or more fans 122 associated with condenser 118, the size and number of these depends on various factors. For complete building (home) systems that require more cooling capacity, the compressor and condenser must provide a higher cooling capacity, the fans are larger, and / or move the air at a faster rate to cool the condenser properly

In various alternative aspects, as illustrated in Figures 4-5, the air conditioning system 110 may include a reduced double suction compressor 116 operating at a single speed. Compressor 116 may be such that the reduced total cooling double suction capacity provided by the compressor

116 Double reduced suction is not sufficient to independently cool the full volume of the build 2 at the highest cooling level. However, given the complete construction, the reduced double suction compressor 116 can more efficiently cool the interior volume of a construction structure 2 as discussed in more detail herein.

In this regard, a suction valve 60 proportionally regulates the flow of refrigerant through the first and second evaporator circuits 64, 66 of the air conditioning system 110. The suction valve 60 in that regard operates to regulate the volume of flow of 62 vaporized refrigerant provided on suction lines 7 4 of each evaporator

64, 66. Accordingly, the suction valve is disposed proximate to compressor 116 where double suction lines 74 are joined to reshape the common suction section that runs through the compressor. The double suction valve may be arranged within a common suction manifold or the double suction valve 60 may be an external double suction valve positioned outside the housing. Double suction valve 60 draws refrigerant 62 through evaporator 64, 66 in a controller so that refrigerant 62 flows through first and second evaporators 64, 66 at the same Index or at different rates depending on the charge of cooling required for the respective zones 50 served by the first and second evaporators 64, 66. In this way, a variable speed compressor is not necessary to provide varying amounts of refrigerant 62 in the various evaporators of the air conditioning system 110.

In operation, the temperature and humidity sensors arranged within each of the various zones 50 served by the air conditioning system 110 communicate with the compressor 116, valve 60, respective evaporators 64, 66 and other portions of system 110 air conditioners that include an optional computer control system to provide information regarding the status of a particular zone. The status information provided may include temperature, relative humidity, and information related to the comfort level of the particular area. The air conditioning system 110 uses this status information and the predetermined set points programmed into the system and / or selected by the user in zone 50 to communicate to the suction valve 60 the appropriate position of valve 60 to sufficiently regulate the flow of refrigerant 62 to each of the evaporators 64, 66 in the system in an efficient manner. Where a zone 50 needs additional cooling or dehumidification, the suction valve 60 changes position to allow a predetermined amount of refrigerant 62 to flow to the evaporator serving this zone to provide the appropriate level of cooling or dehumidification. When conditions in zone 50 change so that space 50 requires more, less or no cooling, or additional dehumidification, suction valve 60 again changes position to adjust the flow of refrigerant 62 to evaporators 64, 66 at only that amount necessary to perform the various functions of the air conditioning system 110 as in particular zone 50.

The air conditioning system 110 operates the suction valve 60 to match the evaporator temperature to the current conditions in room 52 by adjusting the position of the suction valve 60 to proportionally move the refrigerant 62 through the evaporators 64 , 66. The flow of refrigerant 62 through the evaporators 64, 66 of the air conditioning system 110 can be simultaneous, where the refrigerant 62 can flow through each evaporator 64, 66 simultaneously to cool various zones 50 of the air conditioning system 110 in the same or different levels of temperature or humidity. Suction valve 60 can also be configured as sequential so that only one evaporator 64, 66, or a predetermined subset of evaporators is provided with refrigerant 62 at any time. The operation of this system, the set points and parameters used and an algorithm that defines the operation of the system are shown in FIGURE 36. 36.

As illustrated in FIGURE 6, in various respects, a single-speed, single-suction compressor 170 can also be used to provide variant refrigerant flow rates 62 to the first and second evaporators 64, 66 within the air conditioning system 110 . In these aspects incorporating a single suction compressor 170, a solenoid valve 172, or a series of valves may be arranged between the system condenser 118 and various system expansion devices 120. As shown in FIGURE 6, the valve is typically a three-way valve, such as a flow divide valve 68, that regulates the flow of refrigerant from condenser 118 to two different expansion devices 120. In various respects, the valve may also be one of several fractionation devices including, but not limited to, a three-way solenoid valve, a stepper motor valve, or a multi-port fractionation valve. In this way, the valve can regulate the flow of the coolant in each of the devices

120 expansion and evaporators

64, respective of the system

110 air conditioning. Because the valve controls the flow of refrigerant fluid 62 to the various evaporators 64, 66 in the system, a single speed compressor can be used to provide varying degrees of refrigerant 62 in multiple evaporators 64, 66 serving multiple zones 50 within a structure 2 of unique construction. Additionally, the various aspects described above allow the use of smaller size compressors to provide proportionate amounts of refrigerant 62 in the various evaporators as necessary to accurately and efficiently operate the air conditioning system as described above.

The refrigerant fluid lines 124 supply the refrigerant through the vapor compression system and supply the refrigerant fluid passing through the compressor 116, the condenser 118, and the regulating device 120 to a plurality of evaporators 126, 127 ( show two, but more than two could conceivably be employed (and even greater efficiencies can be obtained) operating within an air passage 128 within the frame 2 of construction. The air passage may be an air duct, air vents from a room air conditioning system, or a portion of the ventilation machine compartment and heating air conditioning inside the building located within the building 2 . Typically, evaporators 126 and 127 are placed in proximity to or without a portion of the building heating ventilation and air conditioning machine compartment. Significantly, in various respects, the air conditioning system 110 is typically free of any check valves disposed in the suction lines 74 between the two evaporators 64, 66. 66. Air passage 128 typically has an air circulation fan 130 associated therewith to distribute air through building structure 2 or in a portion of building structure where air conditioning system 110 treats a single room or an area smaller than a total interior volume of a building structure. The air circulation fan supplies the air through the evaporators 126, 127 where the air is cooled by two different evaporator temperatures and the cooled air 132 is distributed to the volume of the indoor air to be cooled within the building structure . Air is returned to the evaporator as shown by reference number 134. Typically, a building structure may have an outside air inlet / path allowing outside air to enter, typically passively entering, the building structure from outside the building structure directly into air passage 128 or in the air of the building structure where the outside air is then circulated inside the building structure.

As illustrated in FIGURE 7, various aspects of the air conditioning system 110 may utilize a single outdoor air unit 180 and indoor air conditioners 182, each of which serves a different area 50 within the construction structure 2. Each of these conditioners 182 may have an independent ductwork system 190, supply vents 192, and return air vents 194. This decreases the total ductwork 190 required in home construction and increases efficiently due to less cooling lost in the environment surrounding ductwork 190. Cold air is supplied more rapidly in zones 50 within structure 2 served by the interior conditioner 182. Within each of these indoor conditioners 182 an evaporator 64, 66 may be provided which generally provides a single air temperature across zone 50 or particular space. In still several other aspects, two or more evaporators may be arranged within an indoor conditioner 182 to provide cooling in the outside air 34 entrained in the conditioner 182, as discussed above. In various other respects, multiple evaporators can be used to provide cooling to individual sub-zones within each zone 50 that is served by air conditioner 182. In this way, multiple evaporators can be arranged within certain branches of ductwork 190 within an air conditioner. 182 to provide various levels of cooling within each subzone. They can also be arranged within the air conditioner 182 for individual evaporators to provide significantly improved humidity control as well as temperature control for the air supplied to the zone or the sub-zone served by the air conditioner 182. In previous aspects, two outdoor units were required to serve each individual air conditioner (Figure 9) or a single outdoor unit that served a single air conditioner that requires an extensive duct network through the entire structure (Figure 8). The various aspects described herein allow users to save resources by utilizing a single outdoor unit that typically employs a condenser that provides a cooling capacity that efficiently and effectively serves multiple air conditioners.

Figure 3 shows a system similar to Figure 2; however, the evaporator 126, which is the high temperature evaporator as discussed further herein, conditions the air from the outside and allows large amounts of external (cool) air to enter the building structure in this way improving the air quality within the building structure such as a home. As discussed in the environmental protection agency's publication The Inside Story:

A Guide to

Indoor Air

Quality, the outside air enters and leaves a house by:

infiltration, natural ventilation, and mechanical ventilation. Infiltration describes outside air flows into the home through seam openings and cracks in walls, floors, and ceilings, and around windows and doors. Air moves through natural ventilation through open windows and doors. Infiltration and natural ventilation are mainly caused by air temperature difference between interiors and exteriors and by wind. There are a number of mechanical ventilation devices to allow more outside air inside such as outside ventilation fans that intermittently remove air from a single room such as bathrooms and kitchens, and air handling systems that use fans and ducts to continuously remove the indoor air and distribute filtered and conditioned outdoor air to strategic points throughout the house. The rate at which the outside air replaces the inside air is the rate of air exchange. When there is a small infiltration, natural ventilation or mechanical ventilation, the air exchange rate is low and the indoor pollutant levels can increase. The present description significantly increases the rate of air exchange with the system of Figure 3 is used allowing direct entry of outside air into the air conditioning system. Typically, the intake is fluidly coupled to, more particularly proximal to, a suction side of an air movement device such as a fan. For example, as shown in Figure 3, the intake is fluidly coupled and close to the air circulation fan 130, which it extracts.

<td>The</td><td>system</td><td colspan="4">air conditioning allows</td><td>the</td><td>pre</td>

<td>treatment</td><td>from air</td><td>Exterior</td><td>by</td><td>the</td><td>evaporator</td><td> 126</td><td>of</td>

<td>temperature</td><td>high. The</td><td>evaporator</td><td> 126</td><td>of</td><td>temperature</td><td>high</td><td>I know</td>

<td colspan="2">places typically</td><td colspan="2">right inside</td><td>of</td><td colspan="2">the structure</td><td>of</td>

construction next to one or more vents 138, which can be opened or closed automatically or manually. Instead of ventilation, shutters or other air closing mechanisms can be used instead of or in addition to ventilation. In this way, the air conditioning system regulates and controls the volume of outside air, fresh to the system and therefore to the interior of the construction structure. Adding more fresh, outside air from outside the building structure helps improve indoor air quality. The system is typically designed to strike a balance between the amount of fresh air and the energy efficiency. Due to the increased energy efficiency of the present disclosure, for the same amount of energy, the system can introduce fresh air from outside the building structure and therefore improve indoor air quality. Alternatively, energy efficiency can be further increased with less fresh, outside air supplied to the system.

In the context of the present disclosure, a control unit 140 may be in signal communication with each of the components of the air conditioning systems of the present disclosure to dynamically adjust various elements of the system, including the cooling capacity of the compressor , to maximize energy efficiency. Control unit 140 may optionally receive signals or other input from a user input such as the desired temperature for a given interior volume of building structure or, for example, temperature sensors within a building structure or input from the compressor with respect to the cooling capacity supplied by the compressor. Control unit 140 which may be a computer or processor system such as a microprocessor, for example, is typically configured to dynamically adjust the functions of compressors of various types (double suction double discharge double suction, and double discharge) of the present description, including, in the case of Figures 230

3, the functionality of the double suction compressor switching mechanism, based on one or more or all of these inputs to create the system as efficiently as possible. Control unit 40 can also control one or more fans 138 between an open and closed position and any position between them and can also regulate the total cooling capacity that is supplied by the compressor when the compressor is a variable capacity compressor such such as a linear compressor or a flexible oil-free orientation linear compressor. However, the most commonly used application is an reciprocating compressor or a scroll compressor, which can be of single or variable capacity. It is also possible to further improve system efficiency by appropriately regulating and varying fans and / or compressor cooling capacity modulation through, for example, compressor speed or stroke length in the case of a linear compressor.

The present disclosure includes the use of multiple (dual) evaporator systems that employ a switching mechanism for the return of the refrigerant to the compressor, where the air conditioning system 10 is free of any suction line check valves. The switching mechanism allows the system to match the total thermal loads with the cooling capacities provided by the compressor. Generally speaking, the system gains efficiency by employing the switching mechanism, allowing switching from suction port to fast, approximately typically on the order of a fraction of a second. The switching mechanism can be switched at an accelerated rate typically around 30 seconds or less or exactly 30 seconds less, more typically around 0.5 seconds or less or exactly 0.5 seconds or less, and more typically around 10 milliseconds or less or exactly 10 milliseconds or less (or any time interval of around 30 seconds or less). As a result, the system quickly switches between a cooling mode of the low temperature evaporator 127 and a cooling mode of the high temperature evaporator 126. Compressor 112 can be a variable capacity compressor, such as a linear compressor, in particular an oil-free linear compressor, which is a flexible orientation compressor (i.e., it operates in any orientation not only in a standard right position, but also a vertical position and an inverted position, for example). The compressor is typically a double suction compressor (see Figure 11) or a single suction compressor (see Figures 12-13) with an external switching mechanism. When the compressor is a single-suction compressor (Figure 12-13), it typically provides non-simultaneous double suction from the refrigerant fluid lines 144 from the high-temperature treatment evaporator and the low-temperature treatment evaporator.

As shown in FIGURES 2-3, one aspect of the present description uses a sequential dual evaporator cooling system such as air conditioning system 110. The dual evaporator cooling system shown in Figure 2 employs a low temperature evaporator 127 and a high temperature evaporator 126, each fed by coolant fluid lines 124 coupled to two separate expansion devices 120. Due to the differences in evaporation pressure that cools the air at different operating temperatures, the evaporators do not continuously feed the refrigerant flow to the suction lines simultaneously and thus activate as cooling at different levels is needed. and to regulate the humidity of the air. In this sense, a main advantage of the double (or multiple) evaporator system is that the high temperature evaporator works at a higher temperature than the low temperature evaporator, therefore increasing the total coefficient of performance (See Figure 10a for a double discharge / double discharge compressor and figure 10b for double discharge compressor).

In several respects, the difference in evaporation pressure in evaporators 64, 66 is mainly influenced by the expansion / restriction provided by the expansion devices 20, and is secondarily influenced by the temperature of the zones 50 that is served by the evaporators 64, 66 respectively. In this way, where there is a large temperature difference between the temperature of zone 50 and the temperature of the respective evaporator 64, 66, the evaporator 64, 66 automatically transfers large amounts of cooling into the space being served thus causing a high evaporation pressure in the refrigerant lines. This results in the respective evaporator circuit 64, 66 having a greater capacity to provide cooling to the zone 50 having a high temperature. As the temperature of zone 50 becomes closer to the temperature of evaporator 64, 66 fewer amounts of cooling are released by evaporator 64, 66, therefore the evaporation pressure will decrease. In this way, the evaporation pressure served to the evaporator 64, 66 can be determined by the current conditions present within the zones 50 served by the evaporator 64, 66. This control mechanism serves to substantially optimize the efficiency of compressor 116 so that air conditioning system 110 tends to maximize the cooling capacity provided by compressor 116 to optimize the amount of cooling provided to zones 50 having the highest loads. large (i.e. highest temperatures). In various other respects, the operating pressure and temperature of the evaporator 64, 66 can be controlled by a combination of the room / evaporator temperature difference and the resistance of the expansion / restriction device as controlled by the placement of the fractionation valve that regulates the supplied flow of refrigerants 62 through the various evaporator circuits 64, 66.

Because the high temperature evaporator refrigerant circuit operates at a much higher temperature than the low temperature evaporator refrigerant circuit operates, the thermodynamic efficiency of the cooling system is improved. For example, assuming the evaporation temperature is 7.2 ° C and the condensing temperature is 54.4 ° C and the isentropic efficiency (including motor efficiency) is 0.6, the COP of the cooling system can be estimated at 2.69. In a double suction compressor system assuming that the refrigerant circuits are at 50% and 50% in terms of heat transfer area and assuming that the first circuit operates at an evaporation temperature of 17 ° C, the first COP circuit is 3.66. The total COP of the system that employs a double suction system can be (0.5 * 3.66) + (2.69 * 0.5) = 3.175. These amounts to about an 18% improvement in the system COP compared to the conventional single suction compression system. The analysis assumes that the condensation temperature is the same for both circuits.

In fact, the condensation temperature will be higher for the double suction compression system so that the actual COP will be less than 18%, but a significant COP is achieved using such double suction systems. The total coefficient of performance is a weighted average of the coefficient of performance of the high temperature evaporator contained in the circuit and the low temperature as follows:

COP_Totai = = X * COPhte + (1-X) * COP_LTE

X is the radius of the high temperature evaporator cooling rate at the total cooling rate that the system provides.

As discussed above, the first evaporator can treat the initial air within the air passage directly in line with the second evaporator (Figure 2), or it can be positioned to pre-cool and dehumidify the air received from outside the structure. construction (Figure 3). The low temperature evaporator 127, operating at a low pressure (colder temperature), can be used to extract more moisture from the air and thus regulate the humidity in an interior volume of the building structure. Similarly, if the high temperature evaporator is used more to cool the indoor air of the building structure, the humidity level may be higher. There may be less latent cooling and thus less moisture is removed from the air.

While the use of two evaporators is the typical configuration of this aspect of the present description, the configuration could conceivably use three, four, or more evaporators placed in various inlets or outdoor locations within the air passages. As long as the low temperature evaporator circuit is at a lower temperature than the high temperature evaporator circuit and the average temperature of the two evaporators is hotter than the average temperatures of the air passing through the single evaporator, we obtain efficiencies.

One aspect of the present disclosure includes increasing the efficiency of the air conditioning system by rapidly switching between the low temperature evaporator mode of operation and a high temperature evaporator mode of operation. Where TI is the opening time of the high pressure suction port; T2 is the opening time of the low pressure suction port; T_on is the time compressor; and T_off is the compressor out of time, by varying TI, T2, T_on and T_off, it is possible to more efficiently meet the total thermal load requirement of the interior volume of the construction structure that is cooled with the cooling capacity (fixed or variable) provided by the compressor to thereby increase the total coefficient of refrigerant performance of the air conditioning system. It is also possible to further improve system efficiency by also regulating and appropriately varying fans and / or compressor cooling capacity modulation through, for example, the

<td>speed of</td><td>compressor or stroke length in the case of</td>

<td>a compressor</td><td>linear.</td>

<td>In</td><td>various aspects, the fast switching of the</td>

flow division valve 68 (shown in FIGURE 34) to supply refrigerant 62 from a single fluid line to the first and second evaporator circuits can create a sequential system such that an evaporator circuit is provided with a predetermined flow of

<td>refrigerant</td><td>62 followed by a predetermined flow of</td>

<td>refrigerant</td><td>62 to a second evaporator circuit 66.</td>

After the completion of a cooling and / or dehumidifying cycle, the flow divide valve 68 changes position to provide one flow of refrigerant 62 to another

<td>circuit of</td><td>evaporator for the duration of this period</td>

<td>particular</td><td>cooling and / or dehumidification.</td>

Alternatively, the system rapidly switches flow divide valve 68 between positions to provide refrigerant 62 so that first evaporator circuit 64 and second evaporator 66 can create a simultaneous air conditioning system. Where the flow division valve 68 is quickly switched, the flow division valve 68 can provide a quasi-continuous flow of refrigerant 62 to each of the first and second evaporator sections 64, 66, thereby creating a system conditioning unit simultaneously supplying refrigerant 62 to multiple evaporators 64, 66. In various other aspects, a simultaneous flow of refrigerant 62 to the various evaporators 64, 66 of the air conditioning system can be provided by one or more valves that can be placed in an open or semi-open position with respect to more than one evaporator at the same time. such that a proportional or continuous flow of refrigerant 62 is provided to more than one evaporator 64, 66 simultaneously.

Compressor 116 may be a reciprocating or rotary compressor, a variable capacity compressor, including but not limited to a linear compressor or a multiple intake compressor system (see Figures 11-13). When a standard rotary reciprocating compressor with a single suction port is used, the system further includes a switching mechanism 150 containing the compressor system (see Figure 1213). As shown in Figure 11, a double suction compressor 116 in accordance with one aspect of the present disclosure may utilize a valve system 142 built into the compressor containing two refrigerant fluid inlet streams 144, one from the evaporator low temperature and one from the high temperature evaporator. When using a linear compressor, which can be an oil-free linear compressor, the linear compressor has a variable capacity modulation, which is typically greater than a typical 3 to 1 modulation capacity with a variable capacity reciprocating compressor. The lower end of modulation is limited by the lubrication and modulation scheme.

Figures 12-13 generally show a mechanism

150 switch according to the present description. The

Figure 11, as discussed above, shows a system

142 valve used in double suction port compression system. Figures 12-13 show a switching mechanism 150 that can be positioned externally or within a single suction port system that allows two or more fluid intake ducts 144 to be fed into a single suction port. A compressor piston 146 is used in each dual refrigerant fluid intake system shown in

Figures 11-13. In the case of Figure 11, the coolant fluid is received in the piston chamber 148 from the low temperature evaporator and high temperature evaporator fluid lines when the piston 146 is inlet from the piston chamber are opened, or, when the solenoid switch 154 is activated, only the refrigerant fluid from the back evaporator fluid line, the low temperature valves 152 is attracted, the piston chamber intake valve 152 associated with the intake from the high temperature evaporator fluid line is not activated but is held in a closed position. When the piston stroke is

<td>active</td><td>toward</td><td>the</td><td>valves</td><td>of</td><td colspan="2">the camera</td><td>piston,</td><td>the</td><td colspan="2">valve</td>

<td>156 of</td><td>departure</td><td>of</td><td>the camera</td><td>of</td><td>piston</td><td>I know</td><td>open at</td><td colspan="2">Pressure</td><td>of</td>

<td>fluid</td><td>for</td><td colspan="2">allow to</td><td>the</td><td>fluid</td><td>of</td><td colspan="2">refrigerant</td><td>pass</td><td>to the</td>

capacitor 118.

Alternatively, depending on which circuit will open frequently, when the high temperature evaporator circuit is opened less frequently as will typically be the case in the system of Figure 3, valve 152 in the high temperature evaporator circuit may biased, typically spring loaded, to a normally closed position and the solenoid may bias the valve to the open position when system cooling is requested again. In this way even more energy is saved. Additionally, the solenoid valve could be a latch type that requires only one pulse (typically on the order of 100-1500 milliseconds) of power to activate.

An alternative aspect is shown in Figures 1213, showing a single piston chamber inlet valve 152, which is fed from a switching mechanism 150. The switching system 150 as shown by lines 158 and 160, representing the compressor housing, can be found within the compressor housing when the housing is in a position 158 relative to the switching mechanism 150 and outside the housing when the housing is in a position 160 relative to the switching mechanism 150. The position of the housing (represented by reference numbers 158 and 160) in Figures 12-13 is intended merely to show that the switching mechanism 150 may be outside the housing or within the housing of the single suction compressor. The switching mechanism 150 may employ a magnetically activated solenoid system where the obstruction 162 is activated between a first position (shown in Figure 12) that allows the coolant to flow from the evaporator (high pressure / temperature) and a second position (not shown) where obstruction 162 is placed to block fluid paths from the high pressure / temperature evaporator and allow refrigerant to flow from the (pressure) evaporator low temperature). The alternative aspect shown in Figure 13 shows two solenoid valves 164 that can be controlled by control unit 140 to be in an open or closed position. The alternate refrigerant from the solenoid valves 164 flows to the compressor between the refrigerant from the first fluid line and the second fluid line. Solenoid valves typically only open once. In the Figures 11-13 aspects of compressor systems, the pressure of the refrigerant fluid leaving the compressor for the condenser is significantly higher than the pressure than the refrigerant received from the high temperature evaporator or temperature evaporator low, but the pressure of the refrigerant received from the high temperature evaporator fluid line is greater than the refrigerant received from the low temperature evaporator fluid line. This, as discussed above, allows for greater efficiencies of the total refrigerant system. In several respects, a. stepper motor in place of a solenoid valve to provide multiple paths of the refrigerant 62 to the various evaporators 64, 66 of the air conditioning system 110. The stepper motor used in the various aspects can be configured to selectively provide a flow of refrigerant 62 to multiple individual evaporators 64, 66, sub-combinations of multiple evaporators, or to all evaporators in the air conditioning system. The stepper motors in various aspects are similar to those made by Saginomiya, Inc. of Tokyo, Japan.

As shown in FIGURES 15-16, even more efficiencies can be achieved in air conditioning systems by using a multiple / dual discharge compressor that is a single suction (see Figure 15) or multiple (double) compressor. Dual-discharge compressors, dual-charge refrigerant fluid lines typically independently feed devices

120 ', 120 thermal expansion separated after passing through the condenser 118. The refrigerant flows from the first condenser circuit 166 to it via a restrictive expansion device 120' and from the second thermal evaporator circuit 168 minus the condenser to evaporator 127 by a more restrictive thermal expansion device 120 than thermal expansion device 120. The double discharge compressor 117, 119 is quickly switched between the two discharge ports. The switching frequency and duration of operation of each port can be controlled by control unit 140 to match the heat load requirement of each capacitor circuit. Since the first circuit operates at a low condensing temperature the thermodynamic efficiency of the cooling system is improved as shown in Figure 10b.

Similar systems such as those used in conjunction with the compressor side suction can also be used in conjunction with the discharge side of the compressor. The compressor may be a double suction double discharge compressor Figure 14a). As shown in Figure 14a, the compressor can include two inlets 144 and two outlet valves 156. Alternatively, as shown in Figure 14b, a switching mechanism can be used on the discharge side of the compressor and placed inside or outside the compressor housing.

The switching mechanism can use a magnetically activated choke or, more typically one or more solenoid valves 164 to regulate the outgoing flow of the refrigerant fluid to the compressor coils.

As shown in Figure 16, the system using a double discharge compressor can be combined with the use of a double suction aspect on the compressor to provide dynamic adjustability to make the system as efficient as possible when take advantage of the concepts of double suction efficiency discussed above and the concepts of double discharge and fast switching also discussed above. Conceivably, the compressor can have multiple suction ports and multiple discharge ports. More than two of each could be used to create even more humidity adjustment efficiency and flexibility as discussed herein.

Dual discharge systems can use condenser coils in stages to provide heating to an appliance.

For example, condensers can be thermally associated with a water heater or a drying chamber.

Figures 17a, 17b, 18a, 18b show two aspects showing a thermally disarticulated evaporator system with low temperature and high temperature evaporators working together to regulate the latent and considerable heating but when there is a thermal breakdown (Figures 17a, 17b) or physical separation (Figures 18a, 18b) between low temperature evaporator 127 and high temperature evaporator 126.

Figures 17a and 17b show a disjointed evaporator system 200 employing low temperature evaporator 127 and high temperature evaporator 126 in a manner in which common fins 202 share. Common fins have at least typically one or more pluralities of thermal rupture portions 204 at a distance from the evaporator tubes to lengthen and interrupt the conductive hot flow path. The low temperature evaporator 127 and the high temperature evaporator 126 have a plurality of conduit loops and are parallel to each other. The evaporator coils generally define a first temperature zone and the evaporator system and a second temperature zone of the evaporator system. The zones are generally separated by thermal breakout portions 204 which are generally positioned below the center of the evaporator system between the coil section of the low temperature evaporator and the coil section of the high temperature evaporator of the evaporator system, which by they are generally half of the total evaporator system.

Figures 18a, and 18b show an alternate disjointed evaporator system that aligns and positions fins 302 and fins 304 relative to one another so that the gap of the fins that engage with the high temperature evaporator 126 are separated to facilitate spilling condensate out of fins for optimal heat transfer. The separate fins (less than 22 fins per inch, more commonly about 14 to about 18 fins per inch) are typically designed to feed the air flow in the space between the fins 304 that are operably connected to the temperature evaporator Low, which predominantly regulates sensible cooling, but also performs some dehumidification. This construction helps facilitate condensate spillage and latent heat transfer and full heat transfer. The downstream fins 304 have larger fins per inch of evaporator coil than the upstream fins to facilitate heat transfer with air flow through the fins, for example, the fins may come in a larger number of 22 fins per inch., 25 fins per inch, or more. Low temperature evaporator 127 and fins 304 may be primarily responsible for primarily considerable cooling and some latent cooling in the system. The high temperature evaporate 126 and fins 302 may be primarily responsible for most latent heat cooling and some considerable cooling. Both evaporators will regulate latent and considerable heat to some degree. These evaporator systems can be more typically employed when the low temperature and high temperature evaporators are separated from each other such as in the aspect of the present description schematically described in Figure 2. Such configurations with largely separated fins could be used in other aspects with evaporators that are not close to each other. For example, in the context of Figure 3, the evaporator system could be used and the evaporators cannot be arranged relative to each other and the air flow path so that the air flow over the fins 302 is fed between the fins 304 , but the more compact natural state of fins 304 improves considerable heat energy transfer, and more spaced fins 302 can facilitate initial latent heat energy transfer and subsequent condensate drainage.

As illustrated in FIGURES 19-21, various aspects of the air conditioning system 10 may include a two-stage cooling system to provide an efficient and rapid decay cooling stage in a given area 50. The decreased cooling stage is initiated when the ambient temperature greatly exceeds the preselected set point of the air conditioning system 10 for that particular zone 50. This typically occurs when the temperature outside the building structure 2 is relatively high and the air conditioning system 10 has been off for a period of time so that the interior temperature is also significantly raised. The decreased cooling stage can also be initiated by a drastic increase in temperature resulting from doors and windows being left open or by the significantly higher internal heat load. In these and other high heat situations, the decreased cooling stage provides a supplemental flow of refrigerant 62 into at least one of the evaporator circuits 12 6 to increase the evaporation temperature so that higher cooling levels are provided in zone 50 to decrease the temperature in the space subsequently faster than a typical single stage cooling system that is capable of doing so.

To achieve a two-stage cooling system, a two-stage regulator is provided by adding a second parallel capillary tube 320 and a two-way solenoid valve 322 in particular evaporator circuit 126 (Figure 19). After the initial start, the system runs less restricted through parallel capillary tubes 120, 320 and thus at higher evaporator temperatures. This increases the cooling capacity (see Figures 20-21).

Since the temperature of zone 50 moves closer to the

<td>load of</td><td colspan="2">temperatures</td><td>of the</td><td colspan="2">set point, the system</td><td>I know</td>

<td>decreases</td><td>and</td><td>eg ecuta</td><td>in</td><td>the</td><td colspan="2">low evaporator temperature</td>

<td>(capacity</td><td>plus</td><td>low)</td><td>than</td><td>I know</td><td>comes closer with the load</td><td>of</td>

<td colspan="2">maintenance of</td><td colspan="2">temperature</td><td>in</td><td>stable state.</td><td></td>

When the temperature in zone 50 reaches a predetermined value, the air conditioning system 10 is turned on, the temperature and humidity sensors communicate with the two-way valve 322 to initiate the decreased cooling stage. To increase the flow of refrigerant 62, the two-way valve 322 opens the passage to the second parallel capillary tube 320 to increase the flow of refrigerant 62 to the evaporator circuit 126. The additional refrigerant flow keeps the evaporator coil flooded with coolant 62 thereby making the rate of cooling faster than if the evaporator coil were to obtain small amounts of refrigerant 62. Once the temperature of zone 50 served by evaporator 126 reaches a predetermined maintenance level, which is a temperature substantially close to the predetermined set point for that particular zone, two-way solenoid valve 322 closes the passage to the second parallel capillary tube 32o to decrease the amount of refrigerant 62 provided in the evaporator 126. As a result, the evaporation temperature decreases so that less cooling is provided in zone 50. In this way, the decreased cooling stage ends and starts a maintenance stage whereby smaller gradual changes in temperature and humidity can be made to keeping the temperature and relative humidity of the space at approximately a predetermined set point for that particular zone 50.

In various aspects of the decreased cooling stage, the higher air flow rates can be used to provide additional displacement of air flow through zone 50, so that the additional amounts of cooling provided during the decreased cooling stage they can spread across more than zone 50 to lower the space temperature in a faster and more efficient manner. In this decreased cooling stage, the high capacity of the evaporator fan is typically required as the fan needs to be large enough to transfer the extra cooling to zone 50 from the flow of high capacity refrigerant supplied during the decreased cooling stage . Additionally, due to the addition of the second parallel capillary tube 320 and the two-way solenoid valve 322 in the air conditioning system to provide the decreased cooling stage, A smaller, less powerful compressor can be used to provide additional cooling bursts through the second parallel capillary tube 320 which may ordinarily require a larger compressor to provide the high levels of cooling necessary to rapidly decrease the temperature of zone 50.

As illustrated in the enthalpy / pressure graph in Figure 21, the air conditioning system, during a decreased cooling stage, can be run at a high evaporator temperature to provide additional cooling capacity to decrease the temperature in zone 50 at a faster and more efficient rate. The evaporator temperature during normal or maintenance mode is lower. However, during maintenance mode, significantly smaller temperature and humidity modifications are required to maintain the comfort level of zone 50 within predetermined parameters. Consequently, a lower evaporator temperature is more efficient during maintenance mode.

Figures 22-23 show an updated air conditioning system thermal storage system 400. The upgraded thermal storage system can be used with the air conditioning systems of the present description or traditional air conditioning systems. Figures 22-23 show the updated thermal storage system 400 installed together with a traditional air conditioning system as shown in Figure 1.

The upgraded thermal storage system 400 is installed to store thermal cooling capacity in an air conditioning system for use during peak usage times when the main cooling system of the construction structure is offline or in use is reduced or otherwise decreased. A pump 402, which may be placed before or after the thermal energy storage fluid tank 404 along the refrigerant loop 416. Although it is schematically shown how the refrigerant fluid is pumped in a counterclockwise direction, the directional flow from the pump 402 could be in either direction as long as the refrigerant is in thermal communication / contact with the energy storage fluid tank 404 thermal and in the path of air flow to be cooled by heat exchanger 406. In the aspect of the description shown in Figure 22, a heat exchanger 402 is placed in the heat energy storage fluid tank 404 and is operably connected to the coolant fluid lines of the coolant loop 416. Thermal energy storage fluid tank 404 is cooled, typically during off-peak times, by a refrigeration system employing a traditional compressor, a thermal expansion device 20, a fan 22, and an evaporator 26. The evaporator 26 system

400 Up-to-date thermal storage is separated within or is otherwise in thermal communication with the material

414 Thermal energy storage (fluids) within the thermal energy thermal storage fluid tangue 404. In the aspect shown in Figure 23, the heat exchanger 412 is omitted and the heat energy storage fluid within the heat energy heat storage fluid tank 404 operates by itself in the heat exchanger / coolant fluid. The refrigerant fluid in this case is the thermal energy storage fluid and is received in the tank through outlet 408 and returns to the refrigerant loop 416 through inlet 410.

As shown in Figure 24, in another aspect of the present disclosure, a split air conditioning system 500 can be used to drive a plurality of indoor air units 502. (Figure 24 shows two indoor air units but multiple indoor air units can be used and one or more air units can be placed in multiple rooms within a building structure.) Each individual indoor air unit 502 can be turned on or off in a given space. The split air conditioning system 500, as shown in Figure 24, uses the double suction (multi-suction) compressor concepts described herein to provide great benefits. Switching of the suction valves to power the evaporators of the various air conditioning units inside the home equally or to provide hotter or colder evaporator temperatures for the respective rooms is possible using this system. The hotter evaporator can cool the air less but still provide a level of dehumidification. The cooler evaporator could be used to cool the air more but also to dry the air more. The cooling capacity and thus the temperature of an evaporator in which it operates is based on the expansion device but also on the flow rate of the refrigerant and the suction pressure that the evaporator considers from the compressor. If the indoor units are identical with the identical expansion device resistance, then the multi-suction valve systems of the present description can drive the evaporator to a lower or higher pressure relative to the other evaporators. Certain ways to complete this include: managing the opening and closing of the compressor suction valves or adjusting the valve opening timer and compression piston or vane stroke position to achieve the level margin of desired pressure. In the example shown in Figure 24, the top section can be a living room that is kept cool and dry and that is powered by a low temperature evaporator (10 ° C (50 ° F)). Consequently, this will provide more cooling capacity (low vapor pressure refrigerant flow) by polarizing the service cycle of the suction port. The cycle on / off switch for use of a variable capacity compressor and fan can be used to reduce the cooling rate and achieve a slight rise in temperature (12.7 ° C (55 ° F)).

As illustrated in FIGURES 26-32, the split air conditioning system 500 may also include a heating element 540 to provide hot air in a particular area 54, 56 served by the split air conditioning system 500. Thus, additional heating accessories such as a central oven, a radiant heating system, or other separate heating is unnecessary to heat a particular area served by the split air conditioning system 500. In several alternative aspects, heating can be provided to zone 54, 56 served by split air conditioning system 500 by reversing the flow of refrigerant 62 through the system so that refrigerant 62 travels from compressor 116 to evaporator 64 , 66, then to condenser 520 and returns to compressor 116. In this way, evaporator 64, 66 draws cooling from the ambient air around evaporator 64, 66 therefore emits heat, as opposed to cooling, in the space served by split air conditioning system 500.

As illustrated in FIGS. 28-31, the heating provided by the separate split air conditioning system 500 may be provided by a heating element 540 arranged within each of the split air conditioning units 502. Each of the split air conditioning units 502 can move air within the space through the use of a rotating displacement fan 550 to draw air through a portion of the air conditioning unit 502 through the air coils. evaporator to cool the air or a heating element 540 to heat the air, and forces the air to withdraw into the respective zone 54, 56 to be conditioned by the air conditioning system 500. Other types of fans can also be used to move air through the split air conditioning units.

As illustrated in FIGURES 26-27, a single room or other continuous space may be served by multiple individual split system units 502 to provide heating or cooling in multiple zones 54, 56 contained in a single space. Those individual split system units 502 may be arranged as floor units, wall units, or arranged close to the ceiling of the space. These individual split system units 502 can provide cooling and heating so that an additional air handling or temperature control system is not required to serve in the respective zone 54, 56 provided by the split air conditioning system 500. Floor units are most typically used because they are at the occupant's level (typically around 1.82 meters (six feet) or less) and cannot intermingle with the hot air typically located in the upper part of the room. Divided indoor units that employ at least one evaporator and one fan are also typically capable of creating and configuring to create differently sized zones (see Figures 27A-C) around each unit depending primarily on the relative fan speed of each unit interior split air conditioner. Additionally, the cooling capacity of the evaporators of each split air conditioning unit can be independently adjusted in accordance with one aspect of the present disclosure. As such, the cooling capacity can be decreased and a high fan speed relative to another split air conditioning unit can be maintained to maintain a relatively large air handling zone, but with less cooling. The cooling capacity can be increased (or kept the same and the fan speed can be decreased) and the air surrounding the unit can be cooled to a greater extent (lower temperature).

The lower section of Figure 24 can be a bedroom that is kept cooler and wetter for optimal comfort (a high temperature evaporator of around 15.5C (60 ° F), for example). Consequently, that system can provide high suction pressure and less cooling capacity by polarizing the service cycle of the suction port.

The system shown in Figure 25 shows a single outdoor unit that drives a single (possibly multiple) indoor unit in a split air conditioning system with double (multiple) suction and a two-section coil evaporator where the suction lines they are free of check valves between the evaporators. Switching the suction valve in this regard provides more or less chilled air temperatures and more or less humidity in a given conditioned living room. The hotter evaporator can cool the air less but still provide a level of dehumidification. A cooler evaporator can cooler the air but drier the air. In combination, the air can be cooled and dehumidified to the desired level in an increased effective COP. The cooling capacity and temperature at which an evaporator operates is a function of the restriction of the expansion device, but also the flow rate of the refrigerant and the suction pressure of the evaporator as discussed above. This is dynamic in the multi-suction systems of the present description which allows., The functionality described in the above.

As illustrated in Figures 33-35, a dual zone indoor air treatment unit 502 can be configured to serve two or more zones 54, 56 within a single room. In this regard, a single outdoor compressor / condenser unit drives two evaporators 540 configured in a parallel arrangement 560. The flow of the refrigerant 62 for each of the parallel evaporators 560 is independently controlled by a proportional flow division valve 68 that provides a quasi-continuous flow of refrigerant 62 from the expansion device 522 and simultaneously through the first and second circuits. 64, 66 evaporator and 560 parallel evaporators. In this regard, the valve is disposed within the indoor unit and proportionally regulates the flow of the fluid refrigerant 62 between the parallel evaporators 560. The valve may be a solenoid valve arranged in the liquid refrigerant portion of the system that is configured to quickly switch between various dedicated parts to provide liquid refrigerant flow to the multiple evaporator circuits. Alternatively, the valve may be a stepper motor driven needle that proportionally exposes the various distribution outlet ports on the respective evaporators. The stepper motor can expose, cover or partially cover the various distribution outlet ports through the use of plungers or cam placement.

As discussed above, the quick-change valve 68 or the stepper motor valve allows the use of a single suction compressor 170, where refrigerant 62 is proportionally supplied to the various evaporator circuits based on the necessary cooling load between the various evaporator circuits. This configuration allows the use of a smaller compressor that may typically be required to serve multiple evaporator circuits simultaneously. In this regard, a single fan controls the release of air flow from parallel evaporators 560 in zones 54, 56 of room 52 to provide the appropriate amount of cooling to regulate temperature and relative humidity within multiple zones 54, 56 contained in a single room 52. In this way, the flow of refrigerant 62 in the parallel evaporators 560 controls the level of heating, since the air flow through each of the parallel evaporators 560 can be the same. In alternative aspects, the parallel evaporators 560 may be arranged within separate split system units 502 so that separate fans can be used to regulate the air flow volumes as well as the flow of the refrigerant 62 in each of the 502 units. divided system.

FIG. 24 shows the compressor, which is typically a multi-suction compressor 516, a fan 518, a condenser 520, expansion devices 522, evaporators 524, and cross flow fans 526 fluidly connected by the fluid flow lines 528. refrigerant. The evaporators 524 are individually separated into the cooling zones or rooms, 530 and 532 of the building structure separately in Figure 24. Figure 25 shows a similar system, but the two evaporators, as discussed above, are located in the same unit and are used to condition the space within a single area or room of a 534 structure.

The aspects described herein are configured to provide cost savings and energy savings over conventional air conditioning systems.

Those skilled in the art will recognize, or be able to verify using no more than routine experimentation, many equivalents of the specific aspects of the disclosure described herein. Such 5 equivalents are intended to be encompassed by the following claims.