阅读说明：本技术 用于液体干燥剂空调系统的储罐系统 (Storage tank system for liquid desiccant air conditioning system ) 是由 彼得·F·范德莫伊伦 埃里克·科祖布阿尔 马克·A·艾伦 斯科特·N·罗韦 于 2018-11-01 设计创作，主要内容包括：一种液体干燥剂空调系统,包括一个或多个液体干燥剂储罐。(A liquid desiccant air conditioning system includes one or more liquid desiccant storage tanks.)

1. A liquid desiccant air conditioning system, comprising:

(a) a first liquid desiccant unit;

(b) a second liquid desiccant unit for a second liquid desiccant unit,

wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator;

(c) a layered liquid desiccant storage tank; and

(d) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, and the liquid desiccant reservoir, the transfer system comprising:

a first conduit coupled to the liquid desiccant reservoir and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the liquid desiccant reservoir to the first liquid desiccant unit;

a second conduit coupled to the first liquid desiccant unit and the second liquid desiccant unit for transferring liquid desiccant from the first liquid desiccant unit to the second liquid desiccant unit;

a third conduit coupled to the second liquid desiccant unit and the liquid desiccant reservoir for transferring liquid desiccant from the second liquid desiccant unit to the liquid desiccant reservoir;

a bypass valve in the second conduit;

a fourth conduit coupling the bypass valve and the liquid desiccant reservoir for transferring liquid desiccant between the second conduit and the liquid desiccant reservoir; and

one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit; and

(e) a heat exchanger coupled to two of the conduits for exchanging heat between the liquid desiccant flowing in one conduit and the liquid desiccant flowing in the other conduit.

2. The system of claim 1, wherein the first liquid desiccant unit is the conditioner and the stratified liquid desiccant storage tank is located in a conditioned space.

3. The system of claim 2, wherein the stratified liquid desiccant storage tank is located in a wet chamber comprising a water supply for adding water to the liquid desiccant.

4. The system of claim 1, wherein the first liquid desiccant unit is the regenerator and the stratified liquid desiccant storage tank is located outside of the conditioned space.

5. The system of claim 1, wherein the first liquid desiccant unit is the conditioner that cools and dehumidifies an air stream provided to a building space when the air conditioning unit is operating in a cooling and dehumidification mode, and wherein the second liquid desiccant unit includes the regenerator that humidifies and heats outside air, return air from the building space, or a combination thereof.

6. The system of claim 1, wherein the first liquid desiccant unit is the conditioner that heats and humidifies an air stream provided to a building space when the air conditioning unit is operating in a heating and humidifying mode, and wherein the second liquid desiccant unit includes the regenerator that dehumidifies and cools outside air, return air from the building space, or a combination thereof.

7. The system of claim 1, wherein the bypass valve is configurable to divert all liquid desiccant flowing in the second conduit to the liquid desiccant reservoir instead of the second liquid desiccant unit when the second liquid desiccant unit is deactivated.

8. The system of claim 1, wherein the bypass valve is disposable to block liquid desiccant from the first liquid desiccant unit and enable liquid desiccant to be drawn from the liquid desiccant storage tank into the second conduit for transfer to the second liquid desiccant unit when the first liquid desiccant unit is deactivated.

9. The system of claim 1, wherein the heat exchanger is coupled to the first conduit and the second conduit to exchange heat between the liquid desiccant flowing into the first liquid desiccant unit and the liquid desiccant flowing out of the first liquid desiccant unit.

10. The system of claim 1, wherein the heat exchanger is coupled to the second conduit and the third conduit to exchange heat between the liquid desiccant flowing into the second liquid desiccant unit and the liquid desiccant flowing out of the second liquid desiccant unit.

11. The system of claim 1, wherein the liquid desiccant reservoir comprises at least one sidewall angled or otherwise configured such that an upper end of the reservoir is wider than a lower end of the reservoir to provide a more linear relationship between liquid desiccant concentration and liquid level in the reservoir.

12. A liquid desiccant air conditioning system, comprising:

(a) a first liquid desiccant unit;

(b) a second liquid desiccant unit for a second liquid desiccant unit,

wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator;

(c) a first layered liquid desiccant reservoir;

(d) a second layered liquid desiccant storage tank;

(e) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, the first liquid desiccant tank, and the second liquid desiccant tank, the transfer system comprising:

a first conduit coupled to the first liquid desiccant tank and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the first liquid desiccant tank to the first liquid desiccant unit;

a second conduit coupled to the first liquid desiccant unit and the first liquid desiccant reservoir for transferring liquid desiccant from the first liquid desiccant unit to the first liquid desiccant reservoir;

a third conduit coupled to the first and second liquid desiccant reservoirs for transferring liquid desiccant from an upper portion of the first liquid desiccant reservoir to an upper portion of the second liquid desiccant reservoir;

a fourth conduit coupled to the first and second liquid desiccant reservoirs for transferring liquid desiccant from a lower portion of the second liquid desiccant reservoir to a lower portion of the first liquid desiccant reservoir;

a fifth conduit coupled to the second liquid desiccant tank and the second liquid desiccant unit for transferring liquid desiccant from an upper portion of the second liquid desiccant tank to the second liquid desiccant unit;

a sixth conduit coupled to the second liquid desiccant unit and the second liquid desiccant tank for transferring liquid desiccant from the second liquid desiccant unit to a lower portion of the second liquid desiccant tank;

one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit; and

(f) a heat exchanger coupled to the third conduit and the fourth conduit for exchanging heat between the liquid desiccant in the third conduit and the liquid desiccant in the fourth conduit.

13. The system of claim 12, wherein the first liquid desiccant unit comprises the conditioner and the second liquid desiccant unit comprises the regenerator.

14. The system of claim 13, wherein the transfer system is configured to selectively vary a ratio of (i) an amount of liquid desiccant flowing from the first liquid desiccant unit to the first liquid desiccant reservoir to (ii) an amount of liquid desiccant flowing from the first liquid desiccant reservoir to the second liquid desiccant reservoir in order to maintain a given concentration range of the liquid desiccant, the given concentration range corresponding to air conditioning to be provided by the first liquid desiccant unit.

15. The liquid desiccant air-conditioner of claim 12, further comprising:

a first layered sub-reservoir positioned within the first liquid desiccant reservoir, the first layered sub-reservoir connected to the second conduit for receiving liquid desiccant from the first liquid desiccant unit, the first layered sub-reservoir also connected to the third conduit for transferring liquid desiccant to the second liquid desiccant reservoir, wherein the first layered sub-reservoir is configured to overflow into the first liquid desiccant reservoir; and

a second split sub-tank positioned within the second liquid desiccant tank, the second split sub-tank connected to the sixth conduit for receiving liquid desiccant from the second liquid desiccant unit, a lower portion of the second split sub-tank connected to the fourth conduit for transferring liquid desiccant to the first liquid desiccant tank, wherein the second split sub-tank is configured to overflow into the second liquid desiccant tank.

16. A liquid desiccant air conditioning system, comprising:

(a) a first liquid desiccant unit;

(b) a second liquid desiccant unit for a second liquid desiccant unit,

wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator;

(c) a liquid desiccant storage tank;

(d) a liquid desiccant heat exchanger in the liquid desiccant reservoir; and

(e) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, and the liquid desiccant reservoir, the transfer system comprising:

a first conduit coupled to the liquid desiccant reservoir and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the liquid desiccant reservoir to the first liquid desiccant unit;

a second conduit coupled to the first liquid desiccant unit and the liquid desiccant heat exchanger for conveying liquid desiccant from the first liquid desiccant unit to a first inlet in the liquid desiccant heat exchanger;

a third conduit coupled to the second liquid desiccant unit and the liquid desiccant heat exchanger in the liquid desiccant reservoir for transferring liquid desiccant from the liquid desiccant heat exchanger to the second liquid desiccant unit;

a fourth conduit coupled to the second liquid desiccant unit and the liquid desiccant heat exchanger for conveying liquid desiccant from the second liquid desiccant unit to a second inlet in the liquid desiccant heat exchanger; and

one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit; and is

Wherein the liquid desiccant heat exchanger exchanges heat between the liquid desiccant received from the second liquid desiccant unit and the liquid desiccant received from the first liquid desiccant unit.

17. The system of claim 16, further comprising a tiered sub-reservoir positioned within the liquid desiccant reservoir, the tiered sub-reservoir configured to overflow into the liquid desiccant reservoir, and wherein the liquid desiccant heat exchanger is located in the tiered sub-reservoir.

18. The system of claim 17, further comprising a low level valve in the liquid desiccant reservoir for detecting a low level of liquid desiccant in the layered sub-reservoir and, in response to such detection, causing liquid desiccant to flow from a space in the liquid desiccant reservoir outside the layered sub-reservoir to the layered sub-reservoir.

19. The system of claim 17, further comprising a layered sub-reservoir positioned within the liquid desiccant reservoir, the layered sub-reservoir configured to overflow into the liquid desiccant reservoir, and wherein the liquid desiccant heat exchanger is located in a space in the liquid desiccant reservoir external to the layered sub-reservoir.

20. The system of claim 17, further comprising a low level valve in the liquid desiccant reservoir for detecting a low level of liquid desiccant in the layered sub-reservoir and, in response to such detection, causing liquid desiccant to flow from a space in the liquid desiccant reservoir outside the layered sub-reservoir to the layered sub-reservoir.

21. A liquid desiccant air conditioning system, comprising:

(a) a first liquid desiccant unit;

(b) a second liquid desiccant unit for a second liquid desiccant unit,

wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator;

(c) a liquid desiccant storage tank;

(d) a high-concentration stratified liquid desiccant sub-tank in the liquid desiccant tank, the high-concentration stratified liquid desiccant sub-tank configured to overflow into the liquid desiccant tank;

(e) a low-concentration tiered liquid desiccant sub-reservoir in the liquid desiccant reservoir configured to overflow into the liquid desiccant reservoir; and

(e) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, the liquid desiccant tank, the high-strength sub-tank, and the low-strength sub-tank, the transfer system comprising:

a first conduit coupled to the liquid desiccant reservoir and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the liquid desiccant reservoir to the first liquid desiccant unit;

a second conduit coupled to the first liquid desiccant unit and the low-concentration liquid desiccant sub-tank for transferring liquid desiccant from the first liquid desiccant unit to the low-concentration liquid desiccant sub-tank;

a third conduit coupled to the second liquid desiccant unit and the low-strength liquid desiccant sub-tank for transferring liquid desiccant from the low-strength liquid desiccant sub-tank to the second liquid desiccant unit;

a fourth conduit coupled to the second liquid desiccant unit and the high-strength liquid desiccant sub-tank for transferring liquid desiccant from the second liquid desiccant unit to the high-strength liquid desiccant sub-tank; and

one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit.

22. The system of claim 21, further comprising a heat exchanger coupled to the first conduit and the second conduit for exchanging heat between the liquid desiccant in the first conduit and the liquid desiccant in the second conduit.

23. The system of claim 22, wherein the heat exchanger is in the low-strength liquid desiccant sub-tank.

24. The system of claim 21, further comprising a low level valve in the liquid desiccant reservoir for detecting a low level of liquid desiccant in the low-concentration tiered sub-reservoir and, in response to such detection, causing liquid desiccant to flow from a space in the liquid desiccant reservoir outside the low-concentration tiered sub-reservoir to the low-concentration tiered sub-reservoir.

25. The system of claim 21, further comprising a low level valve in the liquid desiccant reservoir for detecting a low level of liquid desiccant in the high-concentration layered sub-reservoir and, in response to such detection, flowing liquid desiccant from a space in the liquid desiccant reservoir outside the high-concentration layered sub-reservoir to the high-concentration layered sub-reservoir.

26. The system of claim 21, further comprising:

a bypass valve in the third conduit; and

a fifth conduit coupling the bypass valve and the sub-tank for selectively transferring liquid desiccant from the sub-tank to the second liquid desiccant unit.

27. A method of operating a liquid desiccant air-conditioning system including a conditioner, a regenerator, at least one tiered liquid desiccant storage tank, and a transfer system for controllably transferring liquid desiccant between the conditioner, the regenerator, and the at least one liquid desiccant storage tank, the method comprising the steps of:

(a) when the outside air is warm and has a low relative humidity:

(i) dehumidifying, by the conditioner, an air stream to be provided to a building space using a concentrated liquid desiccant;

(ii) providing the diluted liquid desiccant used in the conditioner to the regenerator;

(iii) (iii) concentrating, by the regenerator, the liquid desiccant received in (ii);

(iv) (iv) returning a portion of the liquid desiccant concentrated in (iii) to the conditioner and storing another portion in the at least one stratified liquid desiccant storage tank;

(b) when the outside air is cool and has a high relative humidity:

(i) providing liquid desiccant concentrated by the regenerator during (a) from the at least one stratified liquid desiccant storage tank to the conditioner; and

(ii) (ii) dehumidifying with the conditioner the air stream to be provided to the space using the concentrated liquid desiccant received in (i); and

(c) repeating steps (a) and (b) periodically.

28. The method of claim 27, wherein (a) occurs during the day and (b) occurs during the night.

29. The method of claim 27, wherein the at least one tiered liquid desiccant storage tank comprises a first tiered liquid desiccant storage tank coupled to the conditioner, and further comprising a second tiered liquid desiccant storage tank coupled to the regenerator and the first tiered liquid desiccant storage tank, wherein the method comprises: controllably transferring liquid desiccant between the first and second tiered liquid desiccant reservoirs to maintain a desired liquid desiccant concentration in each reservoir.

30. The method of claim 27, wherein the at least one tiered liquid desiccant storage tank comprises a first tiered liquid desiccant storage tank and a second tiered liquid desiccant storage tank each coupled to the conditioner, and further comprising a third tiered liquid desiccant storage tank coupled to the regenerator and the first and second tiered liquid desiccant storage tanks, wherein the method comprises: controllably transferring liquid desiccant between the first, second, and third hierarchical liquid desiccant reservoirs to maintain a desired liquid desiccant concentration in each reservoir.

31. The method of claim 27, wherein the regenerator receives an air stream comprising varying amounts of outside air and return air to vary a concentration of liquid desiccant regenerated in the regenerator.

32. The method of claim 27, wherein (iii) concentrating, by the regenerator, the liquid desiccant received in (ii) comprises: the liquid desiccant is concentrated in a series of regenerator units.

Background

The present application relates generally to the use of liquid desiccants in combination with heat pumps, compressors, and coolers to dehumidify and cool, or heat and humidify, an air stream entering a space. One or more embodiments of the present application relate to replacing a conventional air conditioning unit with a (membrane-based) liquid desiccant air conditioning system to achieve substantially the same heating and cooling capabilities while providing additional functionality. Additional functions may include, for example, the ability of the system to heat and simultaneously humidify a space, the ability of the system to heat and simultaneously dehumidify or cool and humidify a space, thereby providing more comfortable and healthier indoor air conditions than would be provided by conventional systems.

Desiccant dehumidification systems-both liquid desiccants and solid desiccants-have been used in parallel with conventional vapor compression HVAC equipment to help reduce humidity in spaces, particularly in spaces requiring large amounts of outdoor air or having large humidity loads inside the building space itself (ASHRAE 2012 manual of HVAC systems and equipment, chapter 24, page 24.10.) humid climates (e.g., Miami, F L) require a lot of energy to properly treat (dehumidify and cool) the spaceDesiccant dehumidification systems-both solid and liquid-have been in use for many years and are generally quite effective in removing moisture from air streams₂And an ionic solution of water. Such brines are strongly corrosive to metals, even in small quantities, and many attempts have been made over the years to prevent desiccant residues in the air stream to be treated. In recent years, efforts have been made to eliminate the risk of desiccant residue by employing microporous membranes to contain the desiccant solution. These membrane-based liquid desiccant systems have been primarily applied to uniform roof units for commercial buildings. However, in addition to roof units, commercial buildings also use air handlers located inside the technical spaces in the building to cool and heat both outside air and recirculated air. There is also a large market for chillers that provide cold water to coils inside buildings and use evaporative cooling to achieve efficient condensers. Residential and small commercial buildings typically use split air conditioners, where the condenser (along with the compressor and control system) is located externally and one or more evaporator cooling coils are installed in the space to be cooled. Particularly in asia (often hot and humid), split-type air conditioning systems are the preferred method of cooling (and sometimes heating) the space. Disclosed herein is a solution well suited for such a split approach using a liquid desiccant heat exchanger.

Liquid desiccant systems typically have two separate functions. The conditioning side of the system conditions the air to the desired conditions, which are typically set using a thermostat or humidifier. The regeneration side of the system provides the reconditioning function of the liquid desiccant so that it can be reused on the conditioning side. Liquid desiccant is typically pumped or moved between the two sides, and the control system helps ensure that: the liquid desiccant is properly balanced between the two sides as conditions require and excess heat and moisture are properly handled without causing over-or under-concentration of the desiccant.

During the cooling cycle, efficient dehumidification can be achieved at higher evaporator temperatures, while regeneration can completely remove condenser energy at lower temperatures, as compared to conventional air cooling systems. Thus, the compressor can move energy from the conditioned space at much lower temperature differentials than conventional systems. This increases the efficiency of the compressor in proportion to the decrease in the temperature difference. This improves the efficiency of the compressor-based cooling and heating in combination with the liquid desiccant heat exchanger.

The advantages of liquid desiccant systems such as those described in U.S. patent No. 9,243,810 and others have been clearly demonstrated for humid hot climates with large latent heat loads. As buildings get better insulated, these latent heat loads increase as a percentage of the total cooling load, making efficient dehumidification more important. As the internal sensible heat load is reduced in tighter, better insulated buildings, conditioning ventilation air has become an even more important part of the overall cooling and heating load.

Extreme design conditions (including very cold and wet, very hot and dry, and very cold and wet) require special cooling and heating solutions for which early liquid desiccant systems were not optimized.

For example, at very high temperatures (>100F) and very low humidity (< 20% RH), existing liquid desiccant systems do not operate efficiently and require special controls to avoid desiccant crystallization. Conventional evaporative cooling systems work well at low and moderate cooling requirements, but cannot handle the extreme hot or more humid conditions that tend to occur in most locations at least part of the time. These conditions require compressor-based solutions that are much less efficient and lose significant capacity at high temperatures and/or very high humidity. Therefore, they tend to treat a mixture of outside air and return air.

For ventilation air, 920 standard C and D conditions require air to be dehumidified and heated to 70F. Existing systems use reheat, hot gas bypass, solid desiccant or other options, which significantly increase system cost and complexity. As disclosed herein, the small coils in the liquid desiccant system can further increase the basic efficiency of the liquid desiccant system, especially for those conditions.

Conventional cooling systems use refrigerant coils that are air cooled and are best suited for explicit cooling. The condensate formed on the coil acts as insulation reducing its capacity. Therefore, multiple coils need to be used in series to adequately dehumidify and cool the air. Four and six rows of coils are not common. However, conventional systems typically cannot handle the full latent heat load without significantly overcooling the air and then reheating the air, or mixing a large volume of return air with a small volume of outside air to minimize the humidity level of the mixture. Particularly on days where only a small amount of explicit cooling is required, the building may reach unacceptable levels of humidity. On cold and humid days with relative humidity levels > 90% and low temperatures (such as in rainy seasons), it would be preferable to heat the air while also dehumidifying the air. Many split system provide heat by operating as a reversible heat pump system. These are often most useful in mild climates where cooling and heating loads are approximately balanced. Very cold climates (e.g., the midwest and northeast of the united states) still require additional heating, typically from natural gas or oil. In milder climates, the efficiency of the heat pump is limited by humidity, which results in frosting and a very inefficient use of the tank defrost cycle. As disclosed herein, defrosting can be avoided by using a liquid desiccant system.

Commercial ventilation standards (AHRI) have been upgraded and now require 20CFM per person instead of 5 CFM. With improved insulation and reduced infiltration, controlled outside air is also becoming more important for residential applications. Traditionally, outside air requirements are met by "infiltration" -open doors and windows and leaks. Early patents by 7AC technology corporation have shown how liquid desiccants can significantly improve the efficiency of such systems.

Thin coils used in many residential systems have difficulty meeting high humidity levels of the outside air. Condensate removal is a particular problem with split systems. Condensate management has a significant impact on installation and maintenance costs. If improperly maintained, the condensate line may be plugged, which can lead to moisture damage if not repaired in time. As disclosed herein, a liquid desiccant heat exchanger can address these issues.

Additional building humidity "guidelines" are being developed to encourage maximum, and sometimes even minimum, humidity levels, primarily due to health concerns, particularly the effects on respiratory illness and allergies.

In dry climates, water-cooled chillers and evaporative coolers use the evaporative energy of water to cool the space and/or increase compressor efficiency. They often use a large volume of drinking water. Managing the fouling effects and biological contamination of such water is a significant challenge. Evaporative coolers are less efficient where both wet and dry conditions occur. Under those conditions, standard liquid desiccant solutions do not operate well. As disclosed herein, the addition of water can be used to simplify liquid desiccant systems and make them competitive in both dry and wet conditions. Many buildings must handle a variety of conditions ranging from very hot dry to relatively cold wet. Buildings with high Dew Point (DP)/high Relative Humidity (RH) and high Dry Bulb (DB)/low DP design points require expensive conventional solutions including, for example, solid desiccant wheels, heat pipes and hot gas reheat technology. The liquid desiccant systems disclosed herein can effectively handle these conditions.

There remains a large and growing need to provide a retrofittable, cost-effective and efficient cooling system that can handle both high humidity loads with low sensible heat loads and high sensible heat loads with low humidity loads for both cooling and heating. For example, existing liquid desiccant systems manage sensible heat load by adding an explicit cooling coil or "heat sink" to the condenser. The range of conditions that each of these solutions can manage is limited. This forces suppliers to offer a wide range of solutions for buildings with different design conditions in terms of outside air conditions and heat/latent heat load. The inventors how the direct combination of the special dehumidification coils disclosed in published U.S. patent application publication No. 2016-. This includes the use of available exhaust air for energy recovery, which requires additional heat exchangers or solid desiccant wheels in conventional systems, while liquid desiccant systems can recover most of the available potential and development of exhaust air without additional components.

Especially the early work of the Oakridge national laboratory has demonstrated the efficiency of using liquid desiccants to store energy, especially dehumidification capability. Increasing the concentration of the liquid desiccant from 20% to 35-40% reduces the volume of the liquid desiccant. For each pound of liquid desiccant in the concentrated solution, 2-3 pounds of water may be removed from the air. Typically, dehumidification involves the removal of as much as 0.005 to 0.01 pounds of water per pound of air. The total weight of 1 pound of liquid desiccant in the liquid desiccant solution was 2.5 pounds at 40% concentration and 5 pounds at 20% concentration.

A 10 ton system producing 1500cfm requires about 25 liters of additional tank space and 10 liters of desiccant to be able to dehumidify 920A air to 55F DP per hour. Alternatively, the 100% liquid desiccant has a storage capacity of about 1 liter per ton per hour. 1 litre of liquid desiccant provides a cooling capacity equivalent to 15kWh or a compressor dehumidification capacity of 3-5 kWh. The cost of latent heat storage capacity per kWh, calculated as $10 per liter of liquid desiccant, is $2-3 for liquid desiccant and $3+ for the entire storage system.

In a thermally driven desiccant enabled evaporative cooling system, concentrated liquid desiccant is used to reach the desired DP from any point on the psychrometric chart. The liquid desiccant is cooled with an indirect evaporative cooler or cooling tower. The cooled liquid desiccant achieves the desired DP condition at higher RH levels and with lower concentrations of desiccant than an uncooled liquid desiccant

Such systems use heat for regeneration of the desiccant and water for cooling. Heat is not always available, for example solar energy is only available during the day. Cogeneration heat is only available when there is a demand for electricity. District heating may have heat available continuously; however, during peak power demand of a utility, it may be most critical to reject district heating.

Overconcentrating the liquid desiccant to 40-45% and using more liquid desiccant to increase storage capacity makes it possible to use additional heat to prepare the concentrated liquid desiccant and use the concentrated liquid desiccant when dehumidification capacity is required, with significant savings due to not having to generate heat during periods when explicit cooling is not required.

In a compressor-based liquid desiccant system, savings are made from a heat pump with a smaller lift, thus increasing its efficiency. The additional dehumidification capability does not immediately reduce the energy requirements by itself. Adiabatic dehumidification does not change the air enthalpy. This means that the amount of kWh required to reach the target temperature (e.g., 70/55Fdp) from the 80F Wet Bulb (WB) is the same at 20% RH as at 95% RH. Thus, the cooling load in compressor-based systems is not always reduced by storage. According to one or more embodiments, compressor usage during the day is optimized by using liquid desiccant storage, thereby increasing compressor efficiency.

Disclosure of Invention

A liquid desiccant air conditioning system according to one or more embodiments includes: (a) a first liquid desiccant unit; (b) a second liquid desiccant unit, wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator; (c) a layered liquid desiccant storage tank; and (d) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, and the liquid desiccant reservoir. The transfer system includes: a first conduit coupled to the liquid desiccant reservoir and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the liquid desiccant reservoir to the first liquid desiccant unit; a second conduit coupled to the first liquid desiccant unit and the second liquid desiccant unit for transferring liquid desiccant from the first liquid desiccant unit to the second liquid desiccant unit; a third conduit coupled to the second liquid desiccant unit and the liquid desiccant reservoir for transferring liquid desiccant from the second liquid desiccant unit to the liquid desiccant reservoir; a bypass valve in the second conduit; a fourth conduit coupling the bypass valve and the liquid desiccant reservoir for transferring liquid desiccant between the second conduit and the liquid desiccant reservoir; and one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit. The system also includes (e) a heat exchanger coupled to two of the conduits for exchanging heat between the liquid desiccant flowing in one conduit and the liquid desiccant flowing in the other conduit.

A liquid desiccant air conditioning system according to one or more further embodiments includes: (a) a first liquid desiccant unit; (b) a second liquid desiccant unit, wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator; (c) a first layered liquid desiccant reservoir; (d) a second layered liquid desiccant storage tank; and (e) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, the first liquid desiccant reservoir, and the second liquid desiccant reservoir. The transfer system includes: a first conduit coupled to the first liquid desiccant tank and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the first liquid desiccant tank to the first liquid desiccant unit; a second conduit coupled to the first liquid desiccant unit and the first liquid desiccant reservoir for transferring liquid desiccant from the first liquid desiccant unit to the first liquid desiccant reservoir; a third conduit coupled to the first and second liquid desiccant reservoirs for transferring liquid desiccant from an upper portion of the first liquid desiccant reservoir to an upper portion of the second liquid desiccant reservoir; a fourth conduit coupled to the first and second liquid desiccant reservoirs for transferring liquid desiccant from a lower portion of the second liquid desiccant reservoir to a lower portion of the first liquid desiccant reservoir; a fifth conduit coupled to the second liquid desiccant tank and the second liquid desiccant unit for transferring liquid desiccant from an upper portion of the second liquid desiccant tank to the second liquid desiccant unit; a sixth conduit coupled to the second liquid desiccant unit and the second liquid desiccant tank for transferring liquid desiccant from the second liquid desiccant unit to a lower portion of the second liquid desiccant tank; and one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit. The system also includes (f) a heat exchanger coupled to the third conduit and the fourth conduit for exchanging heat between the liquid desiccant in the third conduit and the liquid desiccant in the fourth conduit.

A liquid desiccant air conditioning system according to one or more embodiments includes: (a) a first liquid desiccant unit; (b) a second liquid desiccant unit, wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator; (c) a liquid desiccant storage tank; (d) a liquid desiccant heat exchanger in the liquid desiccant reservoir; and (e) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, and the liquid desiccant reservoir. The transfer system includes: a first conduit coupled to the liquid desiccant reservoir and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the liquid desiccant reservoir to the first liquid desiccant unit; a second conduit coupled to the first liquid desiccant unit and the liquid desiccant heat exchanger for conveying liquid desiccant from the first liquid desiccant unit to a first inlet in the liquid desiccant heat exchanger; a third conduit coupled to the second liquid desiccant unit and the liquid desiccant heat exchanger in the liquid desiccant reservoir for transferring liquid desiccant from the liquid desiccant heat exchanger to the second liquid desiccant unit; a fourth conduit coupled to the second liquid desiccant unit and the liquid desiccant heat exchanger for conveying liquid desiccant from the second liquid desiccant unit to a second inlet in the liquid desiccant heat exchanger; and one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit; and wherein the liquid desiccant heat exchanger exchanges heat between the liquid desiccant received from the second liquid desiccant unit and the liquid desiccant received from the first liquid desiccant unit.

A liquid desiccant air conditioning system according to one or more further embodiments includes: (a) a first liquid desiccant unit; (b) a second liquid desiccant unit, wherein one of the first and second liquid desiccant units is a conditioner and the other of the first and second liquid desiccant units is a regenerator; (c) a liquid desiccant storage tank; (d) a high-concentration stratified liquid desiccant sub-tank in the liquid desiccant tank, the high-concentration stratified liquid desiccant sub-tank configured to overflow into the liquid desiccant tank; (e) a low-concentration tiered liquid desiccant sub-reservoir in the liquid desiccant reservoir configured to overflow into the liquid desiccant reservoir; and (e) a transfer system for transferring liquid desiccant between the first liquid desiccant unit, the second liquid desiccant unit, the liquid desiccant reservoir, the high-strength sub-reservoir, and the low-strength sub-reservoir. The transfer system includes: a first conduit coupled to the liquid desiccant reservoir and the first liquid desiccant unit for transferring liquid desiccant from a lower portion of the liquid desiccant reservoir to the first liquid desiccant unit; a second conduit coupled to the first liquid desiccant unit and the low-concentration liquid desiccant sub-tank for transferring liquid desiccant from the first liquid desiccant unit to the low-concentration liquid desiccant sub-tank; a third conduit coupled to the second liquid desiccant unit and the low-strength liquid desiccant sub-tank for transferring liquid desiccant from the low-strength liquid desiccant sub-tank to the second liquid desiccant unit; a fourth conduit coupled to the second liquid desiccant unit and the high-strength liquid desiccant sub-tank for transferring liquid desiccant from the second liquid desiccant unit to the high-strength liquid desiccant sub-tank; and one or more pumps associated with at least one of the conduits for pumping liquid desiccant through the at least one conduit.

In accordance with one or more embodiments, a method of operating a liquid desiccant air conditioning system is also disclosed. The system includes a conditioner, a regenerator, at least one tiered liquid desiccant storage tank, and a transfer system for controllably transferring liquid desiccant between the conditioner, the regenerator, and the at least one liquid desiccant storage tank. The method comprises the following steps: (a) when the outside air is warm and has a low relative humidity: (i) dehumidifying, by the conditioner, an air stream to be provided to a building space using a concentrated liquid desiccant; (ii) providing the diluted liquid desiccant used in the conditioner to the regenerator; (iii) (iii) concentrating, by the regenerator, the liquid desiccant received in (ii); (iv) (iv) returning a portion of the liquid desiccant concentrated in (iii) to the conditioner and storing another portion in the at least one stratified liquid desiccant storage tank; (b) when the outside air is cool and has a high relative humidity: (i) providing liquid desiccant concentrated by the regenerator during (a) from the at least one stratified liquid desiccant storage tank to the conditioner; and (ii) dehumidifying an air stream to be provided to the space with the conditioner using the concentrated liquid desiccant received in (i); and (c) repeating steps (a) and (b) periodically.

Drawings

FIG. 1 illustrates an exemplary 3-way liquid desiccant air conditioning system using a chiller or an external heating or cooling source.

Fig. 2 illustrates an exemplary flexibly configurable membrane module including a 3-way liquid desiccant plate.

Fig. 3 illustrates an exemplary single membrane plate in the liquid desiccant membrane module of fig. 2.

FIG. 4 illustrates an exemplary liquid desiccant air conditioning system having a compressor and a heat exchanger configured to operate in a cooling mode.

FIG. 5 illustrates an exemplary liquid desiccant air conditioning system having a layered liquid desiccant storage tank.

FIG. 6 illustrates an exemplary liquid desiccant air conditioning system including a dual reservoir system with multiple pumps in accordance with one or more embodiments.

FIG. 7 illustrates an example liquid desiccant air conditioning system including features for managing liquid desiccant concentration in accordance with one or more embodiments.

Fig. 8A illustrates an exemplary liquid desiccant air conditioning system including a stratified storage tank with hot and concentrated desiccant, while diluted desiccant flows directly from a conditioner to a regenerator, according to one or more embodiments.

Fig. 8B illustrates an exemplary liquid desiccant air conditioning system including a stratified tank with cold and concentrated desiccant, with diluted desiccant flowing directly from the conditioner to the regenerator, according to one or more embodiments.

FIG. 9 illustrates an exemplary liquid desiccant air conditioning system including a tiered storage tank with cold desiccant according to one or more embodiments.

FIG. 10 illustrates an exemplary liquid desiccant air conditioning system including a dual reservoir system with stratification and low volume transfer between the conditioner reservoir and the regenerator reservoir, according to one or more embodiments.

FIG. 11 illustrates an example liquid desiccant air conditioning system including a tiered dual reservoir system with low volume transfer between a conditioner reservoir and a regenerator reservoir in accordance with one or more embodiments.

Fig. 12A and 12B illustrate an exemplary liquid desiccant air conditioning system including an integrated reservoir system with a direct flow option between a conditioner and a regenerator, with cold liquid desiccant in the reservoir and with an integrated heat exchanger, according to one or more embodiments.

Fig. 13A illustrates an example liquid desiccant air conditioning system including a multi-piece storage tank with an external heat exchanger according to one or more embodiments.

Fig. 13B illustrates an exemplary liquid desiccant air conditioning system including a multi-piece reservoir solution with multiple valves and an integrated heat exchanger according to one or more embodiments.

Fig. 13C illustrates an exemplary three-way tank with an integrated heat exchanger according to one or more embodiments.

FIG. 14 illustrates an exemplary tank having sloped sides to provide a more linear relationship between concentration and liquid level in accordance with one or more embodiments.

FIG. 15 illustrates an example water addition control system for a liquid desiccant air conditioning system according to one or more embodiments.

FIG. 16 illustrates an exemplary liquid desiccant air conditioning system including a water addition device in accordance with one or more embodiments.

FIG. 17 illustrates an exemplary split system liquid desiccant air-conditioning system including a plurality of storage tanks in a heating mode according to one or more embodiments.

Figure 18 shows a multi-zone building with multiple ceiling units, DOAS units, and individual regeneration.

FIG. 19 illustrates an exemplary liquid desiccant air conditioning system including a multi-tank solution in a multi-zone building with different requirements, according to one or more embodiments.

Fig. 20 illustrates an exemplary multi-reservoir system for optimizing liquid desiccant concentration according to one or more embodiments.

Fig. 21 shows a california duck-type plot of power production over the course of a day.

Fig. 22 shows the daily cycle of humidity and temperature.

Figures 23 and 24 show psychrometric charts.

Fig. 25 illustrates an exemplary liquid desiccant air conditioning system showing the activity of the conditioner/evaporator and regenerator/condenser coils during a daily cycle, according to one or more embodiments.

FIG. 26 illustrates an exemplary liquid desiccant air conditioning system including a multi-reservoir system having layered liquid desiccant reservoirs according to one or more embodiments.

Detailed Description

Fig. 1 depicts a novel liquid desiccant system as described in more detail in U.S. patent No. 9,243.810, which is incorporated herein by reference. The regulator 101 comprises a set of plate structures that are hollow inside. Cold heat transfer fluid is generated in cold source 107 and enters the plates. The liquid desiccant solution at 114 travels down the outer surface of each of the plates. The liquid desiccant travels behind a thin film located between the airflow and the plate surface. The outside air at 103 is blown through the set of conditioner plates, which in this example are wavy. The liquid desiccant on the plate surface attracts water vapor in the air stream, and the cooling water inside the plate helps to suppress the air temperature rise. The treated air at 104 is placed into the building space.

The liquid desiccant collects at the bottom of the corrugated conditioner plate at 111 and is transported through heat exchanger 113 to the top of regenerator 102 and to point 115 where the liquid desiccant is distributed across the corrugated plate of the regenerator. The return air or optionally outside air at 105 is blown through the regenerator plates and water vapor is transported from the liquid desiccant into the exiting air stream at 106. Optional heat source 108 provides the driving force for regeneration. Similar to the cold heat transfer fluid on the conditioner, the heat transfer fluid from the heat source at 110 may be placed inside the corrugated plates of the regenerator. Also, the liquid desiccant collects at the bottom of the corrugated plate 102 without the need for collection pans or troughs, so the regenerator airflow can be horizontal or vertical. An optional heat pump 116 may be used to provide cooling and heating of the liquid desiccant. It is also possible to connect a heat pump between the cold source 107 and the heat source 108, said heat pump pumping heat from the cooling fluid instead of the desiccant.

FIG. 2 is described, for example, in U.S. Pat. Nos. 9,308,490; 9,101,874, respectively; and 9,101,875, which are all incorporated herein by reference. The liquid desiccant enters the structure through the ports 204 and is directed behind a series of membranes, as depicted in fig. 1. The liquid desiccant is collected and removed through port 205. Cooling or heating fluid is provided through the ports 206 and travels inside the hollow plate structure opposite the air flow at 201, as also described in more detail in fig. 1 and 2. The cooling or heating fluid exits through port 207. The treated air at 202 is directed to a space in a building or exhausted (as the case may be). The figure shows a 3-way heat exchanger in which the air and heat transfer fluid are in a substantially vertical orientation. However, it is also possible to configure the heat exchanger such that the air and the heat transfer fluid flow in other directions (e.g., horizontal direction).

Fig. 3 depicts a 3-way heat exchanger as described in more detail in U.S. patent No. 9,631,848, which is incorporated herein by reference. The air flow at 351 flows counter to the cooling fluid flow at 354. Membrane 352 contains liquid desiccant at 353 that flows along wall 355 that contains a heat transfer fluid at 354. Water vapor at 356 entrained in the air stream can pass through the membrane 352 and be absorbed into the liquid desiccant at 353. The heat of condensation of water at 358 released during absorption is conducted through wall 355 into the heat transfer fluid at 354. Sensible heat at 357 from the air stream is also conducted through membrane 352, liquid desiccant at 353, and wall 355 into the heat transfer fluid at 354. This heats the liquid desiccant 358, which liquid desiccant 358 is then transferred to the heat transfer fluid 354. The heat transfer fluid also explicitly cools the air to the desired target conditions. The ratio of latent cooling to explicit cooling is determined by the concentration of the liquid desiccant 353. During dehumidification, the concentrated desiccant enters the panel where it is diluted. And the cold heat transfer fluid enters the panel where it is heated.

These figures show how panels are built into modules (fig. 3) with air 351 flowing horizontally or vertically through the modules. The desiccant enters at the top of the module and flows across the panel, exiting at the bottom. The heat transfer fluid 354 flows counter to the gas flow, entering through the bottom and exiting through the top.

Fig. 4 shows a liquid desiccant air conditioning system having a conditioner 403 and a regenerator 422 operating in a cooling mode. The diluted liquid desiccant 428 from the conditioner 403 is pumped through a heat exchanger 426 to the regenerator 422, which regenerator 422 includes a panel module similar to the conditioner 403. Heat transfer fluid 418 from regenerator 419 is heated by the condenser side of compressor system 411 by heat exchanger 415. Thus, air 421 entering regenerator 422 is heated and humidified and exits at 423.

The heat exchanger 426 heats the liquid desiccant 428 using heat from the concentrated desiccant 427 that has just been heated in the regenerator 422.

The heat transfer fluid may comprise water or water and glycol. The heat transfer fluid 406 leaving the conditioner 403 is cooled by a refrigerant-to-heat transfer fluid heat exchanger 407. The heat transfer fluid 418 from the regenerator 422 is heated in a refrigerant-to-water heat exchanger 415.

In case the panels comprise a refrigerant as heat transfer fluid, the heat exchangers 407 and 415 are not used, but the panels are cooled directly, for example as shown in fig. 1.

The regulator 403 regulates the mixture 401 of outside air and return air to supply air 404. The regenerator uses a mixture 421 of exhaust air and outside air to regenerate the liquid desiccant, thereby exhausting hot humid air 423. As shown in the prior art, the compressor system 411 with expansion valve 416 may have other components, including air-cooled coils and hoppers not shown.

Fig. 5 shows a liquid desiccant air conditioning system having a layered liquid desiccant storage tank 501 as described in more detail in U.S. patent No. 9,086,223, which is incorporated herein by reference. Concentrated liquid desiccants have a higher specific gravity than more dilute liquid desiccants. Thus, the liquid desiccant in the vertical reservoir will leave a thinner desiccant at the top of the reservoir. Such a reservoir may be used to treat the air 503 using a higher or lower concentration of liquid desiccant in the conditioner 510 depending on the humidity target of the supply air 504. This requires monitoring the concentration of the desiccant by the level of the reservoir 501, since more dilute liquid desiccant has a higher volume than concentrated liquid desiccant.

Giving time to settle will enable the system to draw concentrated desiccant 505 for the conditioner during cool down using, for example, device 502 at the bottom of the tank and dilute desiccant from the top of the tank. Although not shown in the figures, because of the time required for separation, it is advantageous to return the concentrated desiccant 508 from the regenerator 512 to the bottom of the tank and the more dilute desiccant from the conditioner to the top of the tank 507, or to take one of those streams and connect the conditioner and regenerator directly.

The tank 501 performs several functions in the system:

as the desiccant is diluted, the desiccant expands and the reservoir contains an additional volume

By selecting the point from which the liquid desiccant is extracted, the stratification allows for some difference in concentration

During maintenance, desiccant from the removed panel can flow back into the tank

When the conditioner and regenerator flows are not the same, the tank absorption difference

The tank can provide an air reference to the panel, thereby preventing over-pressurization of the panel

The desiccant may bubble the panel and the reservoir may degas the desiccant, which may be important for predictable and measurable flow.

The multiple pump system of fig. 6, disclosed in U.S. patent application No. 62/580,270, which is incorporated herein by reference, shows multiple reservoirs and pumps for managing desiccant in a liquid desiccant air conditioning system. The inventors will show how such a system can be optimized. The liquid desiccant 607 entering the conditioner 603 is pumped by a pump 609 from the reservoir 650 to the conditioner 603 and returns the liquid desiccant 608 to the reservoir 650. The regulator regulates the air 601 supplied by the fan 602 to the conditions required for supplying the air 606. Desiccant going to the regenerator 648 is pumped from the second storage tank 654 by the regenerator 653, the regenerator 648 regenerating liquid desiccant using air 641 supplied by a fan 642 and then returning the liquid desiccant as 652 to the storage tank 654. Additional pumps (e.g., 655) may be used to pump the desiccant from the reservoir 654 to 650, and vice versa. The heat exchanger 610 heats the cold desiccant 611 and cools the hot desiccant 612 to minimize heat loss between the conditioner and the regenerator. The volume of liquid desiccant can also be affected by direct addition of water 657 by means of module 658.

Fig. 6 further illustrates how compressor 615 can be used as a source of cold water 604 and hot water 640 through liquid-to-water heat exchangers 614 and 620, respectively, with switch 617 setting the system in cooling mode 618A. Additional coils 671 and 622 using air streams 672 and 646 are shown that are suitable for managing concentration by diverting a portion of the condenser duty from the regenerator to coil 671 to avoid over-concentrating the desiccant. Or when valve 618 is set for adiabatic or near adiabatic dehumidification during cold conditions, additional load is generated using expansion valve 624 using coil 622. The system shown in fig. 6 is a complex heat pump configuration with a plurality of check valves (e.g., 637 and 618) shown in a 'C' or closed position to activate the expansion valve 638. The accumulator 618 can be used to balance refrigerant charge during different settings of the heat pump. The air 601 is conditioned using a liquid desiccant in the conditioner 603, typically to reduce humidity during cooling of the humid air and increase humidity during heating of the air. Thus, when operating in the cooling mode, the regeneration tank 654 maintains a higher temperature while the cooling tank 650 maintains a lower temperature. This is the reverse in the heating mode.

The liquid desiccant system of fig. 6 is one possible configuration of a heat source and a cold source that can be used in a variety of operating modes. Generally, cooling and dehumidification, as well as heating and some degree of humidification, are part of the standard operating mode of a liquid desiccant heat pump system. In some applications, for example, with very humid but cool air (e.g., at 65F, 90% RH), heating of the air while dehumidifying is required. As the liquid desiccant concentration changes, and the efficiency of a full regeneration is affected by the compressor load and the outside air conditions.

The present disclosure will demonstrate how such conditions can be managed using storage tanks 650 and 654 without or with minimal use of air cooling coils 622 and 671, thereby simplifying control, reducing system cost and increasing system efficiency, particularly when additional loads generated by 622 can be avoided while adiabatically dehumidifying already cool but humid air 601.

Humidification during cooling may be beneficial during cooling of very dry air (e.g., desert air with DP below 40F and temperature above 35C). It not only improves comfort but also fundamentally changes the cooling load, since cooling can take place partly adiabatically. The water addition module 657 may play a key role in achieving this. It also affects the size and shape of the tank system. If the application requires a wide range of liquid desiccant concentrations, the reservoir size should accommodate the additional volume required to reduce the volume from the highest concentration to the lowest concentration. The reservoir level itself is a measure of the concentration of the liquid desiccant. In a standard tank, the relationship between concentration and tank level is not linear, requiring some adjustment of the control or settings to accommodate this.

The ability to control desiccant concentration by adding water via 657 reduces the concentration range that one or more reservoirs 650 and/or 654 must accommodate. Thus, a system with water addition requires a smaller storage tank than a system that manages drying conditions with air-cooled coils and varying concentration levels.

To achieve 40% to 60% supply RH with L iCl, a concentration of 20% to 35% is required, the concentration of X will give RH-supply 100% -2X + F1 (latent heat efficiency) at the conditioner, where X is the concentration expressed in%, and F is a function of the latent heat efficiency of the conditioner.

As the concentration of the liquid desiccant decreases, the total volume of the liquid desiccant increases. The volume of 20% liquid desiccant is 50% greater than the volume of 30% liquid desiccant. The increase in the actual volume of liquid desiccant in the reservoir is even greater because a significant portion of the desiccant resides in the panel and tubes in a fixed volume. For the baseline configuration of fig. 4, the RH of the regenerator input air is closely coupled to the RH of the regulator supply air. Wherein the RH of the regulator is lower than the RH of the regenerator supply air. However, regardless of the input conditions, the systems shown in fig. 6 and 7 may actively manage the concentration of the liquid desiccant.

Fig. 6 and 7 illustrate several ways in which the liquid desiccant concentration may be varied, including the direction and flow of refrigerant and heat transfer fluid through valves 617, 618, 619 of fig. 6 and valves 723, 729, 751, and 760 of fig. 7. Further, the flow rates of the desiccant and heat transfer fluid may be set by pumps 609, 655 and 653 in fig. 6 and 733, 735, 724 and 755 in fig. 7, wherein in the cooling mode more flow passes through the regenerator and less flow passes through the regulator, thereby increasing the concentration. The airflow rate is driven by the fans 602 and 642 of FIG. 6 and the dampers 660 and 725, 771 and 781 of FIG. 7.

The addition of water at 652 and 772 is the most direct way to reduce the liquid desiccant concentration. It also allows the concentration of the liquid desiccant to be maintained over a wide range of conditions. Since the size of the tank is driven by the ratio of the highest and lowest concentration used in the system, better control of the concentration reduces the required size of the tank. Resulting in a direct tradeoff between liquid desiccant storage and concentration management components in terms of size and weight.

The addition of water is the most direct control of the liquid desiccant concentration. The additional sensible coil that adds load to the evaporator and transfers load from the regenerator directly affects the energy available to concentrate the liquid desiccant. These coils can be managed by transferring heat transfer fluid or by changing the airflow through the coils. More air and cooler air increases the efficiency of the condenser coil, thereby reducing the concentration. In both cooling and heating modes, more and drier air increases the efficiency of the evaporator coil and thus increases the concentration. The gas flow through the regenerator determines whether the available energy is available to increase the concentration. The lower regenerator airflow enhances this capacity by heating the regenerator air, which allows the air to absorb more humidity.

Fig. 7 shows partitioned storage tank 732. During dehumidification, the liquid desiccant 751 is pumped 733 to the conditioner 703 where the liquid desiccant 751 dehumidifies air 724 driven by a fan 725 for supply to the space 790. The regulator 703 is cooled by heat transfer fluid 720 from the evaporator coil 706, which evaporator coil 706 is cooled by refrigerant passing through an expansion valve. Cold heat transfer fluid is pumped by pump 724 through regulator 703 to treat air 724 passing through fan 725 to supply space 790. The diluted desiccant 752 is then returned to the sub-tank 732B. A pump 735 takes liquid desiccant 734 from sub-tank 732B and pumps it through a heat exchanger 738, delivering warmer liquid desiccant 736 from the heat exchanger 738 to a regenerator 753 where the warmer liquid desiccant 736 is reconcentrated by air 770 from fan 771 while being heated by heat transfer fluid 750 from liquid-to-refrigerant condenser coil 740 of chiller 701. Hot desiccant 737 is used in heat exchanger 738 to heat desiccant 734 and is returned to main reservoir 732 as cooled and concentrated desiccant 739. Pump 733 removes concentrated desiccant from reservoir 732 and pumps it through regulator 723, after which it returns 752 to sub-reservoir 732B.

The amount of condenser heat available for regeneration may be affected by air cooling coils (e.g., 780) configured to use a combination of air from regenerator 753 or outside air 782 by adjusting damper 781 to add load to compressor 701 during wet cold conditions, where regenerator 753 requires more energy to fully regenerate the liquid desiccant to a high concentration. While a valve system (e.g., 706) may be used to reject some of the condenser's load from adding load.

Optimizing the performance of systems such as those shown in fig. 6 and 7 is largely driven by minimizing the heat loss that occurs as the desiccant moves from the regenerator to the conditioner and back. The heat exchangers 610 and 738 play a critical role, but so does any heat loss from the storage tanks 650 and 654. Maintaining the tank temperatures close to the ambient temperature of the space in which they are located helps to improve the overall performance of the system.

The concentration of the regenerated liquid desiccant 739 may be 1-2% higher than the concentration of the liquid desiccant 752 from the conditioner. Mixing these two streams increases the compressor's workload for a given target RH of the supply air 726

Fig. 8A and 8B illustrate how this can be managed with a single reservoir system, using natural layering of desiccants in the reservoir, with heavier desiccants having higher concentrations.

Fig. 8A shows how concentrated desiccant 812 from the bottom of the reservoir 801 is pumped 810 through a heat exchanger 840 to a conditioner 811. The diluted cooled desiccant pre-cools 812 in heat exchanger 840. Pump 841 pumps it through regenerator 814 as 815 back to storage tank 801. If the pump 810 is not used or is set to a lower volume than the pump 810, the valve system and overflow 831 returns the desiccant 819 to the reservoir. In such a configuration, the storage tank is maintained at a temperature near the regenerator temperature, which may be useful if the storage tank is exposed to outside air conditions. The flooding shown here does not allow the regenerator to operate without a regulator. This would require a separate supply from the top of the desiccant in 801 to 841. Or by using a dual tank system as shown in figure 7.

Fig. 8A shows the heat exchanger 840 on the side of the conditioner where the reservoir temperature will be near the regenerator temperature. Fig. 8B shows a liquid desiccant heat exchanger 840 on the side of the regenerator 814 that cools the liquid desiccant 815 and heats the liquid desiccant 813. The tank 801 still contains concentrated liquid desiccant, but is now at a lower temperature closer to the conditioned space temperature, which may be appropriate if the tank system is kept inside the building, close to the building conditions, and the regenerator is located outside or receives its air through a conduit.

Air is encapsulated in the desiccant flow in the membrane units 811 and 814, causing "bubbles" to appear in the desiccant flow. This reduces the efficiency of heat exchanger 840. The storage tank deaerates the desiccant. Having the liquid desiccant heat exchanger 840 between the flow from the reservoir to the conditioner and the return flow from the conditioner will be less affected by bubble formation than if the heat exchanger 840 were between the desiccant directly from the conditioner and the desiccant returning from the regenerator. In fig. 8A, the desiccant 812 has been degassed, while the stream 812B will have some encapsulated air. In fig. 8B, both flow 813 and flow 815 will have some enclosed air. Thus, a degassing device at or after the overflow 831 will improve performance. In fig. 7, the sub-tank 732B functions as a degassing device. One skilled in the art will appreciate that degassing may be accomplished in a variety of ways other than using a storage tank.

Fig. 9 shows a system with a single reservoir, where a pump 609 takes concentrated and cooled desiccant 607 from the bottom of the reservoir 901 and supplies it to the conditioner 603. The diluted desiccant 608 is returned to the top of the desiccant reservoir 901. The pump 653 removes the diluted liquid desiccant 913 from the top of the tank 901, for example, by using a floating suction system. Such floating connections may take various forms regardless of system performance. The concentrated desiccant is withdrawn from the regenerator 648 by a pump 844 and flows to the storage tank 901 through the heat exchanger 610 to 915. This system uses tank stratification to ensure that the regulators and regenerators are most efficient. As in fig. 8B, the tank 901 is maintained at a temperature close to the regulator temperature.

Typically, the flow rate of liquid desiccant required for effective dehumidification in the 3-way heat exchanger of the liquid desiccant systems of fig. 1-3 is 5 to 20 times less than the flow rate of the heat transfer fluid, as measured in pounds per minute. Depending on the conditions and efficiency goals required for the application, the maximum flow rates of heat transfer fluid and air are expressed in pounds per minute at 1:1 and 2: 1, in the above range. Generally, higher water flow rates improve system performance by reducing the required temperature offset between water and air and between refrigerant and water. Higher desiccant flow increases the efficiency of the liquid desiccant panel, but increases the size of the liquid desiccant heat exchanger and/or increases heat loss, thereby reducing system level performance. Reducing the desiccant flow rate still improves the overall performance of the system at the current desiccant flow rate of 2-10 mm/min.

For systems with higher desiccant flow, a dual reservoir system has significant benefits. A dual tank system is disclosed in U.S. patent No. 9243810, which is incorporated herein by reference. When higher flow rates are required for applications, such as applications using low concentration and high temperature desiccants, a dual reservoir system is appropriate. The dual reservoir also gives additional flexibility in managing desiccant concentration, as discussed below.

Fig. 10 illustrates such a dual reservoir system with separate pumps 1016 and 1041 to manage the liquid desiccant flow 1041 and 1042 between reservoirs 1001 and 1002 through heat exchanger 1040. This is particularly important where the flow through the regulator or regenerator or both is high. By transferring only 10-20% of the liquid desiccant from the hot reservoir 1002 to the cold reservoir 1001, the heat loss through the heat exchanger 1044 is reduced by 80-90%, to < 5% of the total work done.

The system in fig. 10 is based on the configuration disclosed in U.S. patent No. 9243810. This embodiment does not use the overflow reservoir 732B from fig. 7 to distinguish between treated desiccant and untreated desiccant. Stratification may be used, for example, by supplying diluted desiccant from the conditioner 603 to the top of the reservoir 1001 using a floating supply point similar to that shown in fig. 5, which is then used to flow the desiccant 1042 through a pump 1041 to a heat exchanger 1044 and to the top of the reservoir 1002. The same method with a float device can be used to send the diluted desiccant 1013 to the regenerator 648, from which regenerator 648 the diluted desiccant 1013 is returned 1015 to the bottom of the storage tank 1002. By reducing the flow through the heat exchanger 1040, the heat loss from the conditioner to the regenerator is reduced in proportion to the ratio of the total desiccant flow through the conditioner to the flow between the regenerator and the conditioner.

The dual reservoir system also allows a flow of desiccant 607 through the conditioner 603 and to the reservoir 1001. Given the higher viscosity in the conditioner, the desiccant flow rate can be lower without loss of coverage. If the heat source for regenerator 648 is a heat pump driven by the cooling load of 603, then using a dual reservoir system can further improve performance by: the heat available during hotter and drier outside air conditions is used to deeply dehumidify the liquid desiccant in 1002 up to 40% + while maintaining a steady concentration of desiccant 607 from reservoir 1001 at 20-22% or any other concentration required by the application and conditions.

By increasing the liquid desiccant flow rate 1013 through the regenerator 648, a high concentration of liquid desiccant is produced at 1002. This may be used at a later time (e.g., in the early morning, when the cooling load is low and the humidity of the outside air is high) to maintain the concentration of 1001 using pump 1016.

For a non-compressor based thermally driven liquid desiccant system, this approach allows the operator of the liquid desiccant system as shown in fig. 10 to shift the load from a time with higher availability or lower electricity prices for local solar/wind/cogeneration power to a time with higher electricity prices or lower availability for green power. As renewable energy transfers the timing of peak power from midday to evening, this becomes increasingly important to utilities, which may be reflected in system rebates or kW rates.

Other possible storage solutions are discussed below. Concentrated liquid desiccant is an efficient energy storage device and cools more than ice per pound. It is particularly useful in dehumidifying Direct Outside Air Systems (DOAS), where the key requirement is to maintain dew point/humidity conditions of fresh outside air while leaving management of sensible heat load to traditional systems or leaving only explicit solutions (e.g., chilled beams).

The stratification of the desiccant will ensure that a higher concentration of desiccant is available for conditioning in 603 and a lower concentration of desiccant is available for regeneration in 648. However, some mixing of the desiccants in reservoirs 1001 and 1002 will occur, thereby affecting the efficiency of regeneration and conditioning.

The system disclosed in fig. 11 further improves stratification by using a sub-tank 1102 in the regulator tank 1101. The sub-tank receives diluted desiccant 608 from the conditioner. A small volume of the diluted liquid desiccant is supplied to the regenerator low concentration desiccant storage tank 1103 by a heat exchanger 1044. The low concentration desiccant is processed by regenerator 648 and returned to stratified tank 1104. The most concentrated desiccant 1144 is transferred from the bottom of the tank through heat exchanger 1044 to the conditioning tank 1101 with cold, high concentration desiccant. This maximizes the efficiency of the regeneration process, but at a significant cost in terms of complexity. Whether this tradeoff is worth depends on the volume of desiccant used and the concentration change in each step.

The concentration difference between the conditioner and the regenerator can be further increased by using a float in the reservoir 1103 to supply the lightest and most dilute liquid desiccant from the top of the stratified reservoir 1103. The concentrated liquid desiccant from the regenerator is stratified in reservoir 1101, with the most concentrated liquid desiccant being withdrawn from the bottom of the overflow reservoir and sent to the conditioner

The sub-tanks 1102 and 1104 are designed to overflow. For example, if the pump 1140 is stopped, the sub-tank 1102 will overflow and mix with the desiccant in the main tank 1101. This will decrease the concentration of 1112 and thus increase the RH of the supplied air. Similarly, 1104 will overflow when the pump 1144 is stopped. When the desiccant is significantly diluted, the liquid level in the tanks 1101 and 1103 may rise sufficiently to rise above the maximum level of the tanks 1102 and 1104, which tanks 1102 and 1104 will then be filled.

The proposed multi-tank approach is particularly important for systems that use high liquid desiccant flow rates. In the system of fig. 6, for each pound/minute of air, 1/10 or less desiccant should be used to achieve optimum performance. The system is essential when the desiccant volume is +/-50% of the air volume per minute with the use of dual storage tanks.

To optimize performance, the lowest and hottest desiccant should be used in the regenerator, and the coldest and highest concentrations in the conditioner and the total volume of desiccant passing through the heat exchanger should be minimized. To maximize the difference in the concentrations supplied to the regulator and regenerator, it may be desirable to stratify and/or partition the storage tank.

Fig. 12A shows a divided system with low concentration in the sub tank 1202 and high concentration in the main tank 1201. The valve 1230 may be used to ensure that the sub-tank 1202 does not empty when the regulator is not operating. The liquid desiccant 1202 returning from the conditioner 1211 passes through a heat exchanger 1204, which heat exchanger 1204 may be located in the sub-reservoir 1202 or the main reservoir 1201 (FIG. 12B). Locating the storage tank 1204 inside the storage tank 1201 can simplify maintenance by reducing the complexity of evacuating the system for panel replacement. Furthermore, any small leak in 1204 will not affect system integrity or performance. Fig. 12B shows a heat exchanger 1204 on the regenerator side. This requires that the lines 1213 and 1215 be insulated or kept outside of the conditioned space to minimize heat loss.

U.S. patent No. 9243810 shows that heat exchanger 1204 can take many forms, including plate heat exchangers and insulated pipes for 1212/1209 and 1213/1215 as shown at 1204B in fig. 12A.

From there, the diluted desiccant 1213 is pumped 1241 to the regenerator 648. The regenerated concentrated desiccant 1215 is returned through the heat exchanger 1204 and from there through 1216 to the bottom of the reservoir 1201. Positioning the exchanger 1204 in the low concentration sub-tank 1202 ensures containment of the leak in the event of a 1204 leak. An insulated heat exchanger positioned above the desiccant in the tank has no thermodynamic effects, but has potential maintenance and reliability advantages.

When the regenerator is not in use, the overflow 1231 will return the desiccant 1219 from the heat exchanger 1204 to the dilute storage tank. When the conditioner is not in use, regeneration may continue by using the device 1231 or parallel valve to draw the desiccant 1219 from the reservoir instead of from 1204. Various solutions exist for combining a two-way valve with an overflow/flow restrictor.

The one-way valve 1230 is used when the fluid level in the sub-tank 1202 drops too low, such that desiccant from the main tank needs to be added. For example, during periods when no latent cooling is required, pump 1210 is turned off. Continued regeneration may continue to provide storage of a high concentration of liquid desiccant for later use. This is particularly important in the case of high sensible heat load and low latent heat load at midday, which may increase drastically at night (e.g. in coastal areas).

When the liquid level is too high, the sub-tank 1202 may overflow into the main tank 1201. This can be done by lowering the wall between the two, which is also useful in very low concentration and high volume liquid desiccants to take full advantage of the available reservoir volume to reach the lowest concentration possible.

Those skilled in the art will appreciate that various configurations are possible, including positioning the heat exchanger 1204 in the main reservoir to pre-cool the warm liquid desiccant that will be sent by the pump 609 to the conditioner 603.

The concentration of the liquid desiccant will vary with the supply and target conditions and settings in the system. The concentration can vary from 15% to over 40%. Therefore, the system needs to be able to store additional volumes of liquid desiccant. One or more storage tanks need to be able to manage most or all of the desiccant in the system according to start-up and maintenance protocols.

As shown in fig. 13A, to further minimize the volume of liquid desiccant used in the system, a portion of the high concentration desiccant may be separated in a small high concentration reservoir 1303, which small high concentration reservoir 1303 is connected to the main reservoir 1302 through a valve 1352/1353. Valve 1352 opens when the concentration in main tank 1302 falls below the level of the valve and closes when the level rises above it. 1353 ensure that the reservoir 1303 is filled with a high concentration of liquid desiccant. Various types of valves may be used, such as a valve activated by a float. The exact system is not critical to the critical effect of 1303, which is to allow 1301 to dilute the desiccant from a smaller volume, thus requiring less space. The main reservoir supplies a high concentration of desiccant 1310 to the conditioner and receives a high concentration of desiccant from the regenerator 1311. The sub-tank 1301 with a low concentration of desiccant provides a low concentration of desiccant to the regenerator 648 (in cooling mode) and receives a low concentration of desiccant from the conditioner 603. As indicated above, the heat exchanger 1304 may be located between the conditioner and the reservoir, with concentrated liquid desiccant 1307 from the reservoir 1301 being supplied to the conditioner 603 through the heat exchanger 1304. The diluted liquid desiccant 608 is first heated in 1304 before it is returned to the reservoir 1302. This maintains the tank at a temperature close to ambient or external conditions, i.e. when the tank is not in a conditioned space, which is most appropriate. The heat exchanger may again be integrated in the tank, or it may be separate.

The integrated three-tank solution minimizes the size of the main tank, allowing a wide range of concentrations, and thus a wide range of supply conditions. It also reduces the response time of the system because the total volume of liquid desiccant is further reduced.

A similar multi-compartment reservoir system may be used to store high concentrations of liquid desiccant. In fig. 13B, valves 1350 and 1351 may be actively controlled to adjust the concentration in 1301 to meet the specific requirements of relative humidity in the conditioned space. Valves 1351, 1352 and 1353 may be used to maintain equilibrium in the system or an overflow system may be used to achieve this. This may be useful in advanced solutions where the space occupancy and thus the latent heat load changes significantly over time. Lower concentration and more humid conditions may require less cooling during low occupancy. The use of 1354 as a source for the regenerator increases the concentration in 1303, allowing deeper dehumidification during higher space occupancy.

Fig. 13C is similar to fig. 13A, but now the liquid desiccant heat exchanger 1304 is integrated in the reservoir 1302. Valves 1350, 1351, 1352, and 1353 are used to regulate the liquid level in each of the tanks 1301, 1302, and 1303. These may be passive systems, such as float-based solutions; or an active valve system that is directly controlled by the cell control system for greater fine tuning of the system.

Fig. 14 shows a similar solution, but now the tank 1401 has a sloped bottom 1401 to maximize the height of the most concentrated desiccant in the small volume in the tank and to ensure a more linear relationship between tank level and concentration. Fig. 14 also shows a sub-reservoir 1402 for the overflow diluted liquid desiccant. Also, various modes are possible depending on cost and performance tradeoffs.

One skilled in the art will appreciate that other shapes, valve systems and compartments may be used to minimize size, maximize concentration control and minimize the cost of the valves and reservoir systems. More complex systems may also be used to store high concentrations of desiccant. As mentioned above, this is a form of energy storage.

Fig. 15 shows a simple mechanism for adding water using softened water 1501, the softened water 1501 being supplied through a solenoid valve 1502, the solenoid valve 1502 being driven by a float 1503 in a reservoir 1504. The reservoir level 1505 may be measured by a level sensor 1506, which level sensor 1506 may be used to control a solenoid valve, rather than through a control program that may then vary the desiccant concentration according to input conditions, supply conditions, and outside air.

Fig. 16 shows the direct supply of 1670 filtered water 1680 and softened water 1671 to the storage tank 1601. 1672 may then be used to dilute the liquid desiccant directly. The filtration may be a forward or reverse osmosis process or other process that produces mineral free water. Direct supply to the tank is a simple and easy to understand solution. However, avoiding fouling of liquid desiccant panels in the conditioner 1611 and regenerator 1614 requires a high degree of demineralization of high quality drinking water. The vapor transition module 1674 is another option for diluting the desiccant. They allow the use of seawater and other forms of non-potable water as feed 1681. Their transfer rates are temperature dependent, so they tend to be located in a regeneration loop where the hot and concentrated liquid desiccant 652 from 648 is diluted 1615. When the size of the vapor conversion unit is less important, it can be used in a conditioner loop to dilute the concentrated liquid desiccant to 1610. This is also applicable in heat pump solutions where heating and humidification are the main applications. The strength of the water used by the system and the scarcity of drinking water will influence this choice. For example, if the unit is used in a highly humid climate, where only water addition is rarely used to protect the unit, a cheaper direct addition solution to the reservoir may be more likely, especially if the problem with the delivery of minerals into the desiccant system is limited

Fig. 17 discloses a multiple split system with possibly multiple indoor units 1701 at different floors of the building. In this case, multiple desiccant reservoirs 610 may be used to optimize pressure and flow control. A multi-tank system may be included that includes a single regenerator. This flexibility is crucial in multi-layer multi-space solutions. The desiccant storage tank, the water addition module, the heat exchanger, and the pump may all be positioned in a separate "intermediate unit" 1702 located in a space inside the building, the space having a water supply and a water tank. In this case, the external unit 1703 is very similar in size and weight to a conventional unit, including only the fan, compressor and regenerator panels. Reducing the size of the external unit and ensuring that there is an abundance of water is a key consideration for the success of this solution, particularly for residential units.

Fig. 18 is a diagram from U.S. patent No. 9470426 showing a liquid desiccant system for a building 105 having multiple conditioners 502 and a single regenerator 601. Some of these are ceiling units for the space 110, which use recirculated air. The other may be a DOAS unit 604, which DOAS unit 604 uses a mixture of outside air and exhaust air 102 to condition air 101. A separate regenerator unit 601, shown adjacent to the large chiller 114, provides efficient cooling to the chiller's condenser and uses that cooling to re-concentrate the liquid desiccant from the ceiling unit and the DOAS unit 604. The interior space 106 is used to position a desiccant system 501 that includes the conditioner 50. These units condition return air 109 and outside air 103 processed by DOAS unit 604 to supply air 108 to the space. To do this, desiccants 504 and 505 are required to travel to and from the central regeneration unit via 602 and 603 including the DOAS requirements. And cold water from cooler 114 is supplied through pipes 112 and 113.

This system is best suited for spaces having similar requirements for each of the spaces 110. But does vary due to at least occupancy and location and usage. Some of these zones (e.g., operating rooms in hospitals) may use only outside air, some zones (e.g., sports facilities available for regeneration) may have large amounts of exhaust air, and other zones (e.g., swimming pools) may have a large humidity load but a low demand for fresh air. Thus, each of those spaces may therefore require a different SHR.

This is particularly important for some applications (e.g., grocery stores). Grocery stores typically have wet sections for fruits and vegetables that remain warm and moist. Most buildings require lower temperatures and dry balls, for example, to maximize product life and customer comfort. Cold sections with refrigerated goods typically require lower temperatures and lower humidity levels to avoid container frosting. In buildings having one chiller system using multiple tools, the liquid desiccant system is able to meet such multiple requirements.

Fig. 19 shows how a chiller system 1900 using an evaporator 1901 supplies cold water 1902 to a plurality of regulators (1904, 1905-190 n), returning warmer water 1903. The condenser 1911 supplies hot water 1912 to a plurality of regenerators (1914, 1915, and 191n) to return cooled water 1913. Each of the regulators may serve one of the zones of the building. If the supply conditions 1961 required for the spaces 1931, 1932 and 1933 are different, the desiccants for these spaces should have different concentrations. Thus, each regulator or group of regulators may have its own reservoir 1920, 1921 and 192n with different concentrations of liquid desiccant depending on the desired supply conditions 1961. The volume of the liquid desiccant is determined by the volume of the air to be treated 1960, which air to be treated 1960 may be a mixture of outside air 1960 and return air 1964. Regeneration is required to maintain this condition, and a high concentration of liquid desiccant is supplied from each of the storage tanks 1930, 1931, and 193n, each having its own concentration, which is related to the availability of outside air OA 1965 and bleed air EA (1964) to maintain that concentration.

When low concentrations of liquid desiccants are required to maintain relatively humid conditions, such as in the greenhouse or supermarket vegetable sectors, then regeneration with high flows of outside air 1963 can result in maximum explicit cooling. If even more dilution is required, for example because the external conditions are already fairly dry, further dilution of the desiccant can be achieved by flowing additional external air 1965 through the sensible coils 1951, 19522 and 195 n. Alternatively, direct water addition using a vapor transport membrane unit is an option.

When high concentrations of liquid desiccant are required, air cannot be used for sensible coil 1951-195 n. The coils can even be eliminated for this regenerator sub-unit during the design phase. Low airflow through the regenerator will reduce the apparent efficiency of the panel and may increase submerged regeneration.

Even higher concentrations can be achieved using dry exhaust air from the building. Since the exhaust air is not available anywhere, the regenerator may be placed close to the exhaust location, simply by transferring the desiccant to an appropriate reservoir.

Multiple desiccant and water storage tanks may be used in complex buildings for the purpose of more effectively managing pressure drop and desiccant and water flow.

A combination of sensible coils and/or direct water dilution can be used to vary the concentration of the desiccant. Fig. 19 shows such a configuration. The regenerators 1914, 1915 to 191n are all fed by a single condenser coil 1911. However, the concentration of the desiccant exiting the regenerator may still vary. First through air cooling coils 1951 through 195n, etc. in series or parallel (series shown) with regenerators 1914, 1915, etc. on a water circuit. When sensible coils 1951, 1952 to 195n are in parallel, heat can be transferred from the regenerator by increasing the transfer flow from the regenerator to the air cooling coil. This will reduce the concentration. When they are in series, the concentration can be varied by flowing more or less air through the regenerator and air cooling coils.

Fig. 20 shows how a pump similar to the mechanism shown in fig. 10 and 11 can be used to connect the tanks in various ways to match the expected load. The concentrated liquid desiccant 2001 flows from the regenerator reservoirs 1930, 1931-193 n to the conditioner reservoirs 1920, 1921, and 192 n. The diluted liquid desiccant 2002 is sent from the conditioner to the regenerator. By using a valve system instead of a fixed connection, dynamic control is possible. Since the desiccant concentration directly drives the supply air RH, multiple reservoirs can also improve system response time by: several available concentrations of desiccant are allowed to be maintained, allowing switching between reservoirs to meet varying conditions when needed.

Each space has its own liquid desiccant circuit and the desiccant can be circulated through the panels 1904 to 190n and back to the reservoir 2101 through the heat exchanger 2102. The adjustable valve 2103 allows some or all of the desiccant from the reservoir to be mixed into it. The second adjustable valve 2104 allows a portion of the diluted desiccant to be returned to the reservoir. By controlling the circulation rate with pump 2105 and the mixing rate with valves 2104 and 2103, the desiccant concentration can be varied from space to space. Since the concentration directly drives the RH provided to the space, the inventors can change the RH by the mixing ratio. Using a similar arrangement on the water/heat transfer fluid side, the inventors can independently control the temperature and humidity provided to the space.

Fig. 21 shows duck-type curves in california in different years between 2012 and 2020. In the past, the load for the network would peak at 12 pm (2204). In 2012, the peaks are in the early morning and late night, while in the future, the main peak 2203 will be in the evening and in the morning 2201, the load is significantly reduced, since the solar power supply is higher during the day. The curve is dominated by cooling requirements which are lower in the morning but still higher for a few hours after sunset. Concentrated liquid desiccant may be stored to handle this load. To meet all the requirements of dehumidification, about 2 to 20 liters per ton are required at very high concentrations (35-45%) to manage the total dehumidification load. At the hottest times of the day, the RH level of the outside air tends to be lower, making the desiccant more easily concentrated. Where utility demand management contributes to the value of this feature, it is desirable to maximize the value of this function, justifying the cost of additional tank space and system complexity.

Fig. 22 shows a typical daily temperature cycle in a humid hot climate. The conditions changed from a cold and high RH in the early morning to a hot and lower RH in the late afternoon (2301). The outside air DP (2302) tends to stabilize during this cycle, while RH changes from a low of 40% to as high as 95% in the early morning (2301). Thus, a utility may wish to shift a large amount of load from 9 pm to an earlier time of day.

Fig. 23 shows how the outside air humidity 2302(DP) tends to stabilize during the day, but the temperature 2302 varies significantly with a curve similar to that of the solar supply 2303, but at night the temperature is higher. The regulator needs to provide stable conditions throughout the day: typically, the temperature is below 70F and the DP is 40-55% and the RH is 50-60%. Depending on the total load and the external air conditions, the RH of the supply conditions is determined by the concentration of the liquid desiccant. Typically, a 70% RH requires a liquid desiccant concentration of about 20%, and a 10% liquid desiccant gives about 80% RH.

The dehumidification load and supply conditions of a building tend to be stable during the day, varying mainly due to occupancy. The liquid desiccant regeneration capacity is driven by the availability of heat. In compressor-based systems, more heat is available when the sensible load is higher at noon and later in the day, while much less heat is available early in the morning.

The liquid desiccant regeneration capacity 2301 is driven by the availability of heat. In compressor-based systems, more heat is available when the sensible load is higher at noon and later in the day, while much less heat is available early in the morning.

Fig. 23 shows how during a typical east coast daily cycle, the temperature will rise from 20C in the morning 2004 to 35C at noon 2401. This will reduce the RH from 85% to 40% (2400). Subtropical 2401 and tropical 2402 conditions may vary less throughout the day with RH ranging from 85% to 50-70%. Supply condition 2403 can undergo much less change at very high humidity, except for sensible heat load from light and infiltration that needs to be compensated for in supply condition 2403. For conditions 2402 and 2404, the Sensible Heat Ratio (SHR) may change from 80% at 2400 to between 0 and 0.2. U.S. patent application No. 62/580,270 describes how to manage regeneration using sensible coils from wet conditions 2402 and dry conditions 2400 to the same supply conditions 2403.

One significant problem is the availability of regenerative heat. Figure 24 shows how the conditioning and regeneration are unbalanced in a compressor based system without correction from the sensible coil. In morning condition 2500a, conditions require a liquid desiccant at a concentration of about 25% to dehumidify and heat air to supply condition 2509 a. The enthalpy difference 2540a is too small to be effectively regenerated, so the regenerator can only achieve 95% RH, which corresponds to a liquid desiccant concentration of 10%

In the afternoon, the regulator needs to do more work 2540b to bring the air to the preferred supply condition 2509b at 2500b with the same DP but much higher DB. On the condenser side, the regenerator is then able to produce liquid desiccant at concentrations up to 40%. The regulator still only needs 25% concentration-the same as in the morning. The early patents explain how sensible coils, desiccant dilution and additional heat load are used to add energy in the early morning and to exhaust energy in the evening to balance the system.

Additional coils are a significant additional cost. These coils also reduce system efficiency by increasing load in the morning and increasing compressor lift in the evening.

There is a similar imbalance of energy available for regeneration at different points during the day in non-compressor based systems. For example, in thermal solar-based evaporative cooling (DEVAP or desiccant activated evaporative cooling), regeneration is only performed when sunlight is shining, and cooling and dehumidification is still required during the day. Systems that use waste heat (e.g., from cogeneration) have heat that is only available when electricity is needed. The storage of heat may be in the form of hot water, but requires a large volume.

By using liquid desiccant storage as a way to manage short term fluctuations between high and low RH conditions, additional coil and hot water storage can be avoided while maintaining the ability to maintain supply conditions over the range of environmental conditions often encountered during the day.

The patent applicant's earlier patents describe how to use air cooling coils to reject excess heat and generate additional load by cooling the regeneration exhaust air or outside air. Both of which require the compressor to do more work. Instead of using advanced dehumidification and heat rejection coils, concentrated liquid desiccant can be generated by the regenerator when excess compressor heat is available, then stored and used only when needed to maintain conditioner supply conditions. The latter avoids the need for additional loading of advanced dehumidification coils

Liquid desiccant storage is highly effective compared to other forms of heat storage, with about 30kWh of evaporative humidity per gallon, or about 12kWh per gallon of "storage tank" space. The liquid desiccant concentration peaks at sunset and is lowest at sunrise. It does require a larger storage tank and pump, but the size and weight of these will be at least partially offset by avoiding the need for air cooling coils and fans.

FIG. 25 shows how the conditioner 2600 dehumidifies and cools air in a cooling mode.it takes a higher concentration of liquid desiccant 2601 from a reservoir 2602 with a pump 2608. diluted liquid desiccant 2603 is returned to the reservoir 2602. regenerator 2604 concentrates desiccant 2605 from reservoir 2606 and returns a higher concentration of desiccant 2607. pumps 2608 and 2609 pump desiccant from respective reservoirs 2602 and 2606 to the conditioner and regenerator. As the desiccant in reservoir 2602 is diluted and cooled and the desiccant in reservoir 2606 becomes more concentrated and warmer, pumps 2611 and 2612 are required to pump desiccant through a heat exchanger 2610 between the two reservoirs.

In the heating mode, the temperature and concentration in the tank are reversed.

For a two-tank system, the system would use 20-25% diluted liquid desiccant during the cool down period at 2500a under those conditions, the cool down is nearly adiabatic so the compressor does little work 2540a to reach supply condition 2509a since the RH of air is still > 90%, heat 2511a is not sufficient to reconcentrate the liquid desiccant heat from the regenerator is available at 2500b at a later time of day with the compressor doing a lot of work 2540b, the work 2540b being available to the regenerator, the regenerator has total enthalpy from 2509 and heat from the regenerator is available to regenerate 2511b so the regenerator can reach a temperature that easily reconcentrates the desiccant from 25% to a high concentration of 40%, if heat rejection coils are still needed, it can be sized to prevent over-concentration (about 50% concentration), in which case the desiccant (e.g., L iC L) would crystallize EER or e would not improve the additional work needed to maintain the concentration during cold conditions mra 2005.

As described in U.S. provisional patent application No. 62/580,270, the efficiency of the conditioning and regeneration process can be further enhanced by further separating the concentrated liquid desiccant in stratified or divided reservoirs 2701 and 2702.

Assuming a maximum concentration of 40% and a minimum concentration of 20% for the liquid desiccant, a 2 gallon storage tank can store about 1 ton of hours or 3.4kWh of dehumidification capacity, this corresponds to a required system power of about 1kWh at an MRE of 4kg/kWh, this requires about 1/2 gallons of liquid desiccant (e.g., L iCl, CaCl, or equivalent).

While several illustrative embodiments have been described so far, it should be understood that various alterations, modifications, and improvements will readily occur to those skilled in the art. Such alterations, modifications, and improvements are intended to form part of this disclosure, and are intended to be within the spirit and scope of the disclosure. Although some of the examples presented herein involve specific combinations of functions or structural elements, it should be understood that those functions and elements may be combined in other ways to accomplish the same or different objectives in accordance with the present disclosure. In particular, acts, elements, and features discussed in connection with one embodiment are not intended to be excluded from a similar or other role in other embodiments, and the elements and components described herein may be further divided into additional components or joined together to form fewer components for performing the same function. Accordingly, the foregoing description and drawings are by way of example only and are not intended as limiting.