The present invention relates to an apparatus for climate control of an air stream. In particular, the apparatus is suitable for cooling, dehumidifying, heating and humidifying. The climate control apparatus finds use in all the different types of climate conditions.

Background to the Invention

Air conditioning apparatus known in the art typically comprise a vapour-compression refrigeration cycle. Such devices have a variety of uses ranging from cooling buildings, cars and even outdoor environments.

Figure 1 depicts a typical vapour-compression air conditioning apparatus 1 comprising a refrigerant 2 within a sealed cycle which undergoes repeated phase transitions between a liquid and a gas. Cold, uncompressed, liquid refrigerant 2’ passes into an evaporator 3, absorbs surrounding heat (Q _IN ) and evaporates to form a cold, uncompressed, gaseous refrigerant 2” output. The cold, uncompressed, gaseous refrigerant 2” is then compressed by a compressor 4 which increases the temperature, forming a hot, compressed gaseous refrigerant 2’”. The hot, compressed, gaseous refrigerant 2’” is then cooled by a condenser 5. Heat (QOUT) is expelled from the refrigerant 2 to the surroundings of the condenser 5, typically located outside the building, and the refrigerant 2’” transitions back to a liquid forming a hot, compressed, liquid refrigerant 2””. The hot, compressed, liquid refrigerant 2”” is cooled even further by passing through an expansion valve 6. After which, the cold, uncompressed, liquid refrigerant 2’ is circulated back into the evaporator 3 to absorb more heat from within the building and the cycle repeats thereby cooling the building.

A vapour-compression air conditioning apparatus 1 of Figure 1 can heat a building if the apparatus is configured such that evaporator 3 is located outside the building and the condenser 5 is located inside the building. Heat is effectively pumped into the building.

A significant disadvantage of air conditioning apparatus known in the art, in both indoor and outdoor cooling and heating applications, is the significant amounts of energy consumed by such apparatus. Electrical energy is consumed to operate the compressor 4 and condenser 5. Air conditioning apparatus can be particularly energy intensive when operating at high altitude with fresh air in either a hot humid climate or a cold climate. Furthermore, another disadvantage of the vapour-compression air conditioning apparatus 1 is that the apparatus is limited to cooling and heating. The apparatus 1 cannot control humidity and so cannot offer full climate control, in other words, humidity and temperature control.

Water can be used in air conditioning apparatus for cooling and humidification. For example, an air stream can be directed past a water cooling coil comprising cold water. Heat from the air stream diffuses to the cold water within the water cooling coil. The water, and thereby the heat, is then circulated away from the air stream thereby cooling the air stream.

Whilst in some types of climates water is abundant, in other types of climates, water is a precious commodity. As such, a disadvantage of such an apparatus is that it is not suitable for all types of climates. In particular, it can remain a challenge to balance both electricity and water tariffs to minimise the operational cost of an air conditioning apparatus. Another disadvantages of air conditioning apparatus know in the art is that they can require a significant amount of space, especially the ones used for outdoor air cooling and heating, and it can be challenging to reduce the footprint of the apparatus.

Summary of the Invention

It is an object of an aspect of the present invention to provide climate control apparatus that obviates or at least mitigates one or more of the aforesaid disadvantages of related air conditioning apparatus known in the art.

According to a first aspect of the present invention there is provided a climate control apparatus suitable for cooling and or heating a first air stream comprising: a first air stream path for the first air stream; a second air stream path for a second air stream; a primary water cooling apparatus located within the first air stream path, the primary water cooling apparatus configured to transfer heat from the first air stream to water; a primary evaporative cooling device located within the second air stream path, the primary evaporative cooling device configured to cool the second air stream and the water from the primary water cooling apparatus; and a secondary evaporative cooling device located within the first air stream path and after the primary water cooling apparatus, the secondary evaporative cooling device configured to cool and or control the temperature of the first air stream, humidify the first air stream and or further cool and or control the temperature of the water from the primary evaporative cooling device.

A key advantage is the climate control apparatus is that the configuration requires minimal energy to operate as the evaporative cooling devices do not draw any electricity. The primary evaporative cooling device within the second air stream cools the water to or close to the wet bulb temperature of the first air stream. However, the water can be cooled even further by the secondary evaporative cooling device within first air stream which as the first air stream has a lower web bulb temperature.

Preferably, the primary water cooling apparatus is a primary water cooling coil. Optionally, the water cooling coil may be cross or counter flow heat exchanger, a microchannel heat exchanger, a plate heat exchanger or any other suitable heat exchanger. The water cooling apparatus may be made of any suitable material

Preferably, the climate control apparatus further comprises a vapour-compression refrigeration loop.

Preferably, the vapour-compression refrigeration loop comprises an evaporator. The evaporator is located directly or indirectly by means of a water loop within the first air stream path between the primary water cooling coil and the secondary evaporative cooling device.

Preferably, the vapour-compression refrigeration loop comprises a primary condenser.

The primary condenser is located within the second air stream path after the first evaporative cooling device. The condenser can be air cooled coil, or any air or water cooled heat exchanger. The condenser can be coil, microchannel, cross or plate heat exchanger or any heat exchanger.

Optionally, the vapour-compression refrigeration loop may comprise a secondary condenser. The secondary condenser is located along the first air stream path between the evaporator and secondary evaporative cooling device.

Optionally, the vapour-compression refrigeration loop may comprise one or more valves to operate the primary condenser and secondary condenser in series or parallel, or by pass the secondary condenser.

Optionally, the vapour-compression refrigeration loop may comprise a heat exchanger.

The heat exchanger exchanges heat between the refrigerant before a compressor and after the primary condenser.

Optionally, the climate control apparatus further comprises a secondary water cooling coil. The secondary water cooling coil may be a secondary chilled water cooling coil. The secondary water cooling coil is located within the first air stream path after the primary water cooling coil. Optionally, the primary water cooling coil and the secondary water cooling coil are combined within one single water cooling coil with multiple water circuits. The single water cooling coil with multiple water circuits is a high performance heat exchanger.

Optionally, the vapour-compression refrigeration loop may comprise a heat exchanger. Water transfers heat between the secondary water cooling coil and the heat exchanger such as a plate heat exchanger. The vapour-compression refrigeration loop indirectly cools the first air stream by means of the secondary water cooling coil. The heat exchanger may be a plate heat exchanger or any type of heat exchanger with or without a thermal store.

Optionally, the climate control apparatus comprises a hot water heat exchanger within the second path after the primary evaporative cooling device. The hot water heat exchanger may also be considered a warm water heat exchanger. The hot water heat exchanger receives water from the primary cooling coil. The evaporatively cooled second air stream cools the warm water before being cooled further within the secondary evaporative cooling device. The hot water heat exchanger can be coil, microchannel, cross flow heat exchanger of any type.

Optionally, the primary evaporative cooling device and the hot water heat exchanger are combined within one heat exchanger.

Optionally, the climate control apparatus comprises a thermoelectric heat pump. The thermoelectric heat pump comprises a first plate, a second plate and pillars of p-type and n-type semiconductors between the first and second plates. A first water loop transfers heat between the secondary water cooling coil and the first plate of the thermoelectric heat pump. A second water loop transfers heat between the hot water heat exchanger and the second plate of the thermoelectric heat pump.

Optionally, the climate control apparatus comprises an external water source (e.g. geothermal or cooling tower). The external water source may supply the primary water cooling coil and or the secondary water cooling coil. The external water source may be an external chilled water source. The secondary water cooling coil can utilise cold or hot water from the external water source. This facilitates the climate control apparatus to be able to cool and or heat. Preferably, the climate control apparatus comprises a control unit.

Preferably, the climate control apparatus comprises one or more temperature and or humidity sensors.

Preferably, the climate control apparatus comprises a water tank, and or one or more a pumps suitable for pumping water and or chilled water.

Preferably, the climate control apparatus comprises one or more fans located along the first path and or one or more fans located along the second path.

Preferably, the climate control apparatus comprises ducting. Preferably, the climate control apparatus comprises jet diffusers or grilles.

Preferably, the evaporator can be combined with a thermal store to provide cold water to the secondary water cooling coil and reversibly provide hot water to the secondary water cooling coil.

According to a second aspect of the present invention there is provided a method of manufacturing a climate control apparatus for cooling and or heating a first air stream comprising, providing a first air stream path for the first air stream; providing a second air stream path for a second air stream; providing a primary water cooling apparatus located within the first air stream path, the primary water cooling apparatus configured to transfer heat from the first air stream to water; providing a primary evaporative cooling device located within the second air stream path, the primary evaporative cooling device configured to cool the second air stream and the water from the primary water cooling apparatus; and providing a secondary evaporative cooling device located within the first path and after the primary water cooling apparatus, the secondary evaporative cooling device being configured to cool and or control the temperature of the first air stream, humidify the first air stream and or further cool and or control the temperature of the water from the primary evaporative cooling device.

Embodiments of the second aspect of the invention may comprise features to implement the preferred or optional features of the first aspect of the invention or vice versa.

According to a third aspect of the present invention there is provided an apparatus suitable for retrofitting to a cooling and or heating apparatus with a first air stream path for a first air stream, the apparatus comprising: a second air stream path for a second air stream; a primary evaporative cooling device located within the second air stream path, the primary evaporative cooling device configured to cool the second air stream and the water from the cooling and or heating apparatus; and a secondary evaporative cooling device located within the first air stream path of the cooling and or heating apparatus, the secondary evaporative cooling device configured to cool and or control the temperature of the first air stream, humidify the first air stream and or further cool and or control the temperature of the water from the cooling and or heating apparatus.

Embodiments of the third aspect of the invention may comprise features to implement the preferred or optional features of the first and or second aspect of the invention or vice versa.

According to a fourth aspect of the present invention there is provided a method of manufacturing an apparatus suitable for retrofitting to a cooling and or heating apparatus with a first air stream path for a first air stream, the method comprising: providing a second air stream path for a second air stream; providing a primary evaporative cooling device located within the second air stream path, the primary evaporative cooling device configured to cool the second air stream and the water from the cooling and or heating apparatus; and providing a secondary evaporative cooling device located within the first air stream path of the cooling and or heating apparatus, the secondary evaporative cooling device configured to cool and or control the temperature of the first air stream, humidify the first air stream and or further cool and or control the temperature of the water from the cooling and or heating apparatus. Embodiments of the fourth aspect of the invention may comprise features to implement the preferred or optional features of the first, second and or third aspect of the invention or vice versa.

Brief Description of Drawings

There will now be described, by way of example only, various embodiments of the invention with reference to the drawings, of which:

Figure 1 presents a schematic representation of air conditioning apparatus known in the art;

Figure 2 presents a perspective view of a climate control apparatus in accordance with the present invention;

Figure 3 presents a schematic representation of the climate control apparatus of Figure 2;

Figure 4 presents a schematic representation of a vapour-compression refrigeration loop of the climate control apparatus of Figure 2;

Figure 5 presents an alternative schematic representation of the vapour-compression refrigeration loop of Figure 4;

Figure 6 presents an alternative schematic representation of the climate control apparatus of Figure 2;

Figure 7 presents a further alternative schematic representation of the climate control apparatus of Figure 2;

Figure 8 presents yet another alternative schematic representation of the climate control apparatus of Figure 2; and

Figure 9 presents another alternative schematic representation of the climate control apparatus of Figure 2. In the description which follows, like parts are marked throughout the specification and drawings with the same reference numerals. The drawings are not necessarily to scale and the proportions of certain parts have been exaggerated to better illustrate details and features of embodiments of the invention.

Detailed Description of the Preferred Embodiments

An explanation of the present invention will now be described with reference to Figures 2 to 9.

Figures 2 and 3 depict a substantially cuboid, compact, climate control apparatus 7a comprising a first section 8 and a second section 9. As can clearly be seen in Figure 2, the second section 9 is located upon the first section 8 such that climate control apparatus 7a is split along a horizontal plane. It will be appreciated that the climate control apparatus 7a could instead be split along a vertical plane to define the first and second sections 8, 9. Alternatively, the climate control apparatus 7a may be split to define two non-uniform, irregular shaped sections 8, 9. It will also be appreciated the unitariness, the shape and or the dimensions of the climate control apparatus 7a may vary.

The first section 8 comprises a first inlet opening 10, a first outlet opening 11 and a first path 12 extending through the climate control apparatus 7a between the first inlet and first outlet openings 10, 11. The first inlet and first outlet openings 10, 11 are located on substantially opposing surfaces of the climate control apparatus 7a and aligned such that the first path 12 is substantially straight.

In use, a first air stream 13 is drawn directly or indirectly into the first inlet opening 10, passes through the first path 12 and exits via the first outlet opening 11. The first air stream 13 may be drawn indirectly into the first inlet opening 10 through a ducting 14 as can be seen in Figure 3. The ducting channels air from a remote location instead of in the immediate vicinity of the climate control apparatus 7a. The ducting 14 is an additional, optional feature.

Similarly, the second section 9 comprises a second inlet opening 15, a second outlet opening 16 and a second path 17 extending through the climate control apparatus 7a between the second inlet and second outlet openings 15, 16. The second inlet and second outlet opening 15, 16 are on substantially tangential surfaces such that the second path 12 is curved. In use, a second air stream 18 is drawn directly or indirectly into the second inlet opening 15, passes through the second path 12 and exits via the second outlet opening 16.

It will be appreciated the inlet and outlet openings 10, 11 , 15, 16 may be positioned such that the first and second paths 12, 17 take the form of a straight, curved or any irregular path through the climate control apparatus 7a.

It will be appreciated that the first air stream 13 and or the second air stream 18 may be formed using at least some recirculated air, in other words air that has already been through the climate control apparatus 7a.

The climate control apparatus 7a comprises a primary water cooling apparatus which takes the form of a primary water cooling coil 19. The primary water cooling coil 19 is located along the first path 12 directly after the first inlet opening 10. As such, the primary water cooling coil 19 is the first component the first air stream 13 intersects after entering the first inlet opening 10 and traversing the first path 12. The primary water cooling coil 19 may have any suitable structure. For example, the primary water cooling coil 19 may comprise a tubed coil and or a microchannel coil. The primary water cooling coil 19 may be made of any suitable materials such as metal and or plastic.

The primary water cooling coil 19 is fluidly connected to a water tank 20 by piping 21. In use, water 22 from the water tank 20 is pumped through the piping 21 to the primary water cooling coil 19 by a pump 23 as shown in Figure 3. Note, the path of the piping 21 and water 22 therein is depicted by dashed lines and arrows as can be seen in Figure 3.

The water 22 is sealed within the primary water cooling coil 19 and so does not fluidly mix with the first air stream 13. The water 22 enters the primary water cooling coil 19 relatively cold. As the water 22 traverses the primary water cooling coil 19 heat thermally diffuses from the first air stream 13 to the water 22 within the primary water cooling coil 19. The water 22 exits the primary water cooling coil 19 relatively warm. The first air stream 13 is therefore cooled by the primary water cooling coil 19. The primary water cooling coil 19 acts as a heat exchanger between the first air stream 13 and the water 22. The cooling of the first air stream 13 corresponds to thermodynamic sensible cooling. As such, the relative humidity of the first air stream 13 is increased by the primary water cooling coil 19 while the moisture content in the air remains constant.

After exiting the primary water cooling coil 19, the relatively warm water 22 is channelled to a primary evaporative cooling device 24. The primary evaporative cooling device 24 is located along the second path 17 directly after the second inlet opening 15. The primary evaporative cooling device 24 is the first component the second air stream 18 intersects after entering the second inlet opening 15. The primary evaporative cooling device 24 may be a conventional direct evaporative cooling device comprising evaporative media or a coil with small tubes or channels or combined (evaporative media and coil/channels).

The primary evaporative cooling device 24 may be made from cellulose, plastic, aluminium or any other suitable material with a separate corrosion resistant coating or material.

In use, the primary evaporative cooling device 24 lowers the temperature of the water 22 and the second air stream 18 by means of liquid water 22 evaporating to form a water vapour. Energy from the water 22 and the second air stream 18 is converted into the latent heat of vaporisation, in other words, the energy absorbed by the liquid water 22 in order to undergo the phase change to a gas. The primary evaporative cooling device 24 may be a combined indirect-direct evaporative cooling device in that comprises water flow in pipes for sensible cooling of the second air stream 18 and then water is sprayed over the coil of the primary evaporative cooling device 24 for evaporative cooling.

The cooled temperature of the second air stream 18 and water 22 after having passed through the primary evaporative cooling device 24 is dependent on the temperature (dry bulb temperature) and relative humidity of the second air stream 18 as this defines the wet bulb temperature of the second air stream 18 as now explained.

Relative humidity is defined as the amount of water in air relative to the maximum amount of water which could be in the air. Relative humidity is dependent on the air temperature, or more specifically the dry-bulb temperature of air, which is the temperature measured by a thermometer exposed to the air but shielded from moisture, in other words, shielded from evaporative cooling effects. The dry bulb temperature of air is considered the thermodynamic temperature as is proportional to kinetic energy of the air molecules. The lower the air temperature, the greater the relative humidity. The wet bulb temperature of air is the temperature measured by a moisture-soaked thermometer with a passing air stream. More specifically, the wet bulb temperature is the lowest achievable temperature for a given relative humidity by means of evaporative cooling. At 100% relative humidity there is no evaporation, so the wet bulb temperature is the same as the dry bulb temperature. At lower relative humidity, the wet bulb temperature is lower due to evaporative cooling.

The drier and less humid the second air stream 18 is, the faster the liquid water 22 evaporates, the greater the evaporative cooling affect resulting in a lower temperature of the second air stream 18 after passing through the primary evaporative cooling device 24. In other words, the lower the relative humidity of the second air stream 18, the greater the cooling of the primary evaporative cooling device 24.

As well as lowering the temperature of the second air stream 18, the primary evaporative cooling device 24 also raises the humidity of the second air stream 18. As such, a very small amount of the warm water 22 channelled into the primary evaporative cooling device 24 is evaporated into the second air stream 18 and the majority of the water is cooled and circulated back directly and or indirectly into the water tank 20. The temperature of the water 22 cooled by the primary evaporative cooling device is substantially equal to or close to the wet bulb temperature of second air stream 18. The recirculated cooled water 22 in the water tank 20 can again be pumped into the primary water cooling coil 19 to cool the first air stream 13 thereby repeating the cycle.

It is noted that instead of or in addition to channelling the water 22 from the primary water cooling coil 19 to the primary evaporative cooling device 24, the water 22 may be expelled from climate control apparatus 7a. The water tank 20 may be filled and or replenished with water 22 from any suitable source. The water 22 makeup may be groundwater, potable water, or recycled water.

The climate control apparatus 7a of Figure 2 further comprises an additional cooling component to cool the first air stream 13 in the form of vapour-compression refrigeration loop 25a sealed within which is a refrigerant 2. The path of the refrigerant 2 is depicted by the solid lines and arrows as can be seen in Figures 3 and 4. The vapour-compression refrigeration loop 25a comprises an evaporator 3, a compressor 4, a primary condenser 5a, a secondary condenser 5b, an expansion valve 6, a first valve 26a, a second valve 26b and a third valve 26c.

The evaporator 3 is located along the first path 12 after the primary water cooling coil 19.

In use, the evaporator 3 transfers heat from the first air stream 13 to the cold, uncompressed, liquid refrigerant 402’ inducing a liquid to gas phase change to form cold, uncompressed, gaseous refrigerant 402”. The cold, uncompressed, gaseous refrigerant 402” is then compressed by a compressor 4 which increases the temperature to form hot, compressed, gaseous refrigerant 402’”.

The hot, compressed, gaseous refrigerant 402”’ is then cooled by the primary condenser 5a. The primary condenser 5a is located along the second path 17 after the primary evaporative cooling device 24. Therefore, the second air stream 18 entering the condenser 5a has already been cooled by the primary evaporative cooling device 24 and so is cooler but more humid than ambient conditions. The primary condenser 5a transfers heat from the hot, compressed, gaseous refrigerant 402”’ to the cooled second air stream 18. The refrigerant 402”’ is cooled and condenses back to a liquid to form a hot, compressed, liquid refrigerant 402””. The second air stream 18 is warmed by the primary condenser 5a raising the temperature back towards or above ambient temperature. In effect, the vapour-compression refrigeration loop 25a acts as a heat pump extracting heat from the first air stream 13 and exhausting that heat in the second air stream 18.

As the second air stream 18 has been cooled by primary evaporative cooling device 24 before entering the primary condenser 5a, this increases the temperature difference between the hot, compressed, gaseous refrigerant 402”’ and the second air stream 18. A greater temperature difference increases the amount of heat transferred between from the refrigerant 402”’ to the second air stream 18 resulting in the condenser 5a being more efficient at cooling the refrigerant 402”’.

The hot, compressed, liquid refrigerant 402”” may optionally be further cooled by the secondary condenser 5b to form warm, compressed, liquid refrigerant 402””’. The secondary condenser 5b is located along the first path 12 after the evaporator 3. The first air stream 13 entering the secondary condenser 5b has already been cooling the primary water cooling coil 19 and the evaporator 3. As such, the temperature of the first air stream 13 entering the secondary condenser 5b may be lower than the temperature of the hot, compressed, liquid refrigerant 402”” exiting the primary condenser 5a. In which case, heat transfers from the refrigerant hot, compressed, liquid refrigerant 402”” to the first air stream, thereby cooling the refrigerant 402””. The primary and secondary condensers 5a, 5b may have any suitable structure such as a tubed coil or a microchannel coil and may be made of any suitable material.

Opening and closing the first and second valves 26a, 26b facilitates altering the arrangement of the primary and secondary condensers 5a, 5b. With both the first and second valves 26a, 26b the secondary condenser 5b may be arranged in parallel with the primary condenser 5a. With the first valve 26a open and the second valve 26b closed, the secondary condenser 5b may be arranged in series with the primary condenser 5a. Alternatively, with first valve 26a closed and the second valve 26b open, the secondary condenser 5b may be by-passed all together.

After passing through the primary condenser 5a, and the secondary condenser 5b depending on the configuration of the first and second valves 26a, 26b, the hot and or warm, compressed, liquid refrigerant 402””, 402’”” is decompressed by an expansion valve 6 decreasing the temperature of the refrigerant to form cold, decompressed, liquid refrigerant 402’. The cold, uncompressed, liquid refrigerant 402’ is circulated back into the evaporator 3 for the refrigeration process to be repeated.

The third valve 26c facilitates by-passing the combination of the primary condenser 5a, the secondary condensers 5a, 5b and the expansion valve 6 or even the combination of the primary condenser 5a, the secondary condensers 5a, 5b, the expansion valve 6 and the compressor 4. The third valve 26c provides additional refrigerant control that can be used in the enhanced dehumidification process or for preventing the overloading the vapour- compression refrigeration loop 25a and the climate control apparatus 7a failing.

The evaporator 3 of the refrigeration loop 25 lowers the temperature of the first air stream 13, increasing the relative humidity until reaching saturation, namely 100% relative humidity. The temperature at which the first air stream 13 cannot support any further water vapour is termed the dew point temperature. At this point, if the first air stream is cooled any further, airborne water vapour condenses. The evaporator 3 lowers the temperature of the first air stream 13 below the dew point temperature thereby condensing water vapour from the first air stream 13 to produce liquid water 22, a condensate. As shown by the dashed line and arrow in Figure 3, this water 22 is channelled into the water tank 20 for circulation into the primary water cooling coil 19. The evaporator 3 provides the dehumidifying functionality of the climate control apparatus 7a. The climate control apparatus 7a may be used to generate water 22 at any time, preferably, at night time when the relative humidity is higher than at day time.

The climate control apparatus 7a may comprise a first fan 27 located after the secondary condenser 5b along the first path 12. The first fan 27 draws the first air stream 13 along the first path 12. Similarly, the climate control apparatus 7a may also comprises a second fan 28 located after the primary condenser 5a along the second path 17. The second fan

28 draws the second air stream 18 along the second path 17. It will be appreciated that the relative location of the first and second fans 27, 28 along the respective first and second paths 12, 17 may vary. For example, the first fan 27 could be located before the primary water cooling coil 19.

The climate control apparatus 7a further comprises a secondary evaporative cooling device 29 located along the first path 12 after the first fan 27. Instead of or in addition to circulating the cooled water 22 exiting the primary evaporative cooling device 24 to the water tank 20, this water 22 may be further cooled by the secondary evaporative cooling device 29 and then circulated into the water tank 20. The secondary evaporative cooling device 29 operates in substantially the same way as the primary evaporative cooling device 24 but with one key difference, namely, the condition of the air incident upon the respective devices 24, 29.

An advantageous effect of the combination of the primary water cooling coil 19, the evaporator 3 and secondary condenser 5b is that the first air stream 13 downstream from the secondary condenser 5b and incident upon the secondary evaporative cooling device

29 is colder, has a lower moisture content and a lower relative humidity from the first air stream 13 immediately upstream of the water cooing coil 19 as well as the second air stream 18 incident upon the primary evaporative cooling device 24. As such, the secondary evaporative cooling device 29 is able to further cool the water 22 exiting the primary evaporative cooling device 24 as the second air stream 18 incident upon the secondary evaporative cooling device 29 facilitates achieving a lower wet bulb temperature than the wet bulb temperature of the first air stream 13. By controlling the amount of water 22 entering the secondary evaporative cooling device 29, the first air stream 13 may be colder, slightly warmer or its temperature remains unchanged. The secondary evaporative cooling device 29 can also cool the water 22 and regulates the humidity of the first air stream 13 by means of evaporative cooling.

The climate control apparatus 7a further comprises a control unit 30, temperature sensors 31 and humidity sensors 32. The temperature and humidity sensors 31 , 32 may be positioned throughout the climate control apparatus 7a monitoring, for example, the first and second air streams 13, 18 at various stages along the respective first and second paths 12, 17 as well as the water 22 in the water tank 20. With the various temperature and humidity readings from the sensors 31 , 32 and the desired output air temperature and humidity, the control unit 30 optimises the operation of the climate control apparatus 7a to achieve the desired conditioning of the first air stream 13.

As an example, if the climate control apparatus 7a is required to cool and dehumidify the first air stream 13, then the control unit 30 may favour operating the evaporator 3, which cools and removes moisture to the first air stream 13, instead of the secondary evaporative cooling device 29, which cools and adds moisture.

Another example, the control unit 30 may favour operating various water flow rates entering the second evaporative cooling device to control the temperature of the water 22 in the water tank. The colder the water 22 the colder the air exiting the primary cooling coil and the overall efficiency also improved especially when more dehumidification (latent load) is required from evaporator 3.

Where there is a choice regarding which components to use to, for example cool the first air stream 13, the control system 30 will favour the primary water cooling coil 19 as opposed to the vapour-compression refrigeration loop 25a as this uses less electricity and so is cheaper to operate.

Figure 5 depicts a portion of an alternative climate control apparatus 7b which may comprise the same preferable and optional features as the climate control apparatus 7a as depicted in Figures 3 and 4. The climate control apparatus 7b of Figure 5 comprises an alternative vapour-compression refrigeration loop 25b. The vapour-compression refrigeration loop 25b comprises a refrigerant 502, an evaporator 3, a compressor 4, a condenser 5 and an expansion valve 6, similar to the vapour-compression refrigeration loop 25a of Figures 3 and 4. Flowever, instead of a secondary condenser 5b, the vapour-compression refrigeration loop 25b further comprises a heat exchanger 33.

The evaporated heats the cold, uncompressed, liquid refrigerant 502’ to form a cold, uncompressed gas or gas-liquid mixture 502”. The heat exchanger 33 exchanges heat between the cold, uncompressed gaseous refrigerant or gas-liquid refrigerant mixture 502” after the evaporator 3 and the hot, compressed, liquid refrigerant 502’”” after the condenser 5. The heat exchanger 33 warms the cold, uncompressed gaseous refrigerant or gas-liquid refrigerant mixture 502” such that it fully evaporates to a warm, uncompressed, gaseous refrigerant 502”’ before entering the compressor 4. This advantageously protects the compressor 4 as this arrangement reduces the likelihood that liquid refrigerant enters the compressor 4.

The compressor 4 compresses the warm, uncompressed, gaseous refrigerant 502”’ to form hot, compressed, gaseous refrigerant 502””. The condenser 5 condenses the refrigerant 502”” to form a hot, compressed liquid refrigerant 502””’. The heat exchanger 33 cools the hot, compressed liquid refrigerant 502””’ to form a cooled, compressed liquid refrigerant 502”””. After which, the expansion valve 6 expands the cooled, compressed liquid refrigerant 502””” to form a cold, uncompressed, liquid refrigerant the 502’. Advantageously, as well as protecting the compressor, the heat exchanger 33 facilitates a greater refrigeration capacity as well as low temperature refrigeration for dehumidification and water production.

The configuration of the alternative vapour-compression refrigeration loop 25b of Figure 5 prevents or mitigates the risk of the climate control apparatus 7b tripping, in other words failing, when the first air stream 13 has a high flow rate with high temperature and or humidity.

Figure 6 depicts an alternative climate control apparatus 7c which may comprise the same preferable and optional features as the climate control apparatus 7a, 7b as depicted in Figures 3 to 5. The climate control apparatus 7c of Figure 6 comprises an alternative vapour-compression refrigeration loop 25c. The vapour-compression refrigeration loop 25c comprises a refrigerant 602, a compressor 4, a condenser 5 and an expansion valve 6. However, instead of the evaporator 3, there is a plate heat exchanger 34 or a heat exchanger incorporated within a thermal store for transferring heat from water 22’ to the refrigerant 2. The water 22’ is circulated, by means of a separate pump (not shown), about a water loop 35 which is a separate, isolated stream of water within the climate control apparatus 7c between the heat exchanger 33 and a secondary water cooling coil 36 which is located along the first path 12 after the primary water cooling coil 19. The secondary water cooling coil 36 receives water 22’ chilled by the vapour-compression refrigeration loop 25c to cool the first air stream 13. As such, the secondary water cooling coil 36 may also be referred to as a secondary chilled water cooling coil 36. The vapour-compression refrigeration loop 25b indirectly cools the first air stream 13 by means of the water loop 35 and the secondary water cooling coil 36. The cooled water 22’ from the plate heat exchanger 34 may also be channelled into a thermal store not shown in the figure to control the chilled water temperature and to provide extra cooling load when required.

The configuration of the climate control apparatus 7c of Figure 6 advantageously enhances the operation of the vapour-compression refrigeration loop 25c, increases the cooling functionality and prevents the climate control apparatus 7c tripping when the first air stream 13 has a high flow rate with high temperature and or humidity. More specifically, controlling the temperature of the water 22’ within the water loop 35 by using water by-pass and or automated reduced air flow rates prevents overloading of the vapour-compression refrigeration loop 25c thereby protecting the climate control apparatus 7c.

Another advantage of this configuration of the climate control apparatus 7c is that the cooled water 22’ circulating about the water loop 35 between the secondary water cooling coil 36 and plate heat exchanger 34 may act as an alternative store of cooled water 22’ which can be channelled to throughout the climate control apparatus 7c as required.

It will be appreciated that the plate heat exchanger 34 could alternatively take the form of any type of heat exchanger with or without a thermal store but an essential aerator and water filling tank may exist. Figure 7 depicts an alternative climate control apparatus 7d which may comprise the same preferable and optional features as the climate control apparatus 7a, 7b, 7c as depicted in Figures 2 to 6. Flowever, instead of the vapour-compression refrigeration loop 25a, 25b, 25c, the climate control apparatus 7d comprises a thermoelectric heat pump 37, also termed a solid state heat pump.

The thermoelectric heat pump 37 operates on the principle of the Peltier effect and comprises a first plate 38, a second plate 39 between which is located alternate pillars of p-type 40 and n-type 41 semiconductors. When an electrical current flows through the thermoelectric heat pump 37, heat is transferred from the first plate 38 to the second plate 39. The thermoelectric heat pump 37 pumps heat away from the first plate 38 thereby cooling the first plate 38.

The thermoelectric heat pump 37 is utilised in the embodiment of Figure 7 to cool the first air stream 13. Water 22’ within a water loop 35 is circulated between the first plate 38 and a secondary water cooling coil 36 which is located along the first path 12 after the primary water cooling coil 19. The water cooling coil 36 extracts heat from the first air stream 13, the water 22’ transfers it to the first plate 38 of the thermoelectric heat pump 37, the thermoelectric heat pump 37 pumps heat to the second plate 39 which is in turn transferred to a hot water heat exchanger 42. Water 22’ within another water loop 35 circulating between the second plate 39 to the hot water heat exchanger 42 transfers heat to the hot water heat exchanger 42. The hot water heat exchanger 42 is located along the second path 17 after the primary evaporative cooling device 24. The hot water heat exchanger 42 exhausts heat into the second air stream 18 of the cools the first air stream 13.

The climate control apparatus 7d of Figure 7 does not comprise a refrigerant and so advantageously can be considered more environmentally friendly. Furthermore, the climate control apparatus 7d of Figure 7 comprising the thermoelectric heat pump 37 is advantageously light weight in comparison to the climate control apparatus of 7a, 7b, 7c of Figures 2 to 6. As an alternative it will be appreciated that the primary and secondary water cooling coils 19, 36 of the climate control apparatus 7d may be combined to form a single water cooling coil with multiple circuits.

Figure 8 depicts an alternative climate control apparatus 7e which may comprise the same preferable and optional features as the climate control apparatus 7a, 7b, 7c, 7d as depicted in Figures 2 to 7. Flowever, instead of comprising a secondary water cooling coil 35, the water 22 from the tank 20 is supplied to the first plate 38 of the thermoelectric cold plate 37. The cooled water 22 then enters the primary water cooling coil 19 then passes to the second plate 39 of the thermoelectric heat pump 37. The hot water exits the hot, second plate 39 of the thermoelectric heat pump 37 and then enters the hot water heat exchanger 42, located along the second path 17 after the primary evaporative cooling device 24. The evaporatively cooled second air stream 18 cools down the hot water 22.

In other words, the hot water heat exchanger 42 exhausts heat transferred to the water 22 from the first air stream 13 to the second air stream 18. The second air stream exits the hot water heat exchanger 42 warmer. The water 22 then enters the primary evaporative cooling device 24 and where it is cooled down to a temperature equal to or close to the wet bulb temperature of the second air stream 18. The water 22 is then controlled to enter the second evaporative cooling device 29 and or to the water tank 20 as explained above.

The advantage of this configuration it uses only one pump and one coil that it reduces weight and costs in addition to the environmentally friendly feature.

Figure 9 depicts an alternative climate control apparatus 7f which may comprise the same preferable and optional features as the climate control apparatus 7a, 7b, 7c, 7d, 7e as depicted in Figures 2 to 8. Flowever, instead of the vapour-compression refrigeration loop 25a, 25b, 25c or even a thermoelectric heat pump 37, the climate control apparatus 7f supplies a secondary water cooling coil 36 with cold water 22’ from an external water supply 43. The external water supply 43 is preferably an external chilled water supply.

The secondary water cooling coil 36, or more specifically, the secondary chilled water cooling coil is located along the first path 12 after the primary water cooling coil 19. The water 22’ from external water supply 43 cools the first air stream 13.

Where a suitable external chilled water supply 43 is available, this advantageously minimises the amount of electricity consumed by the climate control apparatus 7f relative to the other embodiments which have to operate a vapour-compression refrigeration loop 25a, 25b, 25c or thermoelectric heat pump 37.

After passing through the secondary water cooling coil 36, the water 22’ is channelled back to the external water supply 43. Warm water that exits the primary cooling coil 19 may be channelled to the hot water heat exchanger 42 located along the second path 17 after the primary evaporative cooling device 24. The hot water heat exchanger 42 exhausts heat transferred to the water 22 from the first air stream 13 to the second air stream 18. The cooled water 22 is then channelled to the primary evaporative cooling device 24 to be further cooled. After which, the water 22 cycles about the climate control apparatus 7f as previously described and may be directed to the secondary evaporative cooling device 29 or water tank 20.

In a further alternative it is envisaged the climate control apparatus 7f as depicted in Figure 9 could operate without the secondary water cooling coil 36 and or hot water heat exchanger 42 and thus be used as a indirect-direct evaporative cooling device.

In the embodiments of Figures 6, 7 and 8 water 22’ is circulated about a water loop 35 to transfer heat between components. For example, in Figure 7 water 22’ transfers heat between the secondary water cooling coil 36 and the first plate 38. It will be appreciated that any suitable alternative fluid may be used such as antifreeze or any nano fluid.

It will also be appreciated that when described the embodiments of Figure 2 to 9, heat is removed from the first air stream 13 to cool the first air stream 13. Flowever, the first air stream 13 may be heated by, for example, reversing the vapour-compression refrigeration loop 25 or the flow of heat in a thermoelectric heat pump 37.

A key advantage of the present invention is that it minimises the amount of electricity required to operate the climate control apparatus 7 by utilising evaporative cooling. A primary water cooling coil 19 cools a first air stream 13 and the extracted heat is exhausted into a second air stream 18 by means of a primary evaporative cooling device 24. Both the second air stream 18 and water 22 are cooled. In addition to the water 22 is further cooled by a second evaporative cooling device 29 located within the first air stream 13. The second evaporative cooling device 29 enhances the cooling functionality of the climate control apparatus 7 and reach lower temperatures than the primary evaporative cooling device 24 as the second air stream 13 has a lower wet bulb temperature.

Another key advantage is that the evaporative cooling functionality of the present invention can be retrofitted to existing cooling apparatus known in the art. For example, a vapour- compression refrigeration apparatus 1 may comprise a single, first path 12 and cool a first air stream 13 traversing this single, first path 12. However, this apparatus 1 can be retrofitted with a second path 17, a primary evaporative cooling device 24 within the second path 17 and a secondary evaporative device 29 within single, first path 12 to enhance the cooling functionality of know apparatus.

Another advantage is that the climate control apparatus 7 can be used to cool, heat, dehumidify and humidify. Furthermore, the functionality of the climate control apparatus 7 can be computationally optimised by the control unit 30 and automatically adapted due to variation in ambient conditions, for example, throughout the day.

Advantageously, the climate control apparatus 7 can operate in a wide range of climate types and the configuration of the device can be optimised accordingly to the availability of, for example water. Advantageously, the climate control apparatus 7 can be controlled to produce water and reused within the cooling process.

A climate control apparatus is disclosed. The climate control apparatus comprises a first air stream path for a first air stream and a second air stream path for a second air stream. A primary water cooling apparatus is located within the first air stream path and is configured to transfer heat from the first air stream to water. A primary evaporative cooling device is located within the second air stream path and is configured to cool the second air stream and the water from the primary water cooling apparatus. A secondary evaporative cooling device is located within the first air stream path and after the primary water cooling apparatus, the secondary evaporative cooling device is configured to cool the first air stream, humidify the first air stream and or further cool the water from the primary evaporative cooling device. The climate control apparatus can cool, heat, humidify and dehumidify. The operation of the climate control apparatus can be computational optimised. A key advantage is the climate control apparatus is that the configuration requires minimal energy to operate as the evaporative cooling devices do not draw any electricity other than to pump water about the apparatus. Throughout the specification, unless the context demands otherwise, the terms “comprise” or “include”, or variations such as “comprises” or “comprising”, “includes” or “including” will be understood to imply the inclusion of a stated integer or group of integers, but not the exclusion of any other integer or group of integers. Furthermore, unless the context clearly demands otherwise, the term “or” will be interpreted as being inclusive not exclusive.

The foregoing description of the invention has been presented for purposes of illustration and description and is not intended to be exhaustive or to limit the invention to the precise form disclosed. The described embodiments were chosen and described in order to best explain the principles of the invention and its practical application to thereby enable others skilled in the art to best utilise the invention in various embodiments and with various modifications as are suited to the particular use contemplated. Therefore, further modifications or improvements may be incorporated without departing from the scope of the invention as defined by the appended claims.