Heat pump humidifier and dehumidifier system and method

A heat pump system for conditioning air supplied to a space is provided. The system includes a pre-processing module that pre-conditions supply air. A supply air heat exchanger is in flow communication with the pre-processing module. The supply air heat exchanger receives air from the pre-processing module and at least one of heats or cools the air from the pre-processing module. A processing module is in flow communication with the supply air heat exchanger. The processing module receiving and conditioning air from the supply air heat exchanger. A regeneration air heat exchanger is provided to at least one of heat or cool regeneration air. The regeneration air heat exchanger and the supply air heat exchanger are fluidly coupled by a refrigerant system.

BACKGROUND OF THE INVENTION

The subject matter herein relates generally to heat pumps and, more particularly, to a heat pump humidifier and dehumidifier system and method.

Heat pumps are used to condition air supplied to a building or structure. Typically, the supply air passes through a first heat exchanger to adjust a temperature and humidity of the supply air. The supply air is then channeled to a desiccant wheel to humidify or dehumidify the air prior to discharging the air into the space. Generally, return air is utilized to regenerate the desiccant wheel by humidifying or dehumidifying the regeneration air. When the supply air is humidified, the regeneration air is dehumidified. When the supply air is dehumidified, the regeneration air is humidified. Generally, the regeneration air also passes through a second heat exchanger prior to passing through the desiccant wheel. The first and second heat exchangers usually transfer energy between the supply air and the regeneration air.

Typically, the regeneration air is supplied from inside the space. As such, outside air generally lacks sufficient energy to properly regenerate the desiccant wheel. Accordingly, known heat pump systems may operate at reduced efficiencies when using outside air to regenerate the desiccant wheel. Because of the reduced efficiency of the heat pump, the heat pump may not be capable of conditioning some outside air. In particular, known heat pumps generally lack the capability of conditioning outside air having extreme hot or extreme cold temperatures.

A need remains for a more efficient heat pump system or method that utilizes the energy of return air to regenerate the desiccant wheel, increase effectiveness of the heat pump and provides considerable humidification load reductions to building operation. Another need remains for a heat pump that pre-processes supply air to enable the heat pump to operate in extreme weather conditions without significant reduction in efficiency.

SUMMARY OF THE INVENTION

In one embodiment, a heat pump system for conditioning air supplied to a space is provided. The system includes a pre-processing module that pre-conditions supply air. A supply air heat exchanger is in flow communication with the pre-processing module. The supply air heat exchanger receives air from the pre-processing module and at least one of heats or cools the air from the pre-processing module. A processing module is in flow communication with the supply air heat exchanger. The processing module receives and conditions air from the supply air heat exchanger. A regeneration air heat exchanger is provided to at least one of heat or cool regeneration air. The regeneration air heat exchanger and the supply air heat exchanger are fluidly coupled by a refrigerant system.

In another embodiment, a method for conditioning air supplied to a space is provided. The method includes pre-conditioning supply air with a pre-processing module. The method also includes at least one of heating or cooling the air from the pre-processing module with a supply air heat exchanger in flow communication with the pre-processing module. The method also includes conditioning air from the supply air heat exchanger with a processing module in flow communication with the supply air heat exchanger. The method also includes at least one of heating or cooling regeneration air with a regeneration air heat exchanger that is fluidly coupled to the supply air heat exchanger by a refrigerant system.

In another embodiment, a method for conditioning air supplied to a space is provided. The method includes conditioning supply air with a processing module. The method also includes at least one of heating or cooling the air prior to or after the processing module with one or more supply air heat exchangers in flow communication with the processing module. The method also includes at least one of heating or cooling the regeneration air with one or more regeneration air heat exchanger that is fluidly coupled to the supply air heat exchangers by a refrigerant system.

In another embodiment, a method for conditioning air supplied to a space is provided. The method includes conditioning supply air with a processing module. The method also includes at least one of heating or cooling the air prior to or after the processing module with one or more supply air heat exchangers in flow communication with the processing module. The method also includes at least one heat exchanger switch in flow communication with the supply air heat exchangers that is fluidly coupled to a refrigerant system.

In another embodiment, a method for conditioning air supplied to a space is provided. The method includes conditioning supply air with a processing module. The method also includes at least one of heating or cooling the air prior to or after the processing module with one or more supply air heat exchangers in flow communication with the processing module. The method also includes at least one heat exchanger switch in flow communication with the supply air heat exchangers that is fluidly coupled to a refrigerant system and a control method that allows the space sensible load and latent load to be maintained independently.

DETAILED DESCRIPTION OF THE DRAWINGS

FIG. 1is a schematic view of a heat pump system100formed in accordance with an embodiment and operating in a summer mode130.FIG. 2is a schematic view of the system100operating in a winter mode132. The system100is configured to condition supply air flowing into a building or space and return air channeled from within the building or space. When in the summer mode130, among other things, the system100dehumidifies the supply air flowing into the building. When in the winter mode132, among other things, the system100humidifies the supply air flowing into the building. The system100is capable of switching between the summer mode130and the winter mode132without the need to reconfigure the components of the system100.

First, the operation of system100is described in connection with the summer mode130, as illustrated inFIG. 1. In the summer mode130, the system includes a supply air flow path112and a return air flow path120. The supply air flow path112travels between a supply air inlet108and a supply air outlet110. In one embodiment, the system100may include at least one fan to draw air into and move air through the supply air flow path112. Outside air flows through the supply air inlet108and into an outside air region101.

A pre-processing module102is positioned downstream of the outside air region101. In one embodiment, the pre-processing module102may include an energy recovery device, such as, an enthalpy wheel, a fixed enthalpy plate, an enthalpy pump and/or any other suitable heat exchanger that transfers both sensible heat and latent heat. In one embodiment the pre-processing module102is formed as a fixed body heat exchanger, an air to air heat exchanger, an air to liquid heat exchanger, a liquid to air heat exchanger, or liquid to liquid heat exchanger. The pre-processing module102includes a supply air side109and a return air side111. The supply air side109is positioned within the supply air flow path112. The return air side111is positioned within the return air flow path120.

Outside air passes through the supply air side109of the pre-processing module102. The pre-processing module102is configured to transfer latent energy and sensible energy between the supply air flow path112and the return air flow path120. The latent energy includes moisture in the flow paths112and120. The pre-processing module102transfers heat from a warmer flow path to a cooler flow path. The pre-processing module102also transfers humidity from a high humidity flow path to a low humidity flow path. The outside air is cooled as the outside air passes through the pre-processing module102. The cooled air from the pre-processing module102is discharged into a pre-processed air region103positioned downstream from the pre-processing module102.

A supply air heat exchanger106is positioned downstream from the pre-processed air region103. The supply air heat exchanger106operates as an evaporator coil or cooling coil in the summer mode130. As an evaporator coil, the supply air heat exchanger106conditions the cooled air and further removes heat from the cooled air to produce saturated air that is discharged into a conditioned air region105. The amount of energy required to saturate air is proportional to the temperature and humidity of the air conditions in the pre-processed air region. Generally cooler air requires less energy to become saturated than warmer air. Because the supply air is first cooled by the pre-processing module102, the energy expended by the supply air heat exchanger106to saturate the supply air to the desired saturated conditions is reduced, thereby increasing an efficiency of the supply air heat exchanger106as the supply air heat exchanger106saturates or cools the air. In the summer mode130, the system100is capable of operating at extreme temperatures. For example, in the summer mode130, the pre-processing module is capable of conditioning outside air having a dry bulb temperature over 90° F. Additionally, the supply air heat exchanger106is capable of conditioning air having a dry bulb temperature over 80° F.

A processing module104is positioned downstream from the conditioned air region105. The saturated air passes through the processing module104. In one embodiment, the processing module104may include a desiccant wheel, liquid desiccant system or any other suitable exchanger that removes and/or transfers moisture from the air. The processing module104may utilize any one of, or a combination of drierite, silica gel, calcium sulfate, calcium chloride, montmorillonite clay, activated aluminas, zeolites and/or molecular sieves to absorb moisture in the air. Other components that may also be used by the processing module are halogenated compounds such as halogen salts including chloride, bromide and fluoride salts, to name a few examples. In one embodiment, the processing module104is formed as a fixed body heat exchanger, an air to air heat exchanger, an air to liquid heat exchanger, a liquid to air heat exchanger, or liquid to liquid heat exchanger. The processing module104includes a supply air side113and a return air side115. The supply air side113is positioned within the supply air flow path112and the return air side115is positioned within the return air flow path120. The saturated air passes through the supply air side113to remove moisture therefrom and produce conditioned supply air that has been further dehumidified. Because the air is first saturated by the supply air heat exchanger106, the efficiency of the processing module104is increased when dehumidifying the air. The dehumidified supply air flows downstream into a processed air region107. From the processed air region107, the dehumidified supply air flows through the supply air outlet110and into the space.

Regeneration air in the form of return air leaves the space at return air inlet116and traverses a return air flow path120. The return air flow path120is defined between the return air inlet116and a return air outlet118. In one embodiment, the system100may include at least one fan to draw air into and move air through the return air flow path120. Return air enters through the return air inlet116and flows downstream into the return air region117.

The return air side111of the pre-processing module102is positioned downstream from the return air region117. The return air passes through the return air side111of the pre-processing module102. The pre-processing module102transfers heat and moisture into the return air passing through the return air side111, thereby removing heat from the supply air passing through the supply air side109. The heated air flows into a pre-processed air region119and through a series of dampers125,127,129, and131. In the summer mode130dampers125and129are opened and dampers127and131are closed to direct the heated air to a regeneration air heat exchanger114positioned downstream from the damper125.

The regeneration air heat exchanger114operates as a condenser coil in the summer mode130to heat and lower a relative humidity of conditioned air. The heat exchanger114uses the heat from the supply air heat exchanger106to lower the relative humidity of the heated air thus increasing the air's capacity to absorb water downstream. The heated air flows into a conditioned air region121. The lowered relative humidity air in the conditioned air region121is channeled downstream to the return air side115of the processing module104.

The lowered relative humidity air passing through the return air side115of the processing module104regenerates the processing module104by receiving moisture from the saturated air in the supply air side113and adding humidity to the exhaust air that flows into a processed air region123. The exhaust air is channeled through the open damper129, through return air outlet118, and is exhausted from the space.

In one embodiment, the heat pump system100senses a condition of at least one of the supply air or return air from the space to control an output of at least one of the pre-processing module102, the processing module104, the supply air heat exchanger106, and/or the regeneration air heat exchanger114to achieve a pre-determined dehumidification in the summer mode130and pre-determined humidification in a winter mode130.

In another embodiment, the heat pump system100senses a condition of at least one of the supply or return air from the space to control an output of at least one of the pre-processing module102, the processing module104, the supply air heat exchanger106, and/or the regeneration air heat exchanger114to achieve a pre-determined performance of the system100.

In another embodiment, the heat pump system100senses a condition of at least one of the supply air or return air from the space to control an output of at least one of the pre-processing module102, the processing module104, the supply air heat exchanger106, and/or the regeneration air heat exchanger114to limit frost formation in the pre-processing module102and/or the regeneration air heat exchanger114in the winter mode132.

In another embodiment, the heat pump system100senses a condition of at least one of the supply air or the return air from the space to control an output of at least one of the pre-processing module102or the processing module104.

In another embodiment, at least one of the pre-processing module102or processing module104is formed as a rotating body. The rotating body is rotated with at least one of a pre-determined speed or a predetermined range to achieve a pre-determined amount of at least one of moisture transfer or heat transfer to limit frost formation in the pre-processing module102and/or the regeneration air heat exchanger114. A rotational speed of at least one of the pre-processing module102and/or the processing module104may be adjusted to a predetermined range, such that the pre-processing module102operates as at least one of a sensible wheel, a enthalpy wheel or a desiccant wheel based on variations in the outside air or return air from the space.

In another embodiment, the heat pump system100senses a condition of at least one of a supply air stream or a return air stream to control the output of at least one of a single compressor or variable compressor to limit frost formation in the pre-processing module and or the heat exchanger in winter mode.

In another embodiment, the heat pump system100senses a condition of at least one of a supply air stream or a return air stream to control the output of at least one of a single compressor or variable compressor to achieve a pre-determined performance of the system100.

It should be noted that the system100is exemplary only and may include any number of pre-processing modules102, processing modules104, supply air heat exchangers106and/or regeneration air heat exchangers114. Additionally, the arrangement of the components may be varied. The components described herein are arranged to provide a balance in energy between the supply air flow path112and the return air flow path120.

The system100includes a refrigerant system133having piping135that fluidly couples the supply air heat exchanger106and the regeneration air heat exchanger114. The refrigerant system133pumps a refrigerant between the supply air heat exchanger106and the regeneration air heat exchanger114. In the summer mode130, the refrigerant system133pumps cooled refrigerant to the supply air heat exchanger106to cool the air flowing through the supply air heat exchanger106. The cooled refrigerant is heated by the air in the supply air heat exchanger106to form heated refrigerant. The heated refrigerant flows through the piping135to the regeneration air heat exchanger114to heat the air flowing through the regeneration air heat exchanger114. The refrigerant is cooled by the air in the regeneration air heat exchanger114to form cooled refrigerant that is pumped back to the supply air heat exchanger106.

In the winter mode132, the refrigerant system133pumps heated refrigerant to the supply air heat exchanger106to heat the air flowing through the supply air heat exchanger106. The heated refrigerant is cooled by the air in the supply air heat exchanger106to form cooled refrigerant. The cooled refrigerant flows through the piping135to the regeneration air heat exchanger114to cool the air flowing through the regeneration air heat exchanger114. The refrigerant is heated by the air in the regeneration air heat exchanger114to form heated refrigerant that is pumped back to the supply air heat exchanger106.

The refrigerant system133may include a metering device and check valve system137to control a flow of the refrigerant between the supply air heat exchanger106and the regeneration air heat exchanger114. Additionally, a switch139may be provided to reverse a flow of the refrigerant through the refrigerant system133. For example, the flow of the refrigerant may be reversed when the system100is switched between the summer mode130and the winter mode132. A compressor141is provided to compress the refrigerant. In the summer mode130, the refrigerant passes through the compressor141after exiting the supply air heat exchanger106and before entering the regeneration air heat exchanger114. In the winter mode132, the refrigerant passes through the compressor141after exiting the regeneration air heat exchanger114and before entering the supply air heat exchanger106.

FIGS. 3 and 4illustrate psychrometric charts350and400for the system100when operating in the summer mode130. It should be noted that the charts350and400are exemplary only and illustrate a single operating point for the summer mode130conditions. The charts350and400include an x-axis300that illustrates a dry bulb temperature of the air in degrees Fahrenheit and a y-axis302that illustrates vapor pressure in inches of mercury. A second y-axis304illustrates a humidity ratio in grains of moisture per pound of dry air. Curve306illustrates a saturation point of the air and lines308illustrate an enthalpy of the air in BTU per pound of dry air. Lines310illustrate a wet bulb temperature of the air in degrees Fahrenheit. A sensible heat ratio is illustrated on line312and a dew point temperature in degrees Fahrenheit is illustrated on line314. A relative humidity of the air is illustrated on curves316and a volume of the air in cubic feet per pound of dry air is illustrated on curves318.

FIG. 3is a psychrometric chart350illustrating the condition of the air in the supply air flow path112when the system100is operating in the summer mode130and when the supply air enters the outside air region101at point352on chart350. The supply air has a dry bulb temperature of approximately 95° F. and a wet bulb temperature of approximately 78° F. The enthalpy of the supply air is approximately 42 BTU per pound of dry air and the humidity ratio is approximately 120 grains of moisture per pound of dry air.

The supply air passes through the supply air side109of the pre-processing module102. The pre-processing module102cools the supply air to generate cooled air that is discharged into the pre-processed air region103of the system100. Point354of chart350illustrates the conditions of the cooled air within the pre-processed air region103. The cooled air has a dry bulb temperature of approximately 80° F. and a wet bulb temperature of approximately 68.5° F. The enthalpy of the cooled air is approximately 33 BTU per pound of dry air and the humidity ratio is approximately 86 grains of moisture per pound of dry air.

The cooled air flows downstream to the supply air heat exchanger106and is conditioned to near the saturation curve306. The supply air heat exchanger106operates as an evaporator coil to further reduce the temperature of the cooled air and generate saturated air. The cooled saturated air is discharged into the conditioned air region105. Point356of chart350illustrates the conditions of the saturated air within the conditioned air region105. At point356the saturated air has a dry bulb temperature of approximately 52° F. and a wet bulb temperature of approximately 52° F. The enthalpy of the saturated air is approximately 22 BTU per pound of dry air and the humidity ratio is approximately 58 grains of moisture per pound of dry air.

Next the saturated air is channeled through supply air side113of the processing module104. The processing module104removes moisture from the saturated air to generate dehumidified supply air within the processed air region107. Point358of chart350illustrates the conditions of the supply air. The supply air has a dry bulb temperature of approximately 74° F. and a wet bulb temperature of approximately 57° F. The enthalpy of the supply air is approximately 24.5 BTU per pound of dry air and the humidity ratio is approximately 42 grains of moisture per pound of dry air. The supply air is discharged through the supply air outlet110and into the space.

FIG. 4is a psychrometric chart400illustrating the condition of the air in the return air flow path120when the system100is operating in the summer mode130. The return air enters the system100through the return air inlet116. Point402of chart400illustrates the condition of the return air within the return air region117. The return air has a dry bulb temperature of approximately 74° F. and a wet bulb temperature of approximately 62.5° F. The enthalpy of the return air is approximately 28 BTU per pound of dry air and the humidity ratio is approximately 66 grains of moisture per pound of dry air.

The return air flows through the return air side111of the pre-processing module102. The heat and moisture removed from the supply air on the supply air side109of the pre-processing module102is transferred into the return air on the return air side111of the pre-processing module102to generate heated air. The heated air flows into the pre-processed air region119. Point404of chart400illustrates the conditions of the heated air. At point404the heated air has a dry bulb temperature of approximately 88° F. and a wet bulb temperature of approximately 73° F. The enthalpy of the heated air is approximately 36 BTU per pound of dry air and the humidity ratio is approximately 98 grains of moisture per pound of dry air.

The heated air passes through the regeneration air heat exchanger114. In the summer mode130, the regeneration air heat exchanger114operates as a condenser coil and transfers the heat from the supply air heat exchanger106to the return air flow path120. The heat exchanger114also lowers a relative humidity of the air to increase the air's capacity to absorb water downstream. The dry air is discharged into the conditioned air region121. Point406of chart400illustrates the conditions of the dry air within the conditioned air region121. At point406the dry air has a dry bulb temperature of approximately 110° F. and a wet bulb temperature of approximately 79° F. The enthalpy of the dry air is approximately 42 BTU per pound of dry air and the humidity ratio is approximately 98 grains of moisture per pound of dry air.

The dry air travels downstream to the return air side115of the processing module104. The processing module104transfers moisture from the cooled saturated air in the supply air side113to the heated dry air in the return air side115. Point408of chart400illustrates the conditions of the exhaust air. The exhaust air has a dry bulb temperature of approximately 87° F. and a wet bulb temperature of approximately 77° F. The enthalpy of the exhaust air is approximately 41 BTU per pound of dry air and the humidity ratio is approximately 125 grains of moisture per pound of dry air. The exhaust air is discharged from the space through the return air outlet118.

Next, the operation of system100is described in connection with the winter mode132, as illustrated inFIG. 2. In the winter mode132, the supply air flow path112follows the same path as defined in the summer mode130. In the winter mode132, the function of the system components may differ from the function of the system components in the summer mode130.

Outside air flows through the supply air inlet108and into the outside air region101. The outside air in the outside air region101travels downstream through the supply air side109of the pre-processing module102. The outside air is heated by the pre-processing module102to generate heated and humidified air that is discharged into the pre-processed air region103.

The heated and humidified air in the pre-processed air region103passes through the supply air heat exchanger106. The supply air heat exchanger106operates as a condenser coil in the winter mode132to lower a relative humidity of the heated air and increase the air's capacity to absorb water downstream. The supply air heat exchanger106generates dry air that is discharged into the conditioned air region105. When processing air having extreme cold temperatures, the supply air heat exchanger will be operating in a very inefficient matter. Because the outside air is first heated by the pre-processing module102, the supply air heat exchanger106is capable of heating outside air having extreme cold temperatures very efficiently. For example, the pre-processing module102is capable of conditioning air having a temperature below 32° F. Using the components illustrated inFIG. 2, the pre-processing module102is capable of conditioning air having a temperature between −10° F. and 32° F. With additional components, the pre-processing module102is capable of conditioning air having temperature between −30° F. and 32° F. Moreover, the supply air heat exchanger106is capable of conditioning air having a temperature below 50° F., in the winter mode132.

The lowered relative humidity heated air travels from the supply air heat exchanger106through the supply air side113of the processing module104. The processing module adds moisture to the conditioned air to produce humidified supply air. The humidified supply air flows into the processed air region107. From the processed air region107, the supply air flows through the supply air outlet110and into the space.

The return air flow path140of the winter mode132differs from the return air flow path120of the summer mode. The dampers125,127,129, and131may be opened and/or closed to change the return air flow path120of the summer mode130to return air flow path140of the winter mode132. Additionally, the functions of at least some of the system components may change in the winter mode132. The return air flow path140is defined between the return air inlet116and a return air outlet142.

Return air flows through the return air inlet116and into the return air region117. The return air then flows into the return air side111of the pre-processing module102. The pre-processing module102transfers heat and moisture from the return air into the supply air passing through the supply air side109of the pre-processing module102, thereby cooling the air in the return air flow path140. The cooled air flows into the pre-processed air region119and is channeled through dampers125,127,129, and131. In the winter mode132dampers125and129are closed and dampers127and131are opened to direct the cooled air to the return air side115of the processing module104.

The processing module104is regenerated by the supply air. The processing module104removes moisture from the cooled air in the return air side115and discharges the moisture into the dry air in the supply air side113. The processing module104dehumidifies air in the return air flow path140while humidifying the supply air flow. The dehumidified air is discharged into a processed air region144. The dehumidified air in the processed air region144is channeled to the regeneration air heat exchanger114.

The regeneration air heat exchanger114operates as an evaporator coil in the winter mode130to cool the dehumidified air. The regeneration air heat exchanger114also removes heat from the return air and discharges the heat to the supply air heat exchanger106. The heat exchanger114cools the dehumidified air to generate cooled exhaust air. When cooling air having extreme cold temperatures, the regeneration air heat exchanger114is susceptible to freezing. Because the return air is first dehumidified by the processing module104, the dehumidified air in the processed air region144is able to be cooled by the regeneration air heat exchanger114to very cold temperatures without the risk of freezing. Furthermore, as the return air is dried by the processing module104, the air's dry bulb condition in the processed air region144is raised, thus enabling additional heat transfer to the supply air heat exchanger106improving efficiency of the system. The cooled exhaust air flows into a conditioned air region146and is channeled through return air outlet142and exhausted from the building.

FIGS. 5 and 6illustrate psychrometric charts450and500for the system100when operating in the winter mode132. It should be noted that the charts450and500are exemplary only and illustrate a single operating point for the winter mode132operating conditions. The charts450and500include an x-axis300that illustrates a dry bulb temperature of the air in degrees Fahrenheit and a y-axis302that illustrates vapor pressure in inches of mercury. A second y-axis304illustrates a humidity ratio in grains of moisture per pound of dry air. Curve306illustrates a saturation point of the air and lines308illustrate an enthalpy of the air in BTU per pound of dry air. Lines310illustrate a wet bulb temperature of the air in degrees Fahrenheit. A sensible heat ratio is illustrated on line312and a dew point temperature in degrees Fahrenheit is illustrated on line314. A relative humidity of the air is illustrated on curves316and a volume of the air in cubic feet per pound of dry air is illustrated on curves318.

FIG. 5is a psychrometric chart450illustrating the condition of the outside air in the supply air flow path112, when the system100is operating in the winter mode132and when the outside air enters the system100through the supply air inlet108and flows into the outside air region101. Point452of chart450illustrates the conditions of the outside air. At point452, the outside air has a dry bulb temperature of approximately −10° F. and a wet bulb temperature of approximately −10° F. The enthalpy of the outside air is approximately −2 BTU per pound of dry air and the humidity ratio is approximately 3 grains of moisture per pound of dry air.

The outside air passes through the supply air side109of the pre-processing module102where the air is heated and discharged into the pre-processed air region103. Point454of chart450illustrates the conditions of the heated air in the pre-processed air region103. At point454, the heated air has a dry bulb temperature of approximately 30° F. and a wet bulb temperature of approximately 27° F. The enthalpy of the heated air is approximately 9.5 BTU per pound of dry air and the humidity ratio is approximately 16 grains of moisture per pound of dry air.

The heated air passes through the supply air heat exchanger106. In the winter mode132, the supply air heat exchanger106operates as a condenser coil to heat the air using heat discharged from the regeneration air heat exchanger114. The supply air heat exchanger106also lowers a relative humidity of the air to increase the air's capacity to absorb water downstream. The supply air heat exchanger106lowers the relative humidity of heated air that is discharged into the conditioned air region105. Point456illustrates the conditions of the heated air. At point456the heated air has a dry bulb temperature of approximately 90° F. and a wet bulb temperature of approximately 56.7° F. The enthalpy of the dried air is approximately 24 BTU per pound of dry air and the humidity ratio is approximately 16 grains of moisture per pound of dry air.

The heated air travels downstream through the supply side113of the processing module104where humidity from the return air in the return side115is discharged into the lower relative humidity air in the supply side113. The humidified supply air is discharged into the processed air region107. Point458of chart450illustrates the conditions of the supply air. At point458, the supply air has a dry bulb temperature of approximately 70° F. and a wet bulb temperature of approximately 53° F. The enthalpy of the supply air is approximately 22 BTU per pound of dry air and the humidity ratio is approximately 33 grains of moisture per pound of dry air. The supply air is discharged through the supply air outlet110and into the building.

FIG. 6is a psychrometric chart500illustrating the condition of the air in the return air flow path140when the system100is operating in the winter mode132and when the return air enters the system100through the return air inlet116and flows into the return air region117. Point502of chart500illustrates the conditions of the return air. The return air has a dry bulb temperature of approximately 70° F. and a wet bulb temperature of approximately 53° F. The enthalpy of the return air is approximately 22 BTU per pound of dry air and the humidity ratio is approximately 33 grains of moisture per pound of dry air.

The return air flows through the return air side111of the pre-processing module102where heat is removed from the return air and discharged into the outside air in the supply air side109of the pre-processing module102. The pre-processing module102produces cooled air in the return air flow path140that is discharged into the pre-processed air region119. Point504of chart500illustrates the conditions of the cooled air in the pre-processed air region119. The cooled air has a dry bulb temperature of approximately 28° F. and a wet bulb temperature of approximately 27° F. The enthalpy of the cooled air is approximately 10 BTU per pound of dry air and the humidity ratio is approximately 20 grains of moisture per pound of dry air.

The cooled air passes through return air side115of the processing module104. The processing module104transfers humidity from the cooled air in the return air side115to the dry air in the supply air side113of the processing module104. Dehumidified air is discharged from the processing module104into the processed air region144. Point506of chart500illustrates the conditions of the dehumidified air in the processed air region144. The dehumidified air in the processed air region144has a dry bulb temperature of approximately 49° F. and a wet bulb temperature of approximately 34° F. The enthalpy of the dehumidified air is approximately 13 BTU per pound of dry air and the humidity ratio is approximately 7 grains of moisture per pound of dry air.

The dehumidified air then passes through the regeneration air heat exchanger114. In the winter mode132, the regeneration air heat exchanger114operates as an evaporator coil to cool the dehumidified air. The regeneration air heat exchanger114removes heat from the dehumidified air. The heat is discharged into the supply air heat exchanger106to heat the supply air traveling through the supply air heat exchanger106. Cooled exhaust air is discharged from the regeneration air heat exchanger114into the conditioned air region146. Point508of chart500illustrates the conditions of the exhaust air. At point508, the exhaust air has a dry bulb temperature of approximately 10° F. and a wet bulb temperature of approximately 9° F. The enthalpy of the exhaust air is approximately 3 BTU per pound of dry air and the humidity ratio is approximately 7 grains of moisture per pound of dry air. The exhaust air is discharged from the space through the return air outlet142.

FIG. 7is a schematic view of another heat pump system200formed in accordance with an embodiment and operating in a winter mode. The heat pump system200includes many of the elements of the heat pump system100. The elements of the heat pump system200that are the same as the elements of the heat pump system100are denoted using the same reference numerals. The heat pump system200includes a reheat coil202positioned upstream from the regeneration air heat exchanger114that is operational in the winter mode132. The reheat coil202is positioned downstream from the return air side115of the processing module104in the winter mode132. The reheat coil202adds heat, lowers the relative humidity of the return air exiting the return air side115of the processing module104prior to entering the regeneration air heat exchanger114. The reheat coil202may prevent frost formation on the regeneration air heat exchanger114during the winter mode132.

The reheat coil202is fluidly coupled to the refrigeration system133through piping204. The piping204is joined to the compressor141to receive heated refrigerant therefrom. A refrigerant flow control device206may be provided to control a flow of refrigerant to the reheat coil202.

FIG. 8is a psychrometric chart210of the heat pump system200operating in a winter mode132. Point212of chart210illustrates the conditions of the return air. The return air has a dry bulb temperature of approximately 70° F. and a wet bulb temperature of approximately 53° F. The enthalpy of the return air is approximately 22 BTU per pound of dry air.

The return air flows through the return air side111of the pre-processing module102where heat is removed from the return air and discharged into the outside air in the supply air side109of the pre-processing module102. The pre-processing module102produces cooled air in the return air flow path140that is discharged into the pre-processed air region119. Point214of chart210illustrates the conditions of the cooled air in the pre-processed air region119. The cooled air has a dry bulb temperature of approximately 28° F. and a wet bulb temperature of approximately 27° F. The enthalpy of the cooled air is approximately 10 BTU per pound of dry air.

The cooled air passes through return air side115of the processing module104. The processing module104transfers humidity from the cooled air in the return air side115to the dry air in the supply air side113of the processing module104. Dehumidified air is discharged from the processing module104into the processed air region144. Point216of chart210illustrates the conditions of the dehumidified air in the processed air region144. The dehumidified air in the processed air region144has a dry bulb temperature of approximately 49° F. and a wet bulb temperature of approximately 34° F. The enthalpy of the dehumidified air is approximately 13 BTU per pound of dry air.

The dehumidified air then passes through the reheat coil202. Point218of the chart210illustrates the conditions of the reheated air discharged from the reheat coil202. The reheated air has a dry bulb temperature of approximately 63° F. and a wet bulb temperature of approximately 42° F. The enthalpy of the dehumidified air is approximately 16 BTU per pound of dry air.

The reheated air then passes through the regeneration air heat exchanger114. The regeneration air heat exchanger114removes heat from the dehumidified air. The heat is discharged into the supply air heat exchanger106to heat the supply air traveling through the supply air heat exchanger106. Cooled exhaust air is discharged from the regeneration air heat exchanger114into the conditioned air region146. Point220of chart210illustrates the conditions of the exhaust air. At point220, the exhaust air has a dry bulb temperature of approximately 10° F. and a wet bulb temperature of approximately 9° F. The enthalpy of the exhaust air is approximately 3 BTU per pound of dry air and the humidity ratio is approximately 7 grains of moisture per pound of dry air. The exhaust air is discharged from the space through the return air outlet142.

FIG. 9is a schematic view of another heat pump system250formed in accordance with an embodiment and operating in a winter mode. The heat pump system250includes many of the elements of the heat pump system100. The elements of the heat pump system250that are the same as the elements of the heat pump system100are denoted using the same reference numerals. The heat pump system250includes a sub-cooling coil252positioned upstream from the regeneration air heat exchanger114. The sub-cooling coil252is positioned downstream from the return air side115of the processing module104. The sub-cooling coil252adds heat, lowers the relative humidity of the return air exiting the return air side115of the processing module104prior to entering the regeneration air heat exchanger114. The sub-cooling coil252may prevent frost formation on the regeneration air heat exchanger114during the winter mode132.

The sub-cooling coil252is fluidly coupled to the refrigeration system133through piping254. The piping254includes a pair of flow control devices256to control a flow of refrigerant to the sub-cooling coil252. In one embodiment, the refrigerant system133may also include an additional metering device and check valve system258to control the flow of refrigerant therethrough.

FIG. 10is a schematic view of another heat pump system150operating in a summer mode180.FIG. 11is a schematic view of the system150operating in a winter mode182. In the summer mode180, a supply air flow path162and a return air flow path170flow through the system150. In the winter mode182, the supply air flow path162follows the same path as defined in the summer mode180and return air follows a return air flow path190. In the winter mode182the function of the system components may differ from the function of the system components in the summer mode180. The system150includes dampers171,172,173, and174to redirect the return air path170of the summer mode180into the return air path190of the winter mode182.

Referring to the summer mode180illustrated inFIG. 10, outside air flows through the supply air inlet158and downstream to a supply air side151of a pre-processing module152. The pre-processing module152removes heat from the outside air. The outside air discharged from the pre-processing module152flows into a pair supply air heat exchangers156and157. In the summer mode180, the supply air heat exchangers156and157operate as evaporator coils to saturate the outside air. The outside air then flows downstream to a supply air side155of a processing module154. The processing module154removes moisture from the outside air to generate dehumidified supply air that is discharged through the supply air outlet160and into the space. At least one fan (not shown) may be positioned within the supply air flow path162to move the supply air from the supply air inlet158downstream to the supply air outlet160.

In the summer mode180, regeneration air in the form of return air flows through the return air inlet166and through a return air side153of the pre-processing module152. The pre-processing module152removes heat from the outside air in the supply air side151and transfers the heat to the return air in the return air side153. The return air is then channeled to a regeneration air heat exchanger164, which preferably is shut off. The return air travels through the regeneration air heat exchanger164unchanged and into a regeneration air heat exchanger165. In the summer mode180, the regeneration air heat exchanger165operates as a condenser coil to lower a relative humidity of the return air to increase the air's capacity to absorb water downstream. The regeneration air heat exchanger165uses the heat removed from the supply air by the supply air heat exchanger157to dry the return air. The heated return air then flows to a return air side159of the processing module154and receives moisture from the supply air side155. The return air discharged from the processing module154flows through a regeneration air heat exchanger167, which operates as a condenser coil to further heat the return air using the heat from the supply air heat exchanger156. The return air is then discharged through a return air outlet168. It is understood that heat exchangers in the supply and return air flow paths could be matched differently then that stated previously. For instance, the regeneration air heat exchanger165could also be coupled with the supply air heat exchanger156. Likewise the regeneration air heat exchanger167could also be coupled with the supply air heat exchanger157.

Referring toFIG. 11, the winter mode182of the system150is illustrated. The supply air flow path162follows the same path as defined in the summer mode180. In the winter mode182the function of the system components may differ from the function of the system components in the summer mode180. Supply air enters the supply air inlet158and flows downstream to the pre-processing module152where the supply air receives heat from the return air flow path190. The supply air discharged from the pre-processing module152flows into the supply air heat exchangers156and157. In the winter mode182, the supply air heat exchangers156and157operate as condenser coils to heat, lower a relative humidity of the supply air and increase the air's capacity to absorb water downstream. The dried supply air then travels to the processing module154where the supply air receives moisture from the return air flow path190to generate humidified supply air. The humidified supply air is discharged through the supply air outlet160and into the space.

The return air flow path190of the winter mode182differs from the return air flow path170of the summer mode180. The dampers171,172,173, and174of the system150are open and/or closed to change the return air flow path170of the summer mode180to the return air flow path190of the winter mode182. Additionally, the functions of at least some of the system components may change in the winter mode182. Return air enters the return air flow path190through the return air inlet166. The return air flows through the pre-processing module152where heat is removed from the return air. The heat is discharged into the supply air flow path162. The return air then flows to the processing module154where moisture is removed from the return air. The moisture from the return air is discharged into the supply air flow path162. The return air discharged from the processing module154travels to the regeneration air heat exchangers165and164. In the winter mode182, the regeneration air heat exchangers165and164operate as evaporator coils to cool the return air prior to the return air being discharged through the return air outlet192. It is understood that the return air flow path190of the winter mode could alternatively flow through the regeneration air heat exchanger167, which is preferably shut off, and then to the process module154depending on the damper (not shown) location and operation.

In one embodiment, the heat pump system150senses a condition of at least one of the supply air or return air from the space to control an output of at least one of the pre-processing module152, the processing module154, the supply air heat exchangers156and/or157, and/or the regeneration air heat exchangers164,165, and/or167to achieve a pre-determined dehumidification of the supply air in summer mode180and a pre-determined humidification of the supply air in the winter mode182.

In another embodiment, the heat pump system150senses a condition of at least one of the supply air or return air from the space to control an output of at least one of the pre-processing module152, the processing module154, the supply air heat exchangers156and/or157, and/or the regeneration air heat exchangers164,165, and/or167to achieve a pre-determined performance of the system150.

In another embodiment, the heat pump system150senses a condition of at least one of the supply air or return air from the space to and control an output of at least one of the pre-processing module152, the processing module154, the supply air heat exchangers156and/or157, and/or the regeneration air heat exchangers164,165, and/or167to limit frost formation in at least one of the pre-processing module152and/or regeneration air heat exchangers164,165, and/or167in the winter mode182.

In another embodiment, the heat pump system150senses a condition of at least one of the supply air stream or the return air stream from the space to control an output of at least one of a single compressor, multiple compressors and/or variable compressor to limit frost formation in at least one of the pre-processing module152and/or regeneration air heat exchangers164,165and/or167in the winter mode182.

In another embodiment, the heat pump system150senses a condition of at least one of the supply air stream or the return air stream from the space to control an output of at least one of a single compressor, multiple compressors and/or variable compressor to achieve a pre-determined performance of the system150.

Referring toFIGS. 10 and 11, the heat pump system150includes a first refrigerant system143and a second refrigerant system145. The first refrigerant system143includes piping147that fluidly couples the supply air heat exchanger156, the regeneration air heat exchanger164, and the regeneration air heat exchanger167. The first refrigerant system143pumps a refrigerant between the supply air heat exchanger156and at least one of the regeneration air heat exchanger164or the regeneration air heat exchanger167. A heat exchanger switch149controls the flow of refrigerant to the regeneration air heat exchanger164and the regeneration air heat exchanger167. In the summer mode180, the first refrigerant system143pumps cooled refrigerant to the supply air heat exchanger156to cool the air flowing through the supply air heat exchanger156. The cooled refrigerant is heated by the air in the supply air heat exchanger156to form heated refrigerant. The heated refrigerant flows through the piping147to at least one of the regeneration air heat exchanger164or the regeneration air heat exchanger167to heat the air flowing through the regeneration air heat exchanger164and/or the regeneration air heat exchanger167. The refrigerant is cooled by at least one of the regeneration air heat exchanger164or the regeneration air heat exchanger167to form cooled refrigerant that is pumped back to the supply air heat exchanger156.

In the winter mode182, the first refrigerant system143pumps heated refrigerant to the supply air heat exchanger156to heat the air flowing through the supply air heat exchanger156. The heated refrigerant is cooled by the air in the supply air heat exchanger156to faun cooled refrigerant. The cooled refrigerant flows through the piping147to at least one of the regeneration air heat exchanger164or the regeneration air heat exchanger167to cool the air flowing through the regeneration air heat exchanger164and/or the regeneration air heat exchanger167. The refrigerant is heated by the air in at least one of the regeneration air heat exchanger164or the regeneration air heat exchanger167to form heated refrigerant that is pumped back to the supply air heat exchanger156.

The first refrigerant system143may include a metering device and check valve system161to control a flow of the refrigerant between the supply air heat exchanger156and the regeneration air heat exchanger164and/or the regeneration air heat exchanger167. Additionally, a switch163may be provided to reverse a flow of the refrigerant through the first refrigerant system143. For example, the flow of the refrigerant may be reversed when the system150is switched between the summer mode180and the winter mode182. A compressor169is provided to compress the refrigerant. In the summer mode180, the refrigerant passes through the compressor169after exiting the supply air heat exchanger156and before entering the regeneration air heat exchangers164and/or167. In the winter mode182, the refrigerant passes through the compressor169after exiting the regeneration air heat exchangers164and/or167and before entering the supply air heat exchanger156.

The second refrigerant system145includes piping175that fluidly couples the supply air heat exchanger157and the regeneration air heat exchanger165. The second refrigerant system145pumps a refrigerant between the supply air heat exchanger157and the regeneration air heat exchanger165. In the summer mode180, the refrigerant system145pumps cooled refrigerant to the supply air heat exchanger157to cool the air flowing through the supply air heat exchanger157. The cooled refrigerant is heated by the air in the supply air heat exchanger157to form heated refrigerant. The heated refrigerant flows through the piping175to the regeneration air heat exchanger165to heat the air flowing through the regeneration air heat exchanger165. The refrigerant is cooled by the air in the regeneration air heat exchanger165to form cooled refrigerant that is pumped back to the supply air heat exchanger157.

In the winter mode182, the second refrigerant system145pumps heated refrigerant to the supply air heat exchanger157to heat the air flowing through the supply air heat exchanger157. The heated refrigerant is cooled by the air in the supply air heat exchanger157to form cooled refrigerant. The cooled refrigerant flows through the piping175to the regeneration air heat exchanger165to cool the air flowing through the regeneration air heat exchanger165. The refrigerant is heated by the air in the regeneration air heat exchanger165to form heated refrigerant that is pumped back to the supply air heat exchanger157.

The second refrigerant system145may include a metering device and check valve system177to control a flow of the refrigerant between the supply air heat exchanger157and the regeneration air heat exchanger165. Additionally, a switch179may be provided to reverse a flow of the refrigerant through the second refrigerant system145. For example, the flow of the refrigerant may be reversed when the system150is switched between the summer mode180and the winter mode182. A compressor181is provided to compress the refrigerant. In the summer mode180, the refrigerant passes through the compressor181after exiting the supply air heat exchanger157and before entering the regeneration air heat exchanger165. In the winter mode182, the refrigerant passes through the compressor181after exiting the regeneration air heat exchanger165and before entering the supply air heat exchanger157.

FIG. 12is a schematic view of another heat pump system600formed in accordance with an embodiment. The system600is capable of switching between a summer mode and a winter mode without the need to reconfigure the components of the system600.

The system600includes a supply air flow path602, a return air flow path604, and an outside air flow path606. The supply air flow path602travels between a supply air inlet608and a supply air outlet610. In one embodiment, the system600may include at least one fan to draw air into and move air through the supply air flow path602. Outside air flows through the supply air inlet608and through a pre-processing module612positioned downstream of the supply air inlet608.

The pre-processing module612includes a supply air side614and a regeneration air side616. The supply air side614is positioned within the supply air flow path602. The regeneration air side616is positioned within the return air flow path604. Outside air passes through the supply air side614of the pre-processing module612. The pre-processing module612is configured to transfer latent energy and sensible energy between the supply air flow path602and the return air flow path604. The latent energy includes moisture in the flow paths602and604. The pre-processing module612transfers heat from a warmer flow path to a cooler flow path. The pre-processing module612also transfers humidity from a high humidity flow path to a low humidity flow path. The outside air is cooled as the outside air passes through the pre-processing module612.

The cooled air from the pre-processing module612is discharged into a supply air heat exchanger618positioned downstream from the pre-processing module612. The supply air heat exchanger618discharges air into another supply air heat exchanger620positioned downstream from the supply air heat exchanger618. The supply air heat exchangers618and620operate as evaporator coils or cooling coils in the summer mode. As evaporator coils, the supply air heat exchangers618and620condition the cooled air and further remove heat from the cooled air to produce saturated air.

A processing module622is positioned downstream from the supply air heat exchangers618and620. The saturated air passes through the processing module622. The processing module622includes a supply air side624and an outside air side626. The supply air side624is positioned within the supply air flow path602and the outside air side626is positioned within the outside air flow path606. The saturated air passes through the supply air side624to remove moisture therefrom and produce conditioned supply air that has been further dehumidified. Because the air is first saturated by the supply air heat exchangers618and620, the efficiency of the processing module622is increased when dehumidifying the air. The dehumidified supply air flows downstream through the supply air outlet610and into the space.

Regeneration air in the form of return air leaves the space at a return air inlet628and traverses the return air flow path604. The return air flow path604is defined between the return air inlet628and a return air outlet630. In one embodiment, the system600may include at least one fan to draw air into and move air through the return air flow path604.

The regeneration air side616of the pre-processing module612is positioned downstream from the return air inlet628. The return air passes through the regeneration air side616of the pre-processing module612. The pre-processing module612transfers heat and moisture into the return air passing through the regeneration air side616, thereby removing heat from the supply air passing through the supply air side614. The heated air flows into a regeneration air heat exchanger632positioned downstream from the regeneration air side616of the pre-processing module612.

The regeneration air heat exchanger632operates as a condenser coil in the summer mode to heat and lower a relative humidity of the conditioned air. The regeneration air heat exchanger632is fluidly coupled to the supply air heat exchanger618by a refrigerant system634. The refrigerant system634pumps a refrigerant between the regeneration air heat exchanger632and the supply air heat exchanger618. The regeneration air heat exchanger632uses the heat from the supply air heat exchanger618to lower a relative humidity of the heated air thus increasing the air's capacity to absorb water downstream. In one embodiment, a compressor636may be provided in the refrigerant system634to condition the refrigerant flowing between the supply air heat exchanger618and the regeneration air heat exchanger632. The heated air from the regeneration air heat exchanger632is discharged from the return air outlet630.

Regeneration air in the form of outside air enters the system600at an outside air inlet638and traverses the outside air flow path606. The outside air flow path606is defined between the outside air inlet638and an outside air outlet640. In one embodiment, the system600may include at least one fan to draw air into and move air through the outside air flow path606. The outside air flows into a regeneration air heat exchanger642positioned downstream from the outside air inlet638.

The regeneration air heat exchanger642operates as a condenser coil in the summer mode to heat and lower a relative humidity of conditioned air. The regeneration air heat exchanger642is fluidly coupled to the supply air heat exchanger620by a refrigerant system644. The refrigerant system644pumps a refrigerant between the regeneration air heat exchanger642and the supply air heat exchanger620. The regeneration air heat exchanger642uses the heat from the supply air heat exchanger620to lower the relative humidity of the heated air thus increasing the air's capacity to absorb water downstream. In one embodiment, a compressor646may be provided in the refrigerant system644to condition the refrigerant flowing between the supply air heat exchanger620and the regeneration air heat exchanger642. The heated air from the regeneration air heat exchanger642is discharged into the outside air side626of the processing module622.

The processing module622transfers heat and moisture into the supply air passing through the supply air side624, thereby removing heat from the outside air passing through the outside air side626. The outside air is discharged from the processing module622through the outside air outlet640.

In a winter mode, the system600may be configured to heat and humidify the supply air flowing into the building. For example, the supply air heat exchangers618and620may be reversed in the winter mode to operate as condenser coils. Additionally, the regeneration air heat exchangers632and642may be reversed in the winter mode to operate as evaporator coils.

FIG. 13is a schematic view of an alternative embodiment of the heat pump system600. InFIG. 12the outside air flow path606is configured to flow in a counter-flow direction with respect to the supply air flow path602. InFIG. 13, the regeneration air heat exchanger642is positioned on an opposite side of the processing module622, in comparison toFIG. 12. Accordingly, the outside air flow path606illustrated inFIG. 13is reversed and flows parallel to the supply air flow path602. Parallel air flow of the outside air flow path606and the supply air flow path602may improve the transfer of heat and moisture between the outside air side626and the supply air side624of the processing module622.

FIG. 14is a schematic view of another alternative embodiment of the heat pump system600. The heat pump system600includes an additional heat source601positioned between the supply air heat exchanger620and the supply air side624of the processing module622. The additional heat source601is positioned downstream of the supply air heat exchanger620and upstream from the processing module622. In one embodiment, the additional heat source601may be located downstream of the processing module622. The additional heat source601may be a hot water coil, steam coil, electric heater, gas burner, or the like. The additional heat source601may be configured for operation in the winter mode. Accordingly, the additional heat source601may be shut-off in the summer mode so that the supply air passes through the additional heat source601unchanged. In one embodiment, the supply air may by-pass the additional heat source601in the summer mode and travel directly from the supply air heat exchanger620to the processing module624.

In the winter mode, the system600may have multiple modes of operation. In one embodiment, the system600may utilize the additional heat source601with the processing module622turned off and the pre-processing module612turned on to heat and humidify the supply air passing therethrough. In such an embodiment, the supply air heat exchanger618and620may also be shut off so that only the additional heating source601would provide heat after the pre-processing module612.

In another embodiment, the additional heat source601may be operated with either one or both of the supply air heat exchangers618and620. In such an embodiment, the supply air heat exchangers618and620are operated as condensers to heat the supply air in the supply air flow path602. Additionally, either one or both of the regeneration air heat exchangers632and642operate as evaporators to cool the air in the return air flow path604and the outside air flow path606, respectively. In such an embodiment, the processing module622may be operated. Accordingly, supply air leaving the supply air heat exchanger620could be heated further by the additional heating source601before entering the processing module622where the supply air is humidified. The outside air flow path606is then heated and dehumidified as it passes through the processing module622.

FIG. 15is a schematic view of another alternative embodiment of the heat pump system600. The heat pump system600includes the additional heat source601(as illustrated inFIG. 14) and a pair of pre-heat coils603and605. The pre-heat coil603is positioned in the return air flow path604between the regeneration air heat exchanger632and the pre-processing module612. The pre-heat coil603is positioned downstream from the regeneration air side616of the pre-processing module612and upstream from the regeneration air heat exchanger632. The pre-heat coil605is positioned in the outside air flow path606upstream of the regeneration air heat exchanger642and the processing module622. The pre-heat coils603and605may be hot water coils, steam coils, electric heaters, gas burners, heat exchangers tied to the refrigeration system or the like.

In the winter mode, the supply air in the supply air flow path602is heated and humidified by the pre-processing module612and then heated by supply air heat exchangers618and620. The supply air may also be heated by the additional heat source601prior to being cooled and humidified by the processing module622. The return air in the return air flow path604is cooled and dehumidified by the pre-processing module612. The return air is then pre-heated by the pre-heat coil603and cooled by the regeneration air heat exchanger632. The outside air in the outside air flow path606is pre-heated by the pre-heat coil605and then cooled by the regeneration air heat exchanger642. The outside air is then reheated and dehumidified by the processing module622.

The pre-heat coil603offsets a saturation point of the return air stream so that heat absorbed by the pre-processing wheel and transferred to the return air stream is recaptured by the regeneration air heat exchanger632without energy being lost. Optionally, a supply pre-heating coil (not shown) may be located upstream of the pre-processing module612.

FIG. 16is a schematic view of another heat pump system700formed in accordance with an embodiment capable of operating in a summer mode or a winter mode.

The system700includes a supply air flow path702, a return air flow path704, a first outside air flow path706, and a second outside air flow path701. The supply air flow path702travels between a supply air inlet708and a supply air outlet710. Outside air flows through the supply air inlet708and through a pre-processing module712positioned downstream of the supply air inlet708. The pre-processing module712includes a supply air side714positioned within the supply air flow path702. Outside air passes through the supply air side714of the pre-processing module712. The pre-processing module712is configured to transfer latent energy and sensible energy between the supply air flow path702and the return air flow path704. The supply air is cooled as the supply air passes through the pre-processing module712.

The cooled air from the pre-processing module712is discharged into a supply air heat exchanger718positioned downstream from the pre-processing module712. The supply air heat exchanger718discharges air into a second supply air heat exchanger719positioned downstream from the supply air heat exchanger718. The supply air heat exchanger719discharges air into a third supply air heat exchanger720positioned downstream from the supply air heat exchanger719. The supply air heat exchangers718,719, and720operate as evaporator coils or cooling coils in the summer mode.

A processing module722is positioned downstream from the supply air heat exchangers718,719, and720. The air passes through the processing module722. The processing module722includes a supply air side724positioned within the supply air flow path702. The air passes through the supply air side724to remove moisture therefrom and produce conditioned supply air that has been dehumidified. The dehumidified supply air flows downstream through the supply air outlet710and into the space.

Regeneration air in the form of return air leaves the space at return air inlet728and traverses the return air flow path704. The return air flow path704is defined between the return air inlet728and a return air outlet730. A return air side716of the pre-processing module712is positioned downstream from the return air inlet728. The return air passes through the return air side716of the pre-processing module712. The pre-processing module712transfers heat and moisture into the return air passing through the return air side716, thereby removing heat from the supply air passing through the supply air side714. The heated air flows into a regeneration air heat exchanger732positioned downstream from the return air side716of the pre-processing module712.

The regeneration air heat exchanger732operates as a condenser coil in the summer mode to heat and lower a relative humidity of conditioned air. The regeneration air heat exchanger732is fluidly coupled to the supply air heat exchanger719by a refrigerant system734. The refrigerant system734pumps a refrigerant between the regeneration air heat exchanger732and the supply air heat exchanger719. In one embodiment, a compressor736may be provided in the refrigerant system734to condition the refrigerant flowing between the supply air heat exchanger719and the regeneration air heat exchanger732. The heated air from the regeneration air heat exchanger732is discharged from the return air outlet730.

Regeneration air in the form of outside air enters the system700at an outside air inlet738and traverses the outside air flow path706. The outside air flow path706is defined between the outside air inlet738and an outside air outlet740. The outside air flows into a regeneration air heat exchanger742positioned downstream from the outside air inlet738. The regeneration air heat exchanger742operates as a condenser coil in the summer mode to heat and lower relative humidity of conditioned air. The regeneration air heat exchanger742is fluidly coupled to the supply air heat exchanger720by a refrigerant system744. The refrigerant system744pumps a refrigerant between the regeneration air heat exchanger742and the supply air heat exchanger720. In one embodiment, a compressor746may be provided in the refrigerant system744to condition the refrigerant flowing between the supply air heat exchanger720and the regeneration air heat exchanger742. The heated air from the regeneration air heat exchanger742is discharged into an outside air side726of the processing module722.

The processing module722transfers heat and moisture into the supply air passing through the supply air side724, thereby removing heat from the outside air passing through the outside air side726. The outside air is discharged from the processing module722through the outside air outlet740.

Regeneration air in the form of outside air enters the system700at an outside air inlet703and traverses the outside air flow path701. The outside air flow path701is defined between the outside air inlet703and an outside air outlet705. The outside air flows into a regeneration air heat exchanger707positioned downstream from the outside air inlet703.

The regeneration air heat exchanger707operates as a condenser coil in the summer mode to heat and lower relative humidity of conditioned air. The regeneration air heat exchanger707is fluidly coupled to the supply air heat exchanger718by a refrigerant system709. The regeneration air heat exchanger707extracts the heat from the supply air heat exchanger718. In one embodiment, a compressor711may be provided in the refrigerant system709to condition the refrigerant flowing between the supply air heat exchanger718and the regeneration air heat exchanger707. The heated air from the regeneration air heat exchanger707is discharged through the outside side air outlet705.

In a winter mode, the system700may be configured to humidify the supply air flowing into the building. For example, the supply air heat exchangers718,719, and720may be reversed in the winter mode to operate as condenser coils. Additionally, the regeneration air heat exchangers707,732and742may be reversed in the winter mode to operate as evaporator coils.

FIG. 17is a schematic view of an alternative embodiment of the heat pump system700. InFIG. 16, the outside air flow path706is configured to flow in a counter-flow direction with respect to the supply air flow path702. InFIG. 17, the regeneration air heat exchanger742is positioned on an opposite side of the processing module722, in comparison toFIG. 16. Accordingly, the outside air flow path706illustrated inFIG. 17is reversed and flows parallel to the supply air flow path702. Parallel air flow of the outside air flow path706and the supply air flow path702may improve the transfer of heat and moisture between the outside air side726and the supply air side724of the processing module722.

FIG. 18is a schematic view of another heat pump system800formed in accordance with an embodiment that operates in a summer mode or a winter mode. The system800includes a supply air flow path802, a return air flow path804, a first outside air flow path806, a second outside air flow path801, and third outside air flow path821. The supply air flow path802travels between a supply air inlet808and a supply air outlet810. Outside air flows through the supply air inlet808and through a pre-processing module812positioned downstream of the supply air inlet808.

The outside air passes through a supply air side814of the pre-processing module812. The supply air is cooled as the supply air passes through the pre-processing module812. The cooled air from the pre-processing module812is discharged into a supply air heat exchanger818positioned downstream from the pre-processing module812. The supply air heat exchanger818discharges air into a second supply air heat exchanger819positioned downstream from the supply air heat exchanger818. The supply air heat exchanger819discharges air into a third supply air heat exchanger820positioned downstream from the supply air heat exchanger819. The supply air heat exchangers818,819, and820operate as evaporator coils or cooling coils in the summer mode.

A processing module822is positioned downstream from the supply air heat exchangers818,819, and820. The saturated air passes through a supply air side824of the processing module822that is positioned within the supply air flow path802. The air passes through the supply air side824to remove moisture therefrom and produce conditioned supply air that has been further dehumidified. The dehumidified supply air flows downstream through the supply air outlet810and into the space.

Regeneration air in the form of return air leaves the space at return air inlet828and traverses the return air flow path804defined between the return air inlet828and a return air outlet830. The return air passes through a return air side816of the pre-processing module812. The pre-processing module812transfers heat and moisture into the return air passing through the return air side816, thereby removing heat from the supply air passing through the supply air side814. The heated air is discharged from the return air outlet830.

Regeneration air in the form of outside air enters the system800at an outside air inlet838and traverses the outside air flow path806that is defined between the outside air inlet838and an outside air outlet840. The outside air flows into a regeneration air heat exchanger842positioned downstream from the outside air inlet838. The regeneration air heat exchanger842operates as a condenser coil in the summer mode to heat and lower relative humidity of conditioned air. The regeneration air heat exchanger842is fluidly coupled to the supply air heat exchanger820by a refrigerant system844. In one embodiment, a compressor846may be provided in the refrigerant system844to condition the refrigerant flowing between the supply air heat exchanger820and the regeneration air heat exchanger842. The heated air from the regeneration air heat exchanger842is discharged into the outside air side826of the processing module822.

The processing module822transfers heat and moisture into the supply air passing through the supply air side824, thereby removing heat from the outside air passing through the outside air side826. The outside air is discharged from the processing module822through the outside air outlet840.

Regeneration air in the form of outside air enters the system800at an outside air inlet803and traverses the outside air flow path801defined between the outside air inlet803and an outside air outlet805. The outside air flows into a regeneration air heat exchanger807positioned downstream from the outside air inlet803. The regeneration air heat exchanger807operates as a condenser coil in the summer mode. The regeneration air heat exchanger807is fluidly coupled to the supply air heat exchanger818by a refrigerant system809. The refrigerant system809pumps a refrigerant between the regeneration air heat exchanger807and the supply air heat exchanger818. In one embodiment, a compressor811may be provided in the refrigerant system809to condition the refrigerant flowing between the supply air heat exchanger818and the regeneration air heat exchanger807. The heated air from the regeneration air heat exchanger807is discharged through the outside side air outlet805.

Regeneration air in the form of outside air enters the system800at an outside air inlet823and traverses the outside air flow path821defined between the outside air inlet823and the outside air outlet805. The outside air flows into a regeneration air heat exchanger825positioned downstream from the outside air inlet823.

The regeneration air heat exchanger825operates as a condenser coil in the summer mode to heat and lower relative humidity of conditioned air. The regeneration air heat exchanger825is fluidly coupled to the supply air heat exchanger819by a refrigerant system827. In one embodiment, a compressor829may be provided in the refrigerant system827to condition the refrigerant flowing between the supply air heat exchanger819and the regeneration air heat exchanger825. The heated air from the regeneration air heat exchanger825is discharged through the outside side air outlet805.

In a winter mode, the system800may be configured to humidify the supply air flowing into the building. For example, the supply air heat exchangers818,819, and820may be reversed in the winter mode to operate as condenser coils. Additionally, the regeneration air heat exchangers807,825and842may be reversed in the winter mode to operate as evaporator coils.

FIG. 19is a schematic view of an alternative embodiment of the heat pump system800. InFIG. 18, the outside air flow path806is configured to flow in a counter-flow direction with respect to the supply air flow path802. InFIG. 19, the regeneration air heat exchanger842is positioned on an opposite side of the processing module822, in comparison toFIG. 18. Accordingly, the outside air flow path806illustrated inFIG. 19is reversed and flows parallel to the supply air flow path802. Parallel air flow of the outside air flow path806and the supply air flow path802may improve the transfer of heat and moisture between the outside air side826and the supply air side824of the processing module822.

FIG. 20is a schematic view of another heat pump system900formed in accordance with an embodiment. The system900includes a supply air flow path902, a first outside air flow path906, a second outside air flow path901, and third outside air flow path921. The supply air flow path902includes return air939that enters the supply air flow path902through a return air inlet908. A portion931of the return air is discharged through a return air outlet930as exhaust air. Another portion933of the return air enters a mixing box935. The supply air flow path902also includes outside air941that enters an outside air inlet937and mixes with the portion933of the return air to form the supply air.

The supply air flows into a supply air heat exchanger918. The supply air heat exchanger918discharges air into a second supply air heat exchanger919positioned downstream from the supply air heat exchanger918. The supply air heat exchanger919discharges air into a third supply air heat exchanger920positioned downstream from the supply air heat exchanger919. The supply air heat exchangers918,919, and920operate as evaporator coils or cooling coils in the summer mode. The air passes through a supply air side924of the processing module922and then flows downstream through a supply air outlet910and into the space.

Regeneration air in the form of outside air enters the system900at an outside air inlet938and traverses the outside air flow path906that is defined between the outside air inlet938and an outside air outlet940. The outside air flows into a regeneration air heat exchanger942positioned downstream from the outside air inlet938.

The regeneration air heat exchanger942operates as a condenser coil in the summer mode. The regeneration air heat exchanger942is fluidly coupled to the supply air heat exchanger920by a refrigerant system944. In one embodiment, a compressor946may be provided in the refrigerant system944to condition the refrigerant flowing between the supply air heat exchanger920and the regeneration air heat exchanger942. The heated air from the regeneration air heat exchanger942is discharged into an outside air side926of the processing module922.

The processing module922transfers heat and moisture into the supply air passing through the supply air side924, thereby removing heat from the outside air passing through the outside air side926. The outside air is discharged from the processing module922through the outside air outlet940.

Regeneration air in the form of outside air enters the system900at an outside air inlet903and traverses the outside air flow path901defined between the outside air inlet903and an outside air outlet905. The outside air flows into a regeneration air heat exchanger907positioned downstream from the outside air inlet903.

The regeneration air heat exchanger907operates as a condenser coil in the summer mode. The regeneration air heat exchanger907is fluidly coupled to the supply air heat exchanger918by a refrigerant system909having a compressor911to condition the refrigerant flowing between the supply air heat exchanger918and the regeneration air heat exchanger907. The heated air from the regeneration air heat exchanger907is discharged through the outside side air outlet905.

Regeneration air in the form of outside air enters the system900at an outside air inlet923and traverses the outside air flow path921defined between the outside air inlet923and the outside air outlet905. The outside air flows into a regeneration air heat exchanger925positioned downstream from the outside air inlet923and fluidly coupled to the supply air heat exchanger919by a refrigerant system927having a compressor929. The heated air from the regeneration air heat exchanger925is discharged through the outside side air outlet905.

In a winter mode, the system900may be configured to humidify the supply air flowing into the building. For example, the supply air heat exchangers918,919, and920may be reversed in the winter mode to operate as condenser coils. Additionally, the regeneration air heat exchangers907,925and942may be reversed in the winter mode to operate as evaporator coils.

FIG. 21is a schematic view of an alternative embodiment of the heat pump system900. InFIG. 20, the outside air flow path906is configured to flow in a counter-flow direction with respect to the supply air flow path902. InFIG. 21, the regeneration air heat exchanger942is positioned on an opposite side of the processing module922, in comparison toFIG. 20. Accordingly, the outside air flow path906illustrated inFIG. 21is reversed and flows parallel to the supply air flow path902. Parallel air flow of the outside air flow path906and the supply air flow path902may improve the transfer of heat and moisture between the outside air side926and the supply air side924of the processing module922.

FIG. 22is a schematic view of another heat pump system1000formed in accordance with an embodiment. The system1000includes a supply air flow path1002, a first outside air flow path1006, a second outside air flow path1001, and third outside air flow path1021. The supply air flow path1002includes return air1039that enters the supply air flow path1002through a return air inlet1008. A portion1031of the return air is discharged through a return air outlet1030as exhaust air. Another portion1033of the return air enters a mixing box1035. The supply air flow path1002also includes outside air1041that enters an outside air inlet1037and mixes with the portion1033of the return air to form the supply air.

The supply air flows into a supply air heat exchanger1018. The supply air heat exchanger1018discharges air into a second supply air heat exchanger1019positioned downstream from the supply air heat exchanger1018. The supply air heat exchanger1019discharges air into a third supply air heat exchanger1020positioned downstream from the supply air heat exchanger1019. The supply air heat exchangers1018,1019, and1020operate as evaporator coils or cooling coils in the summer mode. The air passes through a supply air side1024of the processing module1022and then flows downstream to a fourth supply air heat exchanger1080. The supply air heat exchanger1080also operates as evaporator coils or cooling coils in the summer mode. The air passes from the supply air heat exchanger1080to a reheat coil1060that reheats the supply air during the winter mode.

Regeneration air in the form of outside air enters the system1000at an outside air inlet1038and traverses the outside air flow path1006that is defined between the outside air inlet1038and an outside air outlet1040. The outside air flows into a regeneration pre-reheat coil1062positioned downstream from the outside air inlet1038. The air leaving the regeneration pre-reheat coil1062then passes into a regeneration air heat exchanger1042positioned downstream from the regeneration pre-reheat coil1062.

The regeneration air heat exchanger1042operates as a condenser coil in the summer mode. The regeneration air heat exchanger1042is fluidly coupled to the supply air heat exchanger1020and the supply air heat exchanger1080by a refrigerant system1044. In one embodiment, a compressor1046may be provided in the refrigerant system1044to condition the refrigerant flowing between the supply air heat exchangers1020and1080, and the regeneration air heat exchanger1042. The heated air from the regeneration air heat exchanger1042is discharged into an outside air side1026of the processing module1022.

The refrigerant system1044includes a node branch1068located downstream, along the fluid flow path, from the compressor1046. At the node branch1068, the fluid path splits along parallel refrigerant branches1064and1066. The refrigerant branch1064extends to and from the heat exchanger1020that is located upstream of the process module1022, while the refrigerant branch1066extends to and from the heat exchanger1080that is located downstream of the process module1022. Valves1074and1076are located along the branches1064and1066, respectively, to permit and inhibit flow of the coolant fluid through one or both of the branches1064and1066. The outlets of the valves1074and1076merge again at node1078and re-circulate to the heat exchanger1042. The valves1074and1076may be automatically controlled by a controller module. The valves1074and1076may be adjusted between fully open, fully closed, partially open and partially closed positions to vary the amount of coolant fluid that flows along each of the branches1064and1066. The valves1074and1076may be adjusted based upon summer versus winter mode.

The processing module1022transfers heat and moisture into the supply air passing through the supply air side1024, thereby removing heat from the outside air passing through the outside air side1026. The outside air is discharged from the processing module1022through the outside air outlet1040.

Regeneration air in the form of outside air enters the system1000at an outside air inlet1003and traverses the outside air flow path1001defined between the outside air inlet1003and an outside air outlet1005. The outside air flows into a regeneration air heat exchanger1007positioned downstream from the outside air inlet1003.

The regeneration air heat exchanger1007operates as a condenser coil in the summer mode. The regeneration air heat exchanger1007is fluidly coupled to the supply air heat exchanger1018by a refrigerant system1009having a compressor1011to condition the refrigerant flowing between the supply air heat exchanger1018and the regeneration air heat exchanger1007. The heated air from the regeneration air heat exchanger1007is discharged through the outside side air outlet1005.

Regeneration air in the form of outside air enters the system1000at an outside air inlet1023and traverses the outside air flow path1021defined between the outside air inlet1023and the outside air outlet1005. The outside air flows into a regeneration air heat exchanger1025positioned downstream from the outside air inlet1023and fluidly coupled to the supply air heat exchanger1019by a refrigerant system1027having a compressor1029. The heated air from the regeneration air heat exchanger1025is discharged through the outside side air outlet1005.

In a winter mode, the system1000may be configured to humidify the supply air flowing into the building. For example, the supply air heat exchangers1018,1019,1020and1080may be reversed in the winter mode to operate as condenser coils. Additionally, the regeneration air heat exchangers1007,1025and1042may be reversed in the winter mode to operate as evaporator coils.

FIGS. 23-30illustrates psychrometric charts for the system1000when operating in various configurations.FIGS. 23-30illustrate exemplary data points representative of the air condition when passing between designated regions within system1000.FIG. 23illustrates the system1000when using 100% return air as the entering air while configured to perform pre-cooling with postdehumidification and sensible cooling. In this configuration, the outside air inlet1037is closed such that return air through return air inlet1008provides all of the supply air. The supply air heat exchangers1018and1019are turned off and only the supply air heat exchanger1020is active.FIG. 23illustrates outside air at data point2301with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 74° F. and a relative humidity of approximately 78%.FIG. 23also illustrates return air at data point2302with a dry bulb temperature of 65° F., a wet bulb temperature of approximately 52° F. and a relative humidity of approximately 40%. As the air passes through the supply air heat exchanger1020, the humidity and temperature of the return air is changed to data point2303, and as the air passes through the processing module1022, the air conditions are adjusted to data point2304(dry bulb temperature of 65° F., wet bulb temperature of 50° F. and 31% relative humidity). As the air passes through the supply air heat exchanger1080, the conditions are further changed to data point2305and supplied to the controlled space (dry bulb temperature of 52° F., wet bulb temperature of 44° F. and relative humidity 50%). The heat exchanger1080performs post-dehumidification sensible cooling only without changing the humidity of the supply air.

FIG. 24illustrates a psychrometric chart for the system1000when operating with 100% return air as the entering supply air. In this configuration, the outside air inlet1037is closed such that return air through return air inlet1008provides all of the supply air. The supply air heat exchangers1018and1019are turned off and only the supply air heat exchanger1020is active. The supply air heat exchanger1020changes the supply air condition from the data point2402(dry bulb temperature of 65° F., wet bulb temperature of 52° F. relative humidity 40%) to the conditions at data point2403(dry bulb temperature of 46° F., wet bulb temperature of 43° F. relative humidity 80%). Next as the air passes downstream from the heat exchanger1020through the processing module1022, the conditions of the supply air are moved from data point2403to the conditions at data point2404(dry bulb temperature of 60° F., wet bulb temperature of 47° F. and relative humidity approximately 36%). There is no post-dehumidification sensible cooling.

FIG. 25illustrates a psychrometric chart for the system1000when operating in the summer mode with 50% return air and 50% outside air combined as the entering air at the mixing box1035. The psychrometric chart ofFIG. 25is representative of the supply air processing when the system1000performs pre-cooling with post-dehumidification and sensible cooling. As shown inFIG. 25, the outside air conditions may begin at data point2501(dry bulb temperature of 80° F., wet bulb temperature of 74° F. and relative humidity of 78%), while the return air begins with the conditions at data point2502(dry bulb temperature of 65° F., wet bulb temperature of 52° F. and relative humidity of 40%). When the outside air and return air are mixed at the mixing box1035, the air conditions are representative of data point2503(dry bulb temperature of 72° F., wet bulb temperature of 64° F. and relative humidity of 67%). In the example ofFIG. 25, the system1000operates supply air heat exchanges1019and1020, as well as heat exchanger1080. The air passing from the mixing box1035is conditioned by the heat exchanger1019to change the conditions of the air to data point2504(dry bulb temperature of 57° F., wet bulb temperature of 57° F. and approximately 100% relative humidity, mainly at saturation), as the air exits downstream of the heat exchanger1019. The heat exchanger1020then further processes the supply air to the conditions denoted at data point2505(dry bulb temperature of 46° F., wet bulb temperature of 46° F. and 100% relative humidity, mainly at saturation). The air exiting the heat exchanger1020passes through the processing module1022and is conditioned to the state denoted at data point2506when discharged from the processing module1022(dry bulb temperature of 59° F., wet bulb temperature of 47° F. and relative humidity of 37%). Next, the air on the discharge side of the processing module1022passes through the heat exchanger1080and its condition is changed to the state denoted at data point2507(dry bulb temperature of 53° F., wet bulb temperature of 44° F. and relative humidity 44%). The heat exchanger1080performs post-dehumidification sensible cooling.

FIG. 26illustrates a psychrometric chart for the operation of the system1000when utilizing 100% return air as the entering air and without using any pre-cooling from any of heat exchangers1018,1019and1020, but while using post-dehumidification sensible cooling at heat exchanger1080. The outside air conditions are the same as denoted in previous examples at data point2601, while the return air conditions are as denoted at data point2602. The supply air with the conditions of data point2602are passed through the processing module1022and adjusted to the state denoted at data point2603(dry bulb temperature of 72° F., wet bulb temperature of 54° F. and relative humidity 28%). Next the supply air at the discharge side of the processing module1022passes through the heat exchanger1080at which post-dehumidification sensible cooling is performed to reduce the state of the supply air to the point denoted at data point2604(dry bulb temperature of 60° F., wet bulb temperature of 49° F. and relative humidity 42%).

FIG. 27illustrates a psychrometric chart for the operation of the system1000when utilizing 100% outside air and no return air at entering air. The psychrometric chart ofFIG. 27reflects the operation of the system1000when performing pre-cooling at each of heat exchangers1018,1019and1020, and while performing post-dehumidification sensible cooling at heat exchanger1080. Beginning at data point2701, the conditions of the entering air are changed at heat exchangers1018,1019and1020as denoted at data point2702,2703and2704, respectively. The air conditions at the discharge side of heat exchanger1020(as denoted at data point2704) are at a humidity saturation point (e.g. 100% relative humidity). The air discharged from heat exchanger1020then passes through the processing module1022where the condition of the air is changed to the conditions at data point2705(60° F. dry bulb temperature, 47° F. wet bulb temperature and 38% relative humidity). The air discharged from the processing module1022then passes through the heat exchanger1080at which post-dehumidification sensible cooling is performed to change the conditions of the air to the conditions state denoted at data point2706(dry bulb temperature of 54° F., wet bulb temperature of 44° F. and relative humidity 42%).

FIG. 28illustrates a psychrometric chart of the operation of the processing module1000when using 100% outside air and no return air at the entering air. The psychrometric chart ofFIG. 28illustrates the configuration of the system1000when each of heat exchangers1018,1019and1020are operated, but while heat exchanger1080is turned off and does not perform any post-dehumidification sensible cooling. As shown inFIG. 28, the outside air conditions begin at data point2801and are changed to correspond to data point2802,2803and2804when passing through each of the heat exchangers1018,1019and1020, respectively. The conditions at the downstream side of the heat exchanger1020(data point2804) have a dry bulb temperature of 46° F., wet bulb temperature of 46° F. and is saturated along the moisture saturation line. As the air passes through the processing module1022, the conditions of the air are changed to the state denoted at data point2805(dry bulb temperature of 59° F., wet bulb temperature of 47° F. and relative humidity of 37%). The air conditions at the discharge side of the processing module1022remain steady as the air is passed into the conditioned space without any further post-dehumidification sensible cooling.

FIG. 29illustrates a configuration in which the system1000utilizes 100% return air as the entering air with no outside air being introduced. InFIG. 29, the system1000is configured to perform pre-cooling, only utilizing the heat exchanger1020, while the heat exchangers1018and1019are turned off. The system1000is also configured in the example ofFIG. 29to perform post-dehumidification sensible cooling at heat exchanger1080. As shown inFIG. 29the entering air beings at the conditions denoted at data point2901corresponding to the conditions of return air. As the entering air passes through the heat exchanger1020, the conditions are changed to the state denoted at data point2902(dry bulb temperature of 47° F., wet bulb temperature of 43° F. and relative humidity 80%). As the air passes from the heat exchanger in1020through the processing module1022, the conditions of the air are changed to the state denoted at data point2903(dry bulb temperature of 60° F., wet bulb temperature of 47° F. and relative humidity 27%). As the air passes from the discharge side of the processing module at1022through the heat exchanger1080, the conditions of the air are changed to the state denoted at data point2904(dry bulb temperature of 54° F., wet bulb temperature of 44° F. and relative humidity 43%).

FIG. 30illustrates a psychrometric chart for the operation of the system1000when utilizing 50% outside air and 50% return air as the entering air at the mixing box1035. Once the desired portions of outside and return air are mixed at the mixing box, the mixed air has the conditions denoted at data point3001(dry bulb temperature of 73° F., wet bulb temperature of 64° F. and relative humidity 67%). In the example ofFIG. 30, the system1000utilizes the heat exchangers1019and1020to perform pre-cooling and turns off the heat exchanger1080to perform no post-dehumidification sensible cooling (e.g. without post-dehumidification sensible cooling). The entering air is adjusted from the conditions at data point3001to the conditions denoted at data point3002and then3003as the entering air passes through the heat exchanger1019and then1020, respectively. The air discharged from the heat exchanger1020has a dry bulb temperature of 47° F. and has a saturation moisture content. As the air passes from the heat exchanger1020through the pre-processor1022, the conditions of the air are adjusted to the state at3004(dry bulb temperature of 59° F., wet bulb temperature of 47° F. and relative humidity 38%).

The embodiments described herein utilize a pre-processing module in both summer and winter modes for energy recovery. The embodiments further utilize a processing module for both dehumidification in the summer mode and humidification in the winter mode. Additionally, in the winter mode the processing module dehumidifies the return air, by reduction of grains in moisture and an increase in sensible dry bulb temperature, prior to the return air entering the cooling coil in the air source heat pump. The return air is first dehumidified by entering the pre-processing module, where the source air is heated and humidified. The return air is further dehumidified prior to entering the evaporator coil by the processing module. Additionally, as the return air is dehumidified by the processing module, the dry bulb temperature of the return air is increased which increases the efficiency of the heat pump. The evaporator can then run at lower temperatures without freezing the evaporator fins. In winter mode the energy in the return air is used in the reverse air source heat pump cycle.

Additionally, in the embodiments described herein, supply air is humidified by both the pre-processing module and the processing module to reduce humidification load requirements and energy consumption for the buildings in the winter mode. The embodiments also provide an efficient air source heat pump for winter heating in lieu of electric, gas, HW, or stream. The return air also provides stable and optimum regenerative air temperatures and conditions for the processing module reactivation in the summer mode.

FIG. 31is a schematic view of another heat pump system1100formed in accordance with an embodiment. The system1100is configured to condition supply air flowing into a building or space and return air channeled from within the building or space. When in the summer, among other things, the system1100dehumidifies the supply air flowing into the building. When in the winter mode, among other things, the system humidifies the supply air flowing into the building. The system1100is capable of switching between the summer mode and the winter mode without the need to reconfigure the components of the system1100. The system includes a supply air flow path1102and a regeneration air flow path1106. The supply air flow path1102includes return air flow path1139that enters the supply air flow path1102through a return air inlet1108. A portion1131of the return air may be discharged through a return air outlet1130as exhaust air. Another portion1133of the return air enters a mixing box1135. The supply air flow path1102also includes outside air1141that enters an outside air inlet1137and mixes with the portion1133of the return air to form the supply air.

The supply air flows into a supply air heat exchanger1120. The supply air heat exchanger1120operates as an evaporator coil or cooling coil in the summer mode. As an evaporator coil, the supply air heat exchanger1120conditions the air and removes heat from the air to produce saturated air that is discharged into a conditioned air region1111. A processing module1122is positioned downstream from the conditioned air region1111. The saturated air passes through a supply air side1124of the processing module1122to remove moisture there from and produce supply air that has been further dehumidified and heated. Because the air is first saturated by the supply air heat exchanger1120, the efficiency of the processing module1122is increased when dehumidifying the air. The dehumidified supply air then flows downstream into a processed air region1129. The supply air heat exchanger1180also operates as an evaporator coil or cooling coil in the summer mode. From the processed air region1129, the dehumidified supply air flows through the second supply air heat exchanger1180that further conditions the air and removes heat from the air to produce conditioned supply air. The conditioned air passes from the supply air heat exchanger1180to the supply air outlet1160and into the space.

Regeneration air flow path1106includes return air flow path1139that enters the regeneration air flow path1106through a return air inlet1108. A portion1131of the return air may be discharged through a return air outlet1130as exhaust air. Another portion1133of the return air enters a mixing box1185. The regeneration air flow path1106also includes outside air1186that enters an outside air inlet1103and mixes with the portion1133of the return air to form the regeneration air.

The regeneration air flows into a regeneration air heat exchanger1142. The regeneration air heat exchanger1142operates as a condenser coil in the summer mode to heat and lower a relative humidity of the air. The heat exchanger1142uses the heat from the supply air heat exchangers1120and1180to lower the relative humidity of regeneration air thus increasing the air's capacity to absorb water downstream. The heated air flows into a conditioned air region1112. The lowered relative humidity air in the conditioned air region1112is channeled downstream to the regeneration air side1126of the processing module1122. The lowered relative humidity air passing through the regeneration air side1126of the processing module1122regenerates the processing module1122by receiving moisture from the saturated air in the supply air side1124and adding humidity to the regeneration air that flows into a processed air region1113. The regeneration air flows from the processed air region1113to the second regeneration air heat exchanger1162. The second regeneration air heat exchanger1162operates as a very efficient condenser coil in the summer mode to dissipate heat from the refrigeration system1144in which heat was absorbed by the supply heat exchangers1120and1180. The regeneration air passes from the regeneration air heat exchanger1162into a processed air region1114. The regeneration air flows from the processed air region1114to the regeneration air outlet1105. The regeneration air heat exchangers1142and1162are fluidly coupled to the supply air heat exchangers1120and1180by a refrigerant system1144. In one embodiment, a compressor1146may be provided in the refrigerant system1144to condition the refrigerant flowing between the supply air heat exchangers1120and1180, and the regeneration air heat exchangers1142and1162.

The refrigerant system1144includes a node branch1191located downstream, along the fluid flow path, from the compressor1146. At the node branch1191, the fluid path splits along parallel refrigerant branches1195and1196. The refrigerant branch1195extends to and from the heat exchanger1162that is located downstream of the process module1122in the regeneration air stream, while the refrigerant branch1196extends to and from the heat exchanger1142that is located upstream of the process module1122in the regeneration air stream. Valves1190and1192permit and inhibit flow of the coolant fluid through one or both of the branches1195and1196. The outlet of the valve1192merges at node1193along branch1197. Branch1197includes a metering device and check valve system1194to control a flow of the refrigerant between the supply air heat exchangers1120and1180and the regeneration air heat exchangers1142and1162. At the node branch1178, the fluid path splits again along parallel refrigerant branches1164and1166. The refrigerant branch1164extends to and from the heat exchanger1120that is located upstream of the process module1122in the supply air stream, while the refrigerant branch1166extends to and from the heat exchanger1180that is located downstream of the process module1122in the supply air stream. Valves1176and1174permit and inhibit flow of the coolant fluid through one or both of the branches1164and1166. The outlet of the valve1174merges at node1168along branch1198. Branch1198includes a switch1199to permit reversing the flow of the refrigerant through the refrigerant system1144. For example, the flow of the refrigerant may be reversed between the summer mode and the winter mode. The valves1174,1176,1190and1192may be automatically controlled by a controller module. The valves1174,1176,1190and1192may be adjusted between fully open, fully closed, partially open and partially closed positions to vary the amount of coolant fluid that flows along each of the branches1164,1166,1195and1196. The valves1174,1176,1190and1192may be adjusted independently one from the other based upon summer versus winter mode.

The heat pump system1100includes a refrigerant system1144which includes a series of pipes, branches, metering devices, check valves and switching device that fluidly couples the supply air heat exchanger1120, the supply air heat exchanger1180, the regeneration air heat exchanger1142and the regeneration air heat exchanger1162. The refrigerant system1144pumps a refrigerant between at least one of the supply air heat exchanger1120or the supply air exchanger1180and at least one of the regeneration air heat exchanger1142or the regeneration air heat exchanger1162. Alternatively, the refrigerant system1144pumps a refrigerant between the supply air heat exchanger1120and both the regeneration air heat exchanger1142and the regeneration heat exchanger1162. Heat exchanger switches1190and1192controls the flow of refrigerant to the regeneration air heat exchangers1142and1162. Whereas heat exchanger switches1174and1176controls the flow of refrigerant to the supply air heat exchangers1120and1180. In the summer mode, the refrigerant system1144pumps cooled refrigerant to at least one of the supply air heat exchanger1120or the supply air heat exchanger1180to cool the air flowing through the supply air heat exchanger1120and/or the supply air heat exchanger1180. The cooled refrigerant is heated by the air in at least one of the supply air heat exchangers1120or the supply air heat exchanger1180to form heated refrigerant. The heated refrigerant flows through the piping to at least one of the regeneration air heat exchanger1142or the regeneration air heat exchanger1162to heat the air flowing through the regeneration air heat exchanger1142and/or the regeneration air heat exchanger1162. The refrigerant is cooled by the air in at least one of the regeneration air heat exchanger1142or the regeneration air heat exchanger1162to form cooled refrigerant that is pumped back to the supply air heat exchangers1120and/or1180.

In the winter mode, the refrigerant system1144pumps heated refrigerant to at least one of the supply air heat exchanger1120or the supply air heat exchanger1180to heat the air flowing through the supply air heat exchanger1120and/or the supply air heat exchanger1180. The heated refrigerant is cooled by the air in at least one of the supply air heat exchanger1120or the supply air heat exchanger1180to form cooled refrigerant. The cooled refrigerant flows through the piping to at least one of the regeneration air heat exchanger1142or the regeneration air heat exchanger1162to cool the air flowing through the regeneration air heat exchanger1142and/or the regeneration air heat exchanger1162. The refrigerant is heated by the air in at least one of the regeneration air heat exchanger1142or the regeneration air heat exchanger1162to form heated refrigerant that is pumped back to the supply air heat exchangers1120and/or1180.

The refrigerant system1144may include a metering device and check valve system1194to control a flow of the refrigerant between the supply air heat exchanger1120and/or the supply air heat exchanger1180and the regeneration air heat exchanger1142and/or the regeneration air heat exchanger1162. Additionally, a switch1199may be provided to reverse a flow of the refrigerant through the refrigerant system1144. For example, the flow of the refrigerant may be reversed when the system1100is switched between the summer mode and the winter mode. A compressor1146is provided to compress the refrigerant. In the summer mode, the refrigerant passes through the compressor1146after exiting the supply air heat exchangers1120and/or1180and before entering the regeneration air heat exchangers1142and/or1162. In the winter mode, the refrigerant passes through the compressor1146after exiting the regeneration air heat exchangers1142and/or1162and before entering the supply air heat exchangers1120and/or1180.

In a winter mode, the system1100may be configured to humidify and heat the supply air flowing into the building. For example, the supply air heat exchanger1120and the supply air heat exchanger1180may be reversed in the winter mode to operate as condenser coils. Additionally, the regeneration air heat exchangers1142and1162may be reversed in the winter mode to operate as evaporator coils.

FIGS. 32-43illustrates psychrometric charts for the system1100when operating in various configurations.FIGS. 32-43illustrate exemplary data point's representative of the air condition when passing between designated regions within system1100.FIG. 32illustrates the system1100in the summer mode when using 100% return air as the entering supply air while configured to perform pre-cooling, dehumidification and sensible cooling. In this configuration, the outside air inlet1137is closed, the return air outlet1130is closed, the mixing box damper1135is open, the mixing box damper1185is closed and the outside air inlet1103is closed such that all the return air through return air inlet1108provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% outside air.FIG. 32illustrates return air at data point3202with a dry bulb temperature of 75° F., a wet bulb temperature of approximately 63° F. and a relative humidity of approximately 50%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the return air is changed to data point3203(dry bulb temperature of 52° F., wet bulb temperature of 52° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3204(dry bulb temperature of 66° F., wet bulb temperature of 54° F. and 45% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point3205and supplied to the controlled space (dry bulb temperature of 61° F., wet bulb temperature of 52° F. and relative humidity 55%). The heat exchanger1180performs sensible cooling only without changing the humidity of the supply air. The regeneration air is also illustrated inFIG. 32, where outside air at data point3201with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3206(dry bulb temperature of 103° F., wet bulb temperature of 76° F. and 30% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3207(dry bulb temperature of 88° F., wet bulb temperature of 74° F. and 53% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3208and discharges to ambient (dry bulb temperature of 112° F., wet bulb temperature of 81° F. and relative humidity 27%). Because the heat absorbed in the refrigeration system is released in two separate condenser coils, with the second condenser coil located after the processing module1122where the temperature is reduced this substantially improves the performance of the refrigeration system1144because operation discharge pressures are lowered.

FIG. 33illustrates the system1100in the summer mode when using 100% return air as the entering supply air while configured to perform pre-cooling, dehumidification and no post-dehumidification sensible cooling. In this configuration, the outside air inlet1137is closed, the return air outlet1130is closed, the mixing box damper1135is open, the mixing box damper1185is closed and the outside air inlet1103is closed such that all the return air through return air inlet1108provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% outside air.FIG. 33illustrates return air at data point3302with a dry bulb temperature of 75° F., a wet bulb temperature of approximately 63° F. and a relative humidity of approximately 50%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the return air is changed to data point3303(dry bulb temperature of 49° F., wet bulb temperature of 49° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3304(dry bulb temperature of 63° F., wet bulb temperature of 51° F. and 45% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The regeneration air is also illustrated inFIG. 33, where outside air at data point3301with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3306(dry bulb temperature of 103° F., wet bulb temperature of 76° F. and 30% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3307(dry bulb temperature of 88° F., wet bulb temperature of 74° F. and 53% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3308and discharges to ambient (dry bulb temperature of 112° F., wet bulb temperature of 81° F. and relative humidity 27%). Because the heat absorbed in the refrigeration system is released in two separate condenser coils, with the second condenser coil located after the processing module1122where the temperature is reduced this substantially improves the performance of the refrigeration system1144because operation discharge pressures are lowered.

FIG. 34illustrates the system1100in the summer mode when using 50% return air and 50% outside air as the mixed entering supply air while the system is configured to perform pre-cooling, dehumidification and post-dehumidification sensible cooling. In this configuration, the outside air inlet1137is open, the return air outlet1130is closed, the mixing box damper1135is half open, the mixing box damper1185is half open and the outside air inlet1103is open such that both the supply air and the regeneration is comprised of 50% return air and 50% outside air. Once the desired portions of outside and return air are mixed at the mixing boxes, the mixed air has the conditions denoted at data point3409(dry bulb temperature of 77° F., wet bulb temperature of 66° F. and relative humidity 57%). As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the air is changed to data point3403(dry bulb temperature of 54° F., wet bulb temperature of 54° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3404(dry bulb temperature of 68° F., wet bulb temperature of 55° F. and 43% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point3405and supplied to the controlled space (dry bulb temperature of 63° F., wet bulb temperature of 53° F. and relative humidity 52%). The heat exchanger1180performs sensible cooling only without changing the humidity of the supply air. The regeneration air is also illustrated inFIG. 34, where the mixed regeneration air at data point3409with a dry bulb temperature of 77° F., a wet bulb temperature of approximately 66° F. and a relative humidity of approximately 57%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3406(dry bulb temperature of 100° F., wet bulb temperature of 73° F. and 25% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3407(dry bulb temperature of 85° F., wet bulb temperature of 71° F. and 52% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3408and discharges to ambient (dry bulb temperature of 108° F., wet bulb temperature of 78° F. and relative humidity 32%).

FIG. 35illustrates the system1100in the summer mode when using 50% return air and 50% outside air as the mixed entering supply air while the system is configured to perform pre-cooling, dehumidification and no post-dehumidification sensible cooling. In this configuration, the outside air inlet1137is open, the return air outlet1130is closed, the mixing box damper1135is half open, the mixing box damper1185is half open and the outside air inlet1103is open such that both the supply air and the regeneration is comprised of 50% return air and 50% outside air. Once the desired portions of outside and return air are mixed at the mixing boxes, the mixed air has the conditions denoted at data point3509(dry bulb temperature 77° F., wet bulb temperature 66° F. and relative humidity 57%). As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the air is changed to data point3503(dry bulb temperature of 51° F., wet bulb temperature of 51° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3504(dry bulb temperature of 66° F., wet bulb temperature of 54° F. and 43% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The regeneration air is also illustrated inFIG. 35, where the mixed regeneration air at data point3509with a dry bulb temperature of 77° F., a wet bulb temperature of approximately 66° F. and a relative humidity of approximately 57%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3506(dry bulb temperature of 100° F., wet bulb temperature of 73° F. and 25% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3507(dry bulb temperature of 85° F., wet bulb temperature of 71° F. and 52% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3508and discharges to ambient (dry bulb temperature of 108° F., wet bulb temperature of 78° F. and relative humidity 32%).

FIG. 36illustrates the system1100in the summer mode when using 100% outside air as the entering supply air while configured to perform pre-cooling, dehumidification and sensible cooling. In this configuration, the outside air inlet1137is open, the return air outlet1130is close, the mixing box damper1135is close, the mixing box damper1185is close and the outside air inlet1103is close such that all the outside air through supply air inlet1137provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% return air.FIG. 36illustrates outside air at data point3601with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point3603(dry bulb temperature of 56° F., wet bulb temperature of 56° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3604(dry bulb temperature of 72° F., wet bulb temperature of 57° F. and 40% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point3605and supplied to the controlled space (dry bulb temperature of 66° F., wet bulb temperature of 55° F. and relative humidity 50%). The heat exchanger1180performs sensible cooling only without changing the humidity of the supply air. The regeneration air is also illustrated inFIG. 36, where return air at data point3602with a dry bulb temperature of 75° F., a wet bulb temperature of approximately 62° F. and a relative humidity of approximately 50%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3606(dry bulb temperature of 98° F., wet bulb temperature of 69° F. and 28% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3607(dry bulb temperature of 82° F., wet bulb temperature of 68° F. and 50% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3608and discharges to ambient (dry bulb temperature of 105° F., wet bulb temperature of 75° F. and relative humidity 25%). Because the regeneration air is 100% return air (which is typically drier then the outside air in the summer) the system1100is able to improve the performance of the processing module to extract additional moisture from the supply air stream and further dry the supply air in the summer mode. The performance of the refrigeration system is also improved as the discharge pressures are lowered.

FIG. 37illustrates the system1100in the summer mode when using 100% outside air as the entering supply air while configured to perform pre-cooling, dehumidification and no post dehumidification sensible cooling. In this configuration, the outside air inlet1137is open, the return air outlet1130is close, the mixing box damper1135is close, the mixing box damper1185is close and the outside air inlet1103is close such that all the outside air through supply air inlet1137provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% return air.FIG. 37illustrates outside air at data point3701with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point3703(dry bulb temperature of 55° F., wet bulb temperature of 55° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3704(dry bulb temperature of 70° F., wet bulb temperature of 57° F. and 42% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The regeneration air is also illustrated inFIG. 37, where return air at data point3702with a dry bulb temperature of 75° F., a wet bulb temperature of approximately 62° F. and a relative humidity of approximately 50%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3706(dry bulb temperature of 98° F., wet bulb temperature of 70° F. and 28% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3707(dry bulb temperature of 82° F., wet bulb temperature of 68° F. and 50% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3708and discharges to ambient (dry bulb temperature of 105° F., wet bulb temperature of 75° F. and relative humidity 25%). Because the regeneration air is 100% return air (which is typically drier then the outside air in the summer) the system1100is able to improve the performance of the processing module to extract additional moisture from the supply air stream and further dry the supply air in the summer mode. The performance of the refrigeration system is also improved as the discharge pressures are lowered.

FIG. 38illustrates the system1100in the winter mode when using 100% return air as the entering supply air while configured to perform pre-heating, humidification and post sensible heating. In this configuration, the outside air inlet1137is closed, the return air outlet1130is closed, the mixing box damper1135is open, the mixing box damper1185is closed and the outside air inlet1103is closed such that all the return air through return air inlet1108provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% outside air.FIG. 38illustrates return air at data point3802with a dry bulb temperature of 70° F., a wet bulb temperature of approximately 53° F. and a relative humidity of approximately 30%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the return air is changed to data point3803(dry bulb temperature of 92° F., wet bulb temperature of 62° F. and 15% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3804(dry bulb temperature of 77° F., wet bulb temperature of 59° F. and 33% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point3805and supplied to the controlled space (dry bulb temperature of 100° F., wet bulb temperature of 67° F. and relative humidity 16%). The heat exchanger1180performs post sensible heating. The regeneration air is also illustrated inFIG. 38, where outside air at data point3801with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 37° F. and a relative humidity of approximately 40%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3806(dry bulb temperature of 26° F., wet bulb temperature of 25° F. and 90% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3807(dry bulb temperature of 41° F., wet bulb temperature of 31° F. and 28% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3808and discharges to ambient (dry bulb temperature of 23° F., wet bulb temperature of 20° F. and relative humidity 60%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space.

FIG. 39illustrates the system1100in the winter mode when using 100% return air as the entering supply air while configured to perform pre-heating, humidification and no post sensible heating. In this configuration, the outside air inlet1137is closed, the return air outlet1130is closed, the mixing box damper1135is open, the mixing box damper1185is closed and the outside air inlet1103is closed such that all the return air through return air inlet1108provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% outside air.FIG. 39illustrates return air at data point3902with a dry bulb temperature of 70° F., a wet bulb temperature of approximately 53° F. and a relative humidity of approximately 30%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the return air is changed to data point3903(dry bulb temperature of 105° F., wet bulb temperature of 66° F. and 9% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3904(dry bulb temperature of 87° F., wet bulb temperature of 63° F. and 25% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The regeneration air is also illustrated inFIG. 39, where outside air at data point3901with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 37° F. and a relative humidity of approximately 40%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point3906(dry bulb temperature of 26° F., wet bulb temperature of 25° F. and 90% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point3907(dry bulb temperature of 45° F., wet bulb temperature of 32° F. and 20% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point3908and discharges to ambient (dry bulb temperature of 26° F., wet bulb temperature of 21° F. and relative humidity 45%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space. Furthermore, because the refrigeration system1144includes heat exchanger switches1174and1176that control the flow of refrigerant independently to the supply air heat exchangers1120and1180this allows to the system to control the space sensible load independently from the latent load.

FIG. 40illustrates the system1100in the winter mode when using 50% return air and 50% outside air as the mixed entering supply air while the system is configured to perform pre-heating, humidification and post-sensible heating. In this configuration, the outside air inlet1137is open, the return air outlet1130is closed, the mixing box damper1135is half open, the mixing box damper1185is half open and the outside air inlet1103is open such that both the supply air and the regeneration is comprised of 50% return air and 50% outside air. Once the desired portions of outside and return air are mixed at the mixing boxes, the mixed air has the conditions denoted at data point4009(dry bulb temperature of 57° F., wet bulb temperature of 45° F. and relative humidity 37%). As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the air is changed to data point4003(dry bulb temperature of 80° F., wet bulb temperature of 55° F. and 17% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4004(dry bulb temperature of 68° F., wet bulb temperature of 53° F. and 36% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point4005and supplied to the controlled space (dry bulb temperature of 90° F., wet bulb temperature of 61° F. and relative humidity 17%). The heat exchanger1180performs sensible heating. The regeneration air is also illustrated inFIG. 40, where the mixed regeneration air at data point4009with a dry bulb temperature of 57° F., a wet bulb temperature of approximately 45° F. and a relative humidity of approximately 37%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4006(dry bulb temperature of 38° F., wet bulb temperature of 35° F. and 70% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4007(dry bulb temperature of 51° F., wet bulb temperature of 38° F. and 24% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4008and discharges to ambient (dry bulb temperature of 32° F., wet bulb temperature of 26° F. and relative humidity 50%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space.

FIG. 41illustrates the system1100in the winter mode when using 50% return air and 50% outside air as the mixed entering supply air while the system is configured to perform pre-heating, humidification and no post-sensible heating. In this configuration, the outside air inlet1137is open, the return air outlet1130is closed, the mixing box damper1135is half open, the mixing box damper1185is half open and the outside air inlet1103is open such that both the supply air and the regeneration is comprised of 50% return air and 50% outside air. Once the desired portions of outside and return air are mixed at the mixing boxes, the mixed air has the conditions denoted at data point4109(dry bulb temperature of 57° F., wet bulb temperature of 45° F. and relative humidity 37%). As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the air is changed to data point4103(dry bulb temperature of 92° F., wet bulb temperature of 60° F. and 12% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4104(dry bulb temperature of 77° F., wet bulb temperature of 52° F. and 28% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The regeneration air is also illustrated inFIG. 41, where the mixed regeneration air at data point4109with a dry bulb temperature of 57° F., a wet bulb temperature of approximately 45° F. and a relative humidity of approximately 37%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4106(dry bulb temperature of 38° F., wet bulb temperature of 35° F. and 70% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4107(dry bulb temperature of 55° F., wet bulb temperature of 39° F. and 17% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4108and discharges to ambient (dry bulb temperature of 36° F., wet bulb temperature of 28° F. and relative humidity 38%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space. Furthermore, because the refrigeration system1144includes heat exchanger switches1174and1176that control the flow of refrigerant independently to the supply air heat exchangers1120and1180this allows to the system to control the space sensible load independently from the latent load.

FIG. 42illustrates the system1100in the winter mode when using 100% outside air as the entering supply air while configured to perform pre-heating, humidification and post-sensible heating. In this configuration, the outside air inlet1137is open, the return air outlet1130is close, the mixing box damper1135is close, the mixing box damper1185is close and the outside air inlet1103is close such that all the outside air through supply air inlet1137provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% return air.FIG. 42illustrates outside air at data point4201with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 36° F. and a relative humidity of approximately 40%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point4203(dry bulb temperature of 67° F., wet bulb temperature of 48° F. and 18% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4204(dry bulb temperature of 59° F., wet bulb temperature of 47° F. and 38% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point4205and supplied to the controlled space (dry bulb temperature of 82° F., wet bulb temperature of 56° F. and relative humidity 17%). The heat exchanger1180performs post sensible heating. The regeneration air is also illustrated inFIG. 42, where return air at data point4202with a dry bulb temperature of 70° F., a wet bulb temperature of approximately 53° F. and a relative humidity of approximately 30%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4206(dry bulb temperature of 52° F., wet bulb temperature of 45° F. and 58% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4207(dry bulb temperature of 60° F., wet bulb temperature of 45° F. and 30% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4208and discharges to ambient (dry bulb temperature of 41° F., wet bulb temperature of 36° F. and relative humidity 60%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space. Furthermore, the system utilizes return air from the space to regenerate the processing module improving yet further the overall performance of system1100.

FIG. 43illustrates the system1100in the winter mode when using 100% outside air as the entering supply air while configured to perform pre-heating, humidification and no post-sensible heating. In this configuration, the outside air inlet1137is open, the return air outlet1130is close, the mixing box damper1135is close, the mixing box damper1185is close and the outside air inlet1103is close such that all the outside air through supply air inlet1137provides all of the supply air. Correspondingly the entering regeneration air is comprised of 100% return air.FIG. 43illustrates outside air at data point4301with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 36° F. and a relative humidity of approximately 40%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point4303(dry bulb temperature of 88° F., wet bulb temperature of 56° F. and 9% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4304(dry bulb temperature of 73° F., wet bulb temperature of 54° F. and 28% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The heat exchanger1180performs no post sensible heating. The regeneration air is also illustrated inFIG. 43, where return air at data point4302with a dry bulb temperature of 70° F., a wet bulb temperature of approximately 53° F. and a relative humidity of approximately 30%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4306(dry bulb temperature of 52° F., wet bulb temperature of 45° F. and 58% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4307(dry bulb temperature of 66° F., wet bulb temperature of 47° F. and 18% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4308and discharges to ambient (dry bulb temperature of 48° F., wet bulb temperature of 37° F. and relative humidity 35%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space. Additionally, because the refrigeration system1144includes heat exchanger switches1174and1176that control the flow of refrigerant independently to the supply air heat exchangers1120and1180this allows to the system to control the space sensible load independently from the latent load. Furthermore, the system utilizes return air from the space to regenerate the processing module improving yet further the overall performance of system1100.

In one embodiment, the heat pump system1100senses a condition of at least one of the supply air or return air from the space to control an output of at least one of the supply air heat exchangers1120and/or1180, the supply heat exchanger switches1174and/or1176, the regeneration air heat exchangers1142and/or1162, the regeneration heat exchanger switches1190and/or1192, the processing module1122, the mixing boxes1135and/or1185to achieve a pre-determined dehumidification in the summer mode and pre-determined humidification in a winter mode.

In another embodiment, the heat pump system1100senses a condition of at least one of the supply air or return air from the space to control an output of at least one of the supply air heat exchangers1120and/or1180, the supply heat exchanger switches1174and/or1176, the regeneration air heat exchangers1142and/or1162, the regeneration heat exchanger switches1190and/or1192, the processing module1122, the mixing boxes1135and/or1185to achieve a pre-determined performance of the system1100.

In another embodiment, the heat pump system1100senses a condition of at least one of the supply air or return air from the space to control an output of at least one of the supply air heat exchangers1120and/or1180, the supply heat exchanger switches1174and/or1176, the regeneration air heat exchangers1142and/or1162, the regeneration heat exchanger switches1190and/or1192, the processing module1122, the mixing boxes1135and/or1185to limit frost formation in the regeneration air heat exchangers1142and/or1162in the winter mode.

In another embodiment, the heat pump system1100senses a condition of at least one of a supply air stream or a return air stream to control the output of at least one of a single compressor or variable compressor to limit frost formation in the regeneration heat exchangers1142and/or1162in winter mode.

In another embodiment, the heat pump system1100senses a condition of at least one of a supply air stream or a return air stream to control the output of at least one of a single compressor or variable compressor to achieve a pre-determined performance of the system1100.

In another embodiment, the heat pump system1100is used for conditioning air supplied to a space. The system includes conditioning supply air with a processing module. The system also includes at least one of heating or cooling the air prior to or after the processing module with one or more supply air heat exchangers in flow communication with the processing module. The system1100also includes at least one heat exchanger switch in flow communication with the supply air heat exchangers that is fluidly coupled to a refrigerant system and a control system that allows the space sensible load and latent load to be maintained independently.

In another embodiment, the heat pump system1100described herein utilizes a plurality of heat exchangers and a refrigeration system in both summer and winter modes for energy recovery. The embodiment further utilizes a plurality of heat exchanger switches to control the flow of cold and hot refrigerant in the refrigeration system. Additionally, as the return air is dehumidified by the processing module, the dry bulb temperature of the return air is increased which increases the efficiency of the heat pump. The evaporator can then run at lower temperatures without freezing the evaporator fins. In winter mode the energy in the return air is used in the reverse air source heat pump cycle.

In another embodiment, the heat pump system1100described herein, supply air is humidified by the processing module to reduce humidification load requirements and energy consumption for the buildings in the winter mode. The embodiments also provide an efficient air source heat pump for winter heating in lieu of electric, gas, HW, or stream. The return air also provides stable and optimum regenerative air temperatures and conditions for the processing module reactivation in both the summer and winter mode.

FIG. 44is a schematic view of an alternative embodiment of the heat pump system1100. InFIG. 31, the return air flow path1139is configured to flow in either one of or both mixing box dampers1135and/or1185depending on the different operation mode of system1100to form the portion of the return air flow path1133. InFIG. 44, the portion return air flow paths1133are none existent. Accordingly, the return air flow path1139is configured to flow completely through the return air opening1130forming the exhaust air flow path1131. InFIG. 31, the mixing box damper1135and/or mixing box damper1185can be open, whereas inFIG. 44both the mixing box dampers1135and1185are closed. InFIG. 44, both the outside air inlet1137and outside air inlet1103are fully open providing 100% outside air to both the supply air flow path1102and the regeneration air flow path1106. Providing 100% outside air to both the supply air flow path1102and the regeneration air flow path1106may improve the transfer of heat and moisture between the supply air side1124and the regeneration air side1126of the processing module1122. Additionally, providing 100% outside air to both the supply air flow path1102and the regeneration air flow path1106may improve the coefficient of performance (COP) of the system as the suction pressure may be increased and the discharge pressure may be decreased. Furthermore, because the refrigeration system1144includes and switch1199, heat exchanger switches1174,1176,1190and1192that are all in flow communication with compressor1146as well as heat exchangers1120,1180,1142and1162positioned on the upstream side and downstream side of the processing module1122also in flow communication with compressor1146the overall system1100can be controlled very efficiently to maintain building heating, cooling, humidification and dehumidification loads through the year. While it is preferred in most instances to include a return air flow path, it is also understood that system1100inFIG. 44may not contain a return air inlet1108, return air flow path1139, a return air outlet1130, an exhaust air flow path1131and mixing boxes1135and1185and system1100would still function as described herein.

FIGS. 45-48illustrates psychrometric charts for the system1100when operating in various configurations.FIGS. 45-48illustrate exemplary data point's representative of the air condition when passing between designated regions within system1100.FIG. 45illustrates the system1100in the summer mode when using 100% outside air as the entering supply air while configured to perform pre-cooling, dehumidification and sensible cooling. In this configuration, the outside air inlet1137is open, the return air outlet1130is open, the mixing box damper1135is close, the mixing box damper1185is closed and the outside air inlet1103is open such that all the outside air through outside air inlet1137provides all of the supply air and all the outside air through outside air inlet1103provides all of the regeneration air.FIG. 45illustrates outside air at data point4501with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point4503(dry bulb temperature of 56° F., wet bulb temperature of 56° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4504(dry bulb temperature of 71° F., wet bulb temperature of 58° F. and 47% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point4505and supplied to the controlled space (dry bulb temperature of 65° F., wet bulb temperature of 56° F. and relative humidity 56%). The heat exchanger1180performs sensible cooling only without changing the humidity of the supply air. The regeneration air is also illustrated inFIG. 45, where outside air at data point4501with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4506(dry bulb temperature of 103° F., wet bulb temperature of 76° F. and 30% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4507(dry bulb temperature of 88° F., wet bulb temperature of 75° F. and 53% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4508and discharges to ambient (dry bulb temperature of 115° F., wet bulb temperature of 81.5° F. and relative humidity 24%). Because the heat absorbed in the refrigeration system is released in two separate condenser coils, with the second condenser coil located after the processing module1122where the temperature is reduced this substantially improves the performance of the refrigeration system1144because operation discharge pressures are lowered. Furthermore, since the supply heat exchanger1180is active the sensible load and latent load of the space can be maintained independently.

FIG. 46illustrates the system1100in the summer mode when using 100% outside air as the entering supply air while configured to perform pre-cooling, dehumidification and no post-sensible cooling. In this configuration, the outside air inlet1137is open, the return air outlet1130is open, the mixing box damper1135is close, the mixing box damper1185is closed and the outside air inlet1103is open such that all the outside air through outside air inlet1137provides all of the supply air and all the outside air through outside air inlet1103provides all of the regeneration air.FIG. 46illustrates outside air at data point4601with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point4603(dry bulb temperature of 55° F., wet bulb temperature of 55° F. and 100% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4604(dry bulb temperature of 70° F., wet bulb temperature of 57° F. and 43% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The regeneration air is also illustrated inFIG. 46, where outside air at data point4601with a dry bulb temperature of 80° F., a wet bulb temperature of approximately 70° F. and a relative humidity of approximately 60%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4606(dry bulb temperature of 105° F., wet bulb temperature of 77° F. and 28% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4607(dry bulb temperature of 89° F., wet bulb temperature of 75° F. and 52% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4608and discharges to ambient (dry bulb temperature of 115° F., wet bulb temperature of 81.5° F. and relative humidity 24%). Because the heat absorbed in the refrigeration system is released in two separate condenser coils, with the second condenser coil located after the processing module1122where the temperature is reduced this substantially improves the performance of the refrigeration system1144because operation discharge pressures are lowered. Furthermore, since the supply heat exchanger1180is inactive the sensible load and latent load of the space can be maintained independently.

FIG. 47illustrates the system1100in the winter mode when using 100% outside air as the entering supply air while configured to perform pre-heating, humidification and post-sensible heating. In this configuration, the outside air inlet1137is open, the return air outlet1130is open, the mixing box damper1135is close, the mixing box damper1185is closed and the outside air inlet1103is open such that all the outside air through outside air inlet1137provides all of the supply air and all the outside air through outside air inlet1103provides all of the regeneration air.FIG. 47illustrates outside air at data point4701with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 36° F. and a relative humidity of approximately 40%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point4703(dry bulb temperature of 68° F., wet bulb temperature of 48° F. and 18% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4704(dry bulb temperature of 57° F., wet bulb temperature of 46° F. and 40% relative humidity). As the air passes through the active supply air heat exchanger1180, the conditions are further changed to data point4705and supplied to the controlled space (dry bulb temperature of 81° F., wet bulb temperature of 56° F. and relative humidity 18%). The heat exchanger1180performs post sensible heating. The regeneration air is also illustrated inFIG. 47, where outside air at data point4701with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 36° F. and a relative humidity of approximately 40%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4706(dry bulb temperature of 26° F., wet bulb temperature of 25° F. and 85% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4707(dry bulb temperature of 37° F., wet bulb temperature of 29° F. and 35% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4708and discharges to ambient (dry bulb temperature of 18° F., wet bulb temperature of 17° F. and relative humidity 90%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space. Furthermore, because the refrigeration system1144includes heat exchanger switches1174and1176that control the flow of refrigerant independently to the supply air heat exchangers1120and1180the sensible load and latent load of the space can be maintained independently.

FIG. 48illustrates the system1100in the winter mode when using 100% outside air as the entering supply air while configured to perform pre-heating, humidification and no post-sensible heating. In this configuration, the outside air inlet1137is open, the return air outlet1130is open, the mixing box damper1135is close, the mixing box damper1185is closed and the outside air inlet1103is open such that all the outside air through outside air inlet1137provides all of the supply air and all the outside air through outside air inlet1103provides all of the regeneration air.FIG. 48illustrates outside air at data point4801with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 36° F. and a relative humidity of approximately 40%. As the supply air passes through the active supply air heat exchanger1120, the humidity and temperature of the outside air is changed to data point4803(dry bulb temperature of 88° F., wet bulb temperature of 56° F. and 9% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4804(dry bulb temperature of 72° F., wet bulb temperature of 54° F. and 28% relative humidity). As the air passes through the inactive supply air heat exchanger1180, the supply air conditions are unchanged. The heat exchanger1180performs no post-sensible heating. The regeneration air is also illustrated inFIG. 48, where outside air at data point4801with a dry bulb temperature of 45° F., a wet bulb temperature of approximately 36° F. and a relative humidity of approximately 40%. As the regeneration air passes through the active regeneration air heat exchanger1142, the humidity and temperature of the regeneration air is changed to data point4806(dry bulb temperature of 26° F., wet bulb temperature of 25° F. and 85% relative humidity), and as the air passes through the processing module1122, the air conditions are adjusted to data point4807(dry bulb temperature of 43° F., wet bulb temperature of 30° F. and 22% relative humidity). As the air passes through the second active regeneration air heat exchanger1162, the conditions are further changed to data point4808and discharges to ambient (dry bulb temperature of 24° F., wet bulb temperature of 19° F. and relative humidity 50%). Because the refrigeration system1144includes heat exchanger switches1190and1192that control the flow of refrigerant independently to the regeneration air heat exchangers1142and1162this improved the performance of the processing module1122to absorb moisture and heat the regeneration air stream thus substantially improving the performance of the refrigeration system1144because the suction pressures are higher, improving the coefficient of performance (COP) of the system. Additionally the processing module offsets humidification load requirement in the space. Furthermore, because the refrigeration system1144includes heat exchanger switches1174and1176that control the flow of refrigerant independently to the supply air heat exchangers1120and1180the sensible load and latent load of the space can be maintained independently.

In one embodiment, the heat pump system1100senses a condition of at least one of the supply air or regeneration air to control an output of at least one of the supply air heat exchangers1120and/or1180, the supply heat exchanger switches1174and/or1176, the regeneration air heat exchangers1142and/or1162, the regeneration heat exchanger switches1190and/or1192, the processing module1122, to achieve a pre-determined dehumidification in the summer mode and pre-determined humidification in a winter mode.

In another embodiment, the heat pump system1100senses a condition of at least one of the supply air or regeneration air to control an output of at least one of the supply air heat exchangers1120and/or1180, the supply heat exchanger switches1174and/or1176, the regeneration air heat exchangers1142and/or1162, the regeneration heat exchanger switches1190and/or1192, the processing module1122, to achieve a pre-determined performance of the system1100.

In another embodiment, the heat pump system1100senses a condition of at least one of the supply air or regeneration air to control an output of at least one of the supply air heat exchangers1120and/or1180, the supply heat exchanger switches1174and/or1176, the regeneration air heat exchangers1142and/or1162, the regeneration heat exchanger switches1190and/or1192, the processing module1122, to limit frost formation in the regeneration air heat exchangers1142and/or1162in the winter mode.

In another embodiment, the heat pump system1100is used for conditioning air supplied to a space. The system includes conditioning supply air with a processing module using only outside air. The system also includes at least one of heating or cooling the air prior to or after the processing module with one or more supply air heat exchangers in flow communication with the processing module. The system1100also includes at least one heat exchanger switch in flow communication with the supply air heat exchangers that is fluidly coupled to a refrigerant system and a control system that allows the space sensible load and latent load to be maintained independently.

In another embodiment, the heat pump system1100described herein utilizes a plurality of heat exchangers and a refrigeration system in both summer and winter modes for energy recovery. The embodiment further utilizes a plurality of heat exchanger switches to control the flow of cold and hot refrigerant in the refrigeration system. Additionally, as the outside air is dehumidified by the processing module, the dry bulb temperature of the outside air is increased which increases the efficiency of the heat pump. The evaporator can then run at lower temperatures without freezing the evaporator fins. In winter mode the energy in the outside air is used in the reverse air source heat pump cycle.

In another embodiment, the system1100may include at least one fan to draw air into and move air through the supply air flow path1102. Outside air flows through the supply air inlet1137and through supply heat exchanger1120, a pre-processing module1122positioned downstream of the supply air inlet1137.

In another embodiment additional compressors, additional refrigerant systems, pre-cooling, pre-heating supply heat exchangers and energy recovery devices (not shown) can be added to system1100further performance of the system.

In another embodiment, the heat pump system1100described herein, supply air is humidified by the processing module to reduce humidification load requirements and energy consumption for the buildings in the winter mode while using only outside air. The embodiments also provide an efficient air source heat pump for winter heating in lieu of electric, gas, HW, or stream.

FIG. 49is a schematic view of another heat pump system600formed in accordance with an embodiment capable of operating in a summer mode or a winter mode.