Patent Application
20170284696
This application claims convention priority from Australian provisional patent application 2014903479 filed on 1 Sep. 2014, the contents of which are hereby incorporated by reference.
The present invention relates to an improved air conditioning system, specifically a direct expansion air conditioning system where air supplied to a conditioned space is directly cooled by a refrigerant supplied evaporator.
Conventional air conditioning design theories were challenged in the 1990's by a series of innovative thoughts developed by the late Dr Allan Shaw. These thoughts culminated with the air conditioning control system described in Dr Shaw's Australian patent 728987. This patent, and the system it describes, is now owned by the present applicant and will be referred to throughout this specification as the “Shaw system”.
The Shaw system is a system that operates air conditioning functions in parallel to separate the process of treating latent loads (typically to remove moisture from outdoor air) and sensible loads (typically internal air which is dry). The Shaw system differs from conventional air conditioning processes in that, rather than drawing untreated outdoor air and then cooling it within the total air conditioning system, incoming outdoor air is pre-treated (dehumidified and cooled) by a first, separate outdoor-air heat exchanger before being merged with typically dry (treated or untreated) inside air that generally has been cooled by a second heat exchanger. The two air streams are merged, to then be delivered to a conditioned space.
Additionally, the Shaw system includes the passage of the same cooling medium stream (typically water) through both heat exchangers, in series, to maximize efficiency.
The Shaw system thus describes broad concepts of two evaporator coils, configured into one refrigeration circuit. However, the description of the method of operation of the refrigeration circuit in Australian patent 728987 is only briefly conceptualised.
An aim of the present invention is to enhance the Shaw system, in particular by providing improved refrigeration componentry and control methodology that more clearly allows for the adoption of the Shaw system in a direct expansion air conditioning system, with the incorporation of additional energy efficiency componentry and control methodology.
Having said that, the present invention also aims to provide an air conditioning system that is well suited to allow compliance with building standards that relate to ventilation amenity in buildings, while at the same time reducing energy usage by the building to desirably low levels.
In this respect, there is increasing importance being placed upon the use of adequate proportions of outside air to provide a building's occupants with a healthy and comfortable environment. Indeed, requirements for the maintenance of CO2 levels in buildings below unhealthy and dangerous levels are increasingly being mandated in countries via local building codes and standards. An example is Standard 62.1 of the ASHRAE 62 Standard titled “Ventilation and Acceptable Indoor Air Quality in Commercial, Institutional and High-Rise Residential Buildings”.
However, the use of higher proportions of outside air (to help achieve compliance with the maintenance of CO2 levels in buildings below unhealthy and dangerous levels), such as by opening dampers by greater extents or for longer periods, typically requires higher energy usage in air conditioning systems, particularly when the ambient conditions include higher temperatures or higher humidity levels. At a time when building owners are also under pressure to reduce overall energy usage, this tension between adequate ventilation with outside air and low energy use is driving the development of improved air conditioning systems.
Before turning to a summary of the present invention, it must be appreciated that the above description of the prior art has been provided merely as background to explain the context of the invention. It is not to be taken as an admission that any of the material referred to was published or known, or was a part of the common general knowledge in Australia or elsewhere.
The present invention provides an air conditioning system, the air conditioning system being capable of treating a conditioned space by treating outdoor air from outside the conditioned space and treating air returned from inside the conditioned space, and mixing the outdoor air with the returned air to form supply air for the conditioned space, the air conditioning system including:
In one form of the present invention, the two evaporators will be configured in parallel so as to separately treat outdoor air and return air. In another form of the present invention, the two evaporators will be configured in series such that the outdoor air is treated by the dehumidification evaporator, the treated outdoor air to then be mixed with untreated return air, with the mixed air stream then being treated by the sensible evaporator. In the preferred arrangement, the evaporators are configured in parallel, which will be the arrangement that is generally described in the following description.
The dehumidification evaporator provides latent cooling to the outdoor air used to ventilate the conditioned space. In a preferred form, air is induced by a system supply air fan and airflow is regulated by an automated damper, with the ambient airflow volume measured by a differential pressure sensor and an included ambient air sensor preferably incorporating carbon dioxide, dry bulb and humidity sensing. Liquid refrigerant flow through the dehumidification evaporator is preferably regulated through the evaporator by automated stop and metering valves.
The sensible evaporator provides sensible cooling to the conditioned space return air. In a preferred form, air is again induced by the system supply air fan with the supply airflow being regulated by a variable frequency drive coupled to the supply air fan, and with the return airflow volume being measured by a differential pressure sensor and an included return air sensor that preferably incorporates carbon dioxide, dry bulb and humidity sensing. Liquid refrigerant flow through the sensible evaporator is again preferably regulated through the evaporator by automated stop and metering valves.
The present invention thus provides the opportunity to control both dry bulb temperature and humidity within the conditioned space by maintaining separation of the airflow associated with ventilating the conditioned space from the airflow required to offset the sensible heat load of the conditioned space. The use of outdoor air, desirable for maintaining ventilation amenity in a building but usually problematic for the energy usage of air conditioning systems, is advantageous and important in a system in accordance with the present invention.
In this respect, as buildings have become more efficient at sheltering the occupied space from ambient conditions, the relationship between the ratio of latent cooling and sensible cooling has increased, typically resulting in elevated humidity within the building, thereby causing discomfort to occupants. In addition to this, the part load operation of conventional direct expansion refrigerated air conditioning systems preferentially satisfies sensible loads over that of latent loads, thereby accentuating the potential for occupant discomfort from elevated humidity within the conditioned space. On the other hand, the present invention enhances the sophistication of refrigeration componentry to the extent that the latent cooling capacity can be separately regulated from the sensible cooling capacity, thus more easily satisfying comfort conditions with the space.
The system of the present invention may also include a liquid refrigerant receiver that stores transitional refrigerant, preferably being able to provide both storage and regulation of liquid flow through the system. Ideally, the liquid refrigerant receiver is capable of performing at least some oil separation (of the compressor oil from the refrigerant) and will also aid in determination of the required compressor refrigerant mass flow rate to meet system load to achieve enhanced flow of refrigerant and oil through the system. In a preferred form, the liquid refrigerant receiver incorporates liquid level sensing, an automated pressure equalization valve and automated oil return valves.
Ideally, the liquid refrigerant receiver is also capable of providing a greater refrigerant mass charge, reducing the potential for an excessive gas compression ratio and improving evaporator heat transfer efficiency by its use as an oil separator. The present invention preferably incorporates a two stage refrigerant oil separation system that reduces oil flow through the system, which increases evaporator heat transfer efficiency, thereby reducing the potential physical size of the evaporators and improves the performance of refrigerant metering valves to more closely approximate capacity delivery to offset the presented heat load.
Such a two stage refrigerant oil separation system will ideally include a first stage hot gas (oil) separator and a second stage cool liquid (oil) separator, the latter being provided, in a preferred form, by the liquid refrigerant receiver. In this form, both separators return separated oil to the compressor via suction gas refrigerant. In this respect, the traditional use of reduced capacity liquid receiving devices (or the total omission of such devices) in small space, air cooled, direct expansion air conditioning systems reduces the mass of refrigerant within the system, rendering the mass charge more important in the performance of the system and providing an improvement to the energy efficiency of the system over time.
The present invention thus provides not only relative independence of control of latent and sensible capacity delivery through its inclusion of dual evaporators, but it also enhances the variability of capacity delivery through the separation of control of the refrigerant mass flow by the compressor, determined by space loads, to the volumetric use of liquid refrigerant within the system, by the inclusion of the liquid refrigerant receiver and its preferred role as a second stage oil separator. In this respect, it will be appreciated that the present invention ideally meters refrigerant mass flow on the basis of evaporator loads and not the quality of suction gas. This permits the suction gas to return to the compressor with a higher rate of super-heat, thereby enhancing the refrigerant mass flow refrigeration effect.
The present invention preferably also utilizes refrigerant temperature sensing to provide heat rejection relative to the potential for cooling from the ambient dry bulb temperature and the potential for liquid refrigerant sub cooling to enhance the refrigeration effect from the potential for cooling from the ambient wet bulb temperature. In a preferred form, the system of the present invention includes a sub-cool heat exchanger to reject heat into the local ambient air to sub cool liquid refrigerant. In one form, the sub-cool heat exchanger can incorporate an adiabatic pre-cooling media, or a progressive indirect adiabatic cooling process, together with a fan to move air through the condensers, a refrigerant temperature sensor and a variable performance drive to regulate the mass flow rate of the fan.
The refrigeration effect of the system of the present invention may be further enhanced through the reclaim of energy from the latent cooling load to super cool the heat of rejection to approach the evaporator operating temperature. A reduction of the temperature of the liquid refrigerant feeding the evaporators enhances the potential refrigeration effect, resulting in a reduced compressor mass flow rate. In this respect, the system of the present invention may also include a system for the capture and utilization of latent cooling condensate to regain energy associated with the latent cooling process, preferably in the form of a super-cool heat exchanger to super cool liquid refrigerant utilizing condensate collected from the dehumidification evaporator of the outdoor air latent cooling treatment stage.
The system of the present invention thus ideally provides a three stage heat of rejection process that incorporates an ambient condenser, the sub-cool heat exchanger and the super-cool heat exchanger to achieve an enhanced refrigeration effect for the circulating refrigerant mass flow rate. The use of such a three stage heat of rejection process incorporating super cooling from the system latent cooling load as determined by the space humidity sensor, and the decoupling of the compressor suction condition from direct management of the refrigerant flow rate, assists to enhance the utilization of the refrigeration effect potential of the low pressure transition from sub-cooled liquid to super-heated gas.
Furthermore, through the preferred use of dry bulb, wet bulb and suction temperature super cooling control of head pressure and load determined evaporator temperature, and suction super-heating, a resulting increase in refrigeration effect is seen with reduced compression ratios. This reduces the energy required to develop refrigerant compression, thereby improving the compressor refrigeration coefficient of performance.
Before turning to a more detailed description of a preferred embodiment of a direct expansion air conditioning system in accordance with the above broad descriptions, it will thus be appreciated that the system of the present invention provides cooling to a conditioned space that manages both dry bulb temperature and moisture content to enhance occupant comfort.
In one preferred form described above, the system ideally utilizes ambient dry bulb, ambient vapour pressure and reclaim of space latent cooling to reduce the condensing temperature associated with low pressure expansion to extend the refrigeration effect of the compressor mass flow rate.
In another preferred form described above, the system alternatively or in addition utilizes a liquid receiver to de-couple compressor mass flow from variable heat load requirements, thereby reducing compressor discharge pressure and permitting enhanced utilization of refrigerant gas super heat within the evaporators.
In yet another preferred form described above, the system alternatively or in addition utilizes a two stage compressor oil separation process to enhance heat transfer of both the condenser and evaporators, and alternatively or in addition utilizes ambient and conditioned space sensors to regulate the rate of introduction of outdoor air for amenity and the rate of supply air circulation to deliver cooling to the space.
The adoption of some or all of these preferred forms in a direct expansion air conditioning system broadly in accordance with the present invention reduces energy consumption associated with providing the required levels of comfort and amenity (particularly with regard to ventilation) for occupants of a conditioned space.
Having briefly described the general concepts involved with the present invention, a preferred embodiment of a direct expansion air conditioning system will now be described that is in accordance with the present invention. However, it is to be understood that the following description is not to limit the generality of the above description.
In the drawings,
In general terms, shown in the flow diagram of
The cooling process for the return air stream Y is principally sensible cooling, which is conducted in the return air sensible cooling treatment stage represented in this embodiment by a sensible evaporator H placed in the return air stream Y. The cooling process for the outdoor air stream X is principally latent cooling, which is conducted in the outdoor air latent cooling treatment stage represented in this embodiment by a dehumidification evaporator G placed in the outdoor air stream X.
As will be outlined in the following tabular description of the various components in the preferred embodiment, the thermal capacity of the dehumidification evaporator G is regulated in response to a desired conditioned space humidity set point, together with a load driven variance from that set point. Also, the thermal capacity of the sensible evaporator H is regulated in response to a desired conditioned space dry bulb temperature set point, together with a load driven variance from that set point.
The following table (Table 1) provides a more detailed explanation of the various elements illustrated in the flow diagram of
It will be appreciated that Table 1 above describes the different air conditioning componentry that makes up the physical form of the preferred embodiment. The following table (Table 2) describes the logic algorithms that form the basis of the control of the preferred embodiment.
As will be appreciated from Table 1 and Table 2, the use of evaporators to separately manage space dry bulb and space humidity enhances occupant comfort, while the use of control algorithms to regulate liquid refrigerant to the evaporators in response to space load conditions enhances the utilization of evaporator heat transfer capabilities to extend the refrigeration effect of the circulating refrigerant mass flow. Also, the preferred use of sub-coolers and super-coolers in the heat of rejection condensing process extends the refrigeration effect of the circulating refrigerant mass flow and reduces compressor head pressure, and the preferred use of liquid refrigerant sensing decouples the volumetric dependence of compressor head pressure from compressor suction pressure.
In conjunction with the preferred use of liquid refrigerant metering valves and suction gas set point management, the adoption of these components configured in the manner described enables evaporators to operate at higher saturation temperature, thereby reducing compressor pressure lift requirements for generation of an enhanced refrigeration effect.
Additionally, the preferred use of volumetric calculation of outdoor air flow and supply airflow in response to feedback signals to provide ventilation amenity and space comfort, reduces both heat load and air circulation energy consumption.
A person skilled in the art will understand that there may be variations and modifications other than those specifically described. It is to be understood that the invention includes all such variations and modifications. The invention also includes all components, steps, functions and features referred to, or indicated in this specification, individually or collectively, and any and all combinations of any two or more of those components, steps, functions and features.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2014903479 | Jan 2014 | AU | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/AU2015/000522 | 8/28/2015 | WO | 00 |
