VAV reheat versus active chilled beams & DOAS.
Three mechanical engineering firms with offices in the Bay Area provided a Design Development (DD) level design for a real office building currently in design, the UC Davis Medical Center Graduate Studies Building (GSB) in Davis, Calif. One firm designed an ACB+DOAS system, another firm designed a VAVR system, and the third designed a hybrid combination of these two systems. A fourth engineering firm simulated each of the three designs using the EnergyPlus energy simulation program. Finally, a major mechanical contractor provided a detailed HVAC construction cost estimate for each design.
The VAV reheat system had the lowest first costs and the lowest energy costs of the three systems. The analysis showed that many of the supposed advantages of ACB+DOAS relative to VAVR, such as improved indoor air quality and a lower floor/floor height, also turned out to be largely overstated. Note that the results of this analysis are only strictly applicable to these three designs and this building and climate, but the conclusions also may apply more broadly.
Genesis of Competition
The UC Davis Medical Center Graduate Studies Building (GSB) will be a 56,500 [ft.sup.2] (5249 [m.sup.2]) office building. The space program is fairly evenly split between private offices, open offices and classroom/conference rooms. Chilled water and hot water will be provided by the campus central plant.
When UC Davis first decided to build the GSB, it started with a traditional plans/specifications approach with Firm A as the engineer-of-record. Firm A, which has designed more than 1 million [ft.sup.2] (92 900 [m.sup.2]) of chilled beam buildings, chose an ACB+DOAS design. In early 2012, when the design was in the design development (DD) stage, the owner decided to switch to a design/build approach, and Firm A's design became the bridging documents.
One of the design/build teams bidding on the project proposed a VAVR system (designed by Firm B, the authors' firm) and also carried the design through about the DD level in its bid. Another bidder proposed a hybrid chilled beam + VAV reheat system, designed by Firm C. The three designs included equipment schedules, detailed equipment layouts and zoning plans. The team with the hybrid design was awarded the job, but the project has been placed on hold since.
After UC Davis selected a design/build team, the ASHRAE Golden Gate chapter decided to use this building for a competition between chilled beams and VAV reheat since it had already been designed with both systems and with a hybrid combination of the two. All three firms were eager to participate. The results of the competition were presented at a seminar sponsored by the ASHRAE Golden Gate Chapter at the Pacific Gas & Electric Energy Center in San Francisco on Oct. 17, 2012.
Active Chilled Beam Design
The ACB+DOAS design consists of a 100% outside air, constant volume air handler serving two supply risers. The air handler has a chilled water coil with a bypass damper and a hot water coil. The air handler has a variable speed drive primarily for reducing fan speed when the bypass damper is open. The air handler provides the primary air to the active chilled beams. The average DOAS primary airflow rate is about 0.6 cfm/[ft.sup.2] (0.28 L/ [s x [m.sup.2]]), which is considerably higher than the minimum ventilation in low occupant density spaces, like offices, but close to the minimum ventilation in higher density spaces such as conference rooms and classrooms. A DOAS flow rate higher than the minimum ventilation in low density spaces is often needed to meet the space loads as the capacity of the chilled beams is a function of the primary airflow rates. In densely occupied spaces, it also ensures space dew point does not rise above the surface temperature of the chilled beams, possibly causing condensation. It also improves the indoor air quality compared to code minimum ventilation.
Hot water and chilled water are provided by an existing campus central plant supplying 45[degrees]F (7[degrees]C) chilled water to the buildings on campus. However, 45[degrees]F (7[degrees]C) typically cannot be supplied to the chilled beams because of the likelihood of condensation and dripping. Therefore, the ACB design includes one set of chilled water pipes supplying 45[degrees]F (7[degrees]C) chilled water to the air handler and a separate chilled water heat exchanger and chilled water pump in the building to maintain the chilled water supply temperature to the chilled beams at 57[degrees]F (14[degrees]C). The design engineer felt that a heat exchanger was needed, rather than just a blending valve, as an added layer of protection against condensation.
Each ACB has both heating and cooling coils. The primary air is maintained at 63[degrees]F (17[degrees]C), and the ACB heating and cooling coils are controlled by the thermostat to maintain space conditions.
The ACB design also includes a partially ducted exhaust system--exhaust ducts extend from the air handler down the shafts and into the ceiling return plenum about two thirds of the way from the exhaust shafts to the building skin. This was in response to perceived owner preference for ducted return. However, neither of the other two designs in the design/build competition included ducted return and, therefore, the return ductwork was not included for any design in the cost model or energy model for the Golden Gate ASHRAE Chapter competition.
VAV Reheat Design
The VAVR design includes a single VAV air handler with a cooling coil and an airside economizer. Unlike the ACB design, which had two supply risers, the VAVR design only has one supply riser. The air handler is sized for about 0.9 cfm/[ft.sup.2] (4.5 L/[s x [m.sup.2]]), at design conditions. There is no return ductwork, even in the return shaft, and building relief is accomplished with two propeller relief fans.
All zones are served by VAV boxes, most of which have reheat coils. Zones that serve open plan interior spaces that are open to perimeter zones do not have reheat coils because minimum ventilation for both the interior and perimeter can be provided by the perimeter zone reheat box (Figure 5). The cooling-only VAV boxes have zero minimum flow rates. The reheat boxes use a dual maximum zone control sequence (5) with minimum flow rates in the deadband between heating and cooling of about 0.15 cfm/[ft.sup.2] (0.07 L/[s x [m.sup.2]]). High occupant density spaces, such as conference rooms and classrooms, have C[O.sub.2] controls that also allow these spaces to have minimum flow rates in deadband of about 0.15 cfm/[ft.sup.2] (0.07 L/[s x [m.sup.2]]) dynamically reset upwards based on C[O.sub.2] concentration.
The air handler supply air temperature is reset from 55[degrees]F to 65[degrees]F (13[degrees]C to 18[degrees]C) using zone feedback to provide supply air just cold enough to satisfy the worst-case zone. Similarly, duct static pressure setpoint is reset to maintain the worst-case zone damper nearly wide open. (6)
The Hybrid system includes a single VAV air handler with a chilled water coil and airside economizer ducted to two supply risers. Interior zones are served by conventional VAV reheat boxes because adding chilled beams to these low load zones would not significantly reduce primary airflow rates. Similarly, conference rooms and classrooms, which have relatively high peak ventilation rates, are served by conventional reheat boxes with C[O.sub.2] controls. Chilled beams are only provided in low density perimeter zones where the chilled beams allow significant reduction in the primary airflow rates. Thus about 70% of the total area is conventional VAV reheat and about 30% is hybrid VAV + ACB. The air handler is designed for about 0.7 cfm/[ft.sup.2] (0.33 L/[s x [m.sup.2]]). and 55[degrees]F (13[degrees]C) supply air temperature. Like the VAV reheat design, the air handler controls include supply air temperature reset and duct static pressure reset.
The chilled beams are two pipe, cooling-only beams, rather than four pipe beams. Heating is provided by VAV reheat boxes that serve the chilled beams (Figure 7). As with the ACB+DOAS Design, one set of 45[degrees]F (7[degrees]C) chilled water pipes serve the AHU and a second set of 57[degrees]F (14[degrees]C) chilled water pipes serve the chilled beams.
Each of the three designs was simulated with EnergyPlus. EnergyPlus was chosen because it has an explicit chilled beam module. Other simulation programs such as EnergyPro and eQUEST do not have a chilled beam module and, therefore, typically approximate chilled beams with induction units. EnergyPlus does not explicitly allow chilled beams served by VAV reheat boxes. Therefore, the hybrid design was approximated using two systems serving the ACB zones: VAV with HW reheat boxes and four-pipe fan coil units with zero zone fan energy operating in sequence; whatever load the VAV box could not meet was met by the four-pipe fan coil.
Lighting power density was modeled using the prescriptive requirements of ASHRAE Standard 90.1-2007. Occupant density and receptacle power density was modeled using the defaults in ASHRAE Standard 90.1-2007 User's Manual Table G-B (e.g., 275 [ft.sup.2]/person and 0.75 W/[ft.sup.2] for offices [26 [m.sup.2]/ person and 8.0 W/[m.sup.2]]). Schedules for HVAC, lighting, occupants and receptacles were modeled using the defaults in User's Manual Tables G-E to G-M.
The campus central cooling and heating plants are modeled per the baseline modeling assumptions in Standard 90.1-2007 Appendix G for chilled water and hot water plants.
The results of the EnergyPlus simulations are shown in Figure 9. The VAV reheat design uses 40% less HVAC energy than the ACB design, and the hybrid design uses 33% less HVAC e nergy than the ACB design. The VAV reheat savings relative to the ACB design are across the board: VAV reheat has 28% less cooling energythan ACB, 70% less heating energy, 60% less fan energy, etc.
Understanding Simulation Results
Further analyses of the designs reveal that the simulation results are not surprising.
Table 1 shows VAV reheat design has about 40% higher fan power at design conditions than the ACB+DOAS design. However, the ACB+DOAS fan power is constant at part load while the VAV reheat fan power goes down very quickly at part load (thanks to the near cube law relationship between fan speed and fan power).
As Figure 10 shows, the VAVR design uses less fan power than the ACB+DOAS design whenever the part load ratio (airflow fraction required to meet the load) is less than about 83%, which is almost all of the time. The annual average airflow rate in the VAV reheat simulation was about 60% of peak flow, which explains why the VAV reheat design used less than half of the fan energy of the ACB+DOAS design. Figure 10 also shows that even if the ACB+DOAS design had been reduced to 0.3 cfm/[ft.sup.2] (0.14 L/[s x [m.sup.2]]) it would still use more fan energy compared to a VAVR system with an average annual flow rate of 60%. A primary airflow rate of 0.3 cfm/[ft.sup.2] (0.14 L/[s x [m.sup.2]]) is about the lowest possible with an ACB+DOAS system to meet latent loads with the primary air and the sensible loads with the chilled beams. Furthermore, there is reason to believe that the 60% average part load ratio in the EnergyPlus model is probably unrealistically high. The default ASHRAE schedules for office occupancy call for a nearly constant occupancy schedule of 95% and a nearly constant lights and receptacles schedule of 90%. ASHRAE Research Project 1515 (7) suggests that realistic schedules are smaller than this and that a realistic annual average part load ratio for office buildings is closer to 40% than 60%. (7) At 40% part load ratio, the 0.5 cfm/[ft.sup.2] (0.24 L/[s x [m.sup.2]]) ACB+DOAS design uses six times as much fan energy as the VAVR design and the 0.3 cfm/[ft.sup.2] (0.14 L/[s x [m.sup.2]]) ACB+DOAS design uses four times as much.
In non-economizer conditions (outside air temperature > return air temperature), the ACB+DOAS design has a higher cooling load than the VAVR design because it has a higher outside air load (0.5 cfm/[ft.sup.2] [0.24 L/(s x [m.sup.2])]) compared to 0.15 cfm/[ft.sup.2] [0.07 L/[s x [m.sup.2]]). In economizer conditions, the ACB+DOAS design also has higher mechanical cooling loads because it does not have an air economizer while the VAVR design does have an air economizer and thus benefits from economizer free cooling. The ACB+DOAS design also has higher reheat/recool loads than the VAVR design because the fixed primary airflow rate (0.5 cfm/[ft.sup.2] [0.24 L/(s x [m.sup.2])]) and fixed supply air temperature (63[degrees]F [17[degrees]C]) mean the ACB+DOAS design is always providing about 6 Btu/h-[ft.sup.2] (19 W/[m.sup.2]) of cooling even when the actual load is lower. The VAVR design, on the other hand, provides no more than about 3 Btu/[h.sup.*][ft.sup.2] (9 W/[m.sup.2]) at minimum flow, even if the supply air temperature is fixed at its minimum of 55[degrees]F (13[degrees]C). Therefore, the ACB+DOAS design has a higher cooling load under all conditions compared to the VAVR design.
In this building, all mechanical cooling loads are met by the campus central plant, so the cooling efficiency is the same for all three designs. Therefore, the ACB+DOAS design must have higher cooling energy than the VAVR design; the loads are higher and the cooling plant efficiency is the same (or worse when pump energy is included). To take advantage of the warmer chilled water supply temperature required by the chilled beams, a medium temperature chilled water plant is required, preferably with an integrated water-side economizer. One lesson learned from this analysis is that connecting to a 45[degrees]F (7[degrees]C) central plant loses all cooling efficiency benefits of medium temperature systems such as chilled beams or radiant cooling.
Similar to cooling energy, the ACB+DOAS design has to use more heating energy than the VAVR design because the zone reheat load is higher, as described previously, and because the outside air heating load is higher. In the winter, the ACB+DOAS design must heat 0.5 cfm/[ft.sup.2] (0.24 L/[s x [m.sup.2]]) of outside air while the VAVR design only has to heat 0.15 cfm/ [ft.sup.2] (0.07 L/[s x [m.sup.2]]) of outside air, three times as much outside air load.
Also, as with the cooling loads, the heating loads are met by the campus central plant, so the heating efficiency is the same for all three designs. Therefore, it is not surprising that the ACB+DOAS model uses more than twice as much heating energy as the VAVR model. To take advantage of the reduced temperature hot water required by the chilled beams in heating mode, a condensing boiler plant is required. As with cooling, connecting to a conventional central plant loses all heating efficiency benefits of chilled beams. Note that the VAVR design and the hybrid design can also take advantage of condensing boilers, but not to the extent of the ACB+DOAS design, because they have smaller hot water coils.
HVAC Cost Model
A major mechanical contractor used the DD level drawings of each design to estimate the HVAC installed costs for each design. As noted previously, the cost of the return ductwork on the floors and in the return shaft in the ACB+DOAS design was not included in the cost estimate because return ductwork is not required for the ACB+DOAS design and was not included the other two designs. As shown in Table 2, The ACB+DOAS design costs more than twice as much as the VAVR design and the Hybrid Design is about half way between the other two. The ACB+DOAS design is so much more expensive that even if it used no HVAC energy at all it would still take 80 years to pay back the incremental first cost compared to VAVR.
The cost breakdown in Table 2 sheds some light on the cost differential. The VAVR design uses 30% more sheet metal than the ACB+DOAS design, but the ACB+DOAS design uses 30 times more chilled water piping and five times more hot water piping. One reason the VAVR hot water piping costs are so much lower is because the VAV boxes are grouped close to the duct mains to minimize hot water piping (Figure 5). In the ACB+DOAS design, the hot water piping must run out to every chilled beam. The ACB+DOAS equipment cost is double the VAVR equipment cost. This is due primarily to the cost of the active chilled beams and to the added pumps and heat exchanger used for the secondary chilled water circuit. The ACB+DOAS subcontractor cost also is double the VAVR subcontractor cost. This is due to the higher controls costs (e.g., more chilled water valves, humidity sensors, etc.), higher insulation costs (for all that extra piping) and higher test and balance costs.
Many other potential costs are not included in these figures that could make the ACB+DOAS design even more expensive relative to VAVR. One example is seismic bracing for the chilled beams. General contractors have reported that they have been caught off guard by the amount of seismic bracing required for chilled beams and the resultant impact on other utilities. Another potential additional cost is lighting. The chilled beams take up much more ceiling space than conventional diffusers. This increases the cost of coordination between mechanical and electrical trades and potentially the cost of lighting fixtures.
The VAVR system was clearly better on both energy efficiency and HVAC costs compared to the ACB+DOAS system, but what about the other supposed advantages of ACB+DOAS?
The impact of the HVAC system on the floor-to-floor height is primarily a function of the size of the supply mains on the floors. The bigger the mains, the more floor-to-floor height is required. Other HVAC components, such as VAV boxes, rarely affect the floor-to-floor height because they are usually smaller than the mains and can be tucked up between beams while supply mains must run under the beams.
On a typical floor of the GSB, the ACB+DOAS design has four supply mains each sized at 40 x 12 in. (1 x 0.30 m), for a total supply main area of 13 [ft.sup.2] (1 [m.sup.2]) per floor (Figure 11). On the same floor, the VAVR design has one 54 x 16 in. (1.37 x 0.40 m), main and one 30 x 16 in. (0.76 x 0.40 m), main for a total supply main area of 9 [ft.sup.2] (0.8 [m.sup.2]) (Figure 12). So in this case the ACB+DOAS design has larger supply mains and thus has no advantage in terms of floor-to-floor height.
The ACB+DOAS supply mains are larger because they are sized for a lower velocity. To mitigate the fan energy penalty of a constant volume system relative to a VAV system, an ACB+DOAS system must use lower duct velocities compared to a VAVR system. In this case, the VAVR supply mains are sized at about 2,000 fpm (10 m/s) while the ACB+DOAS mains are sized at about 900 fpm (5 m/s). VAVR mains can be sized for a higher velocity because they are variable volume, and the actual flow rate is almost always well below the design flow. VAVR supply mains can be sized up to about 2,500 fpm (13 m/s) with minimal impact on annual fan energy or noise risk.
An ACB+DOAS design might have a floor-to-floor advantage over VAVR with different design choices. For example, if the ACB+DOAS system had been designed for 0.3 cfm/ [ft.sup.2] instead of 0.6 cfm/[ft.sup.2] and the duct mains sized at 1,500 fpm, then the duct mains would be about 30% smaller than a comparable VAVR system sized at 2,500 fpm. Of course, an ACB+DOAS system at 0.3 cfm/[ft.sup.2] and 1,500 fpm (0.14 L/[s x [m.sup.2]] and 8 m/s) would still have more than double the annual fan energy of a VAVR system at 0.9 cfm/[ft.sup.2] and 2,500 fpm (0.42 L/[s x [m.sup.2]] and 13 m/s) (see Figure 10).
Indoor Air Quality
Proponents of ACB+DOAS argue it provides better indoor air quality than VAVR because it uses higher design ventilation rates. What this argument fails to capture, however, is the IAQ benefits of the airside economizer in a VAVR design. As part of the competition, a detailed eQuest simulation of the GSB was performed to determine how the ventilation rates of the designs compared to each other and to ASHRAE Standard 62.1 in every space and every hour of the year. (5)
Figure 13 shows the actual outside airflow in the VAVR design met or exceeded the outside airflow required by Standard 62.1 every hour of the year and the annual average outside airflow is 260% larger than Standard 62.1 rates including multiple space inefficiencies. Figure 13 also shows a DOAS system at 0.6 cfm/[ft.sup.2] (0.28 L/[s x [m.sup.2]]) does provide more outside air than a VAVR system averaged over a year but a DOAS system designed at 0.3 cfm/[ft.sup.2] (0.14 L/[s x [m.sup.2]]) does not. Ventilation for the hybrid design was not simulated, but it will be worse than the VAVR because it has the same design minimum outside airflow rate but less economizer benefit because of the lower airflow rates in the chilled beam zones.
Another IAQ issue related to chilled beams is the potential for mold and mildew growth due to condensation on chilled beam cooling coils. While ACB systems are designed not to condense, condensation can occur due to humidity sensor drift, incorrectly programmed control sequences, building engineers unfamiliar with chilled beams, unexpected space latent loads, etc. VAVR, of course, is not vulnerable to this potential IAQ risk. Another downside of ACB systems is that they do not work well with operable windows because of the risk of humid outside air condensing on the chilled beams. Chilled beams are available with vertical coils and condensate drip pans, but this can reduce capacity per foot (at the same water temperature), so more linear feet of beam is required, further increasing the cost and, of course, there is the cost of piping all the drip pans to drains.
LEED Energy Points
There is one area the ACB+DOAS design significantly outperformed the VAVR design: LEED energy points. How could a system that uses twice as much HVAC energy score more LEED energy points? The answer is that the two systems are not compared to the same baseline model by EnergyPro, the software most commonly used to demonstrate compliance with the California Title 24 energy code and to determine LEED energy credits. The Title 24 modeling rules state the baseline model shall have the same outdoor air ventilation rate as the proposed model. EnergyPro interprets this to mean the same percentage of outside air. EnergyPro also considers ACB+DOAS to be a single zone system and thus compares it to constant volume, 100% outside air, packaged single zone units. On the other hand, EnergyPro compares the VAVR design to a packaged VAV reheat system with the same minimum ventilation rate.
Figure 14 shows the ACB+DOAS design uses 25% less HVAC energy than its EnergyPro-generated baseline while the VAVR Design only uses 15% less HVAC energy than its baseline. However, it also shows the ACB+DOAS baseline is three times higher than the VAVR baseline! Fortunately, the California Energy Commission is currently revising the Title 24 modeling rules so that the HVAC design and ventilation rate in the baseline model are fixed regardless of the proposed HVAC design or proposed ventilation rate.
Other Downsides of ACB versus VAVR
Water Leaks. In addition to the condensation risk, ACB systems also have a much higher risk of chilled and hot water leaks than VAVR systems because they have so much more piping, particularly over tenant spaces.
Maintenance. It is possible with VAVR systems to locate many boxes in corridors or non-critical spaces outside the zones they serve, so that maintenance or repairs can be done without disrupting the occupied space; but no such option exists for ACBs.
Lighting. Lighting quality and efficiency may be compromised due to restrictions in fixture location imposed by chilled beams.
Flexibility for Future Tenant Improvements. Rigidly secured and piped chilled beams are much more expensive to relocate than VAVR diffusers, which do not require seismic bracing and are generally connected with flex duct. Not only will HVAC cost be higher for tenant improvements but other trades' costs are also likely to be higher as a result of the "forest" of seismic bracing supporting the ACBs.
LEED EQ Credit 5 (Indoor Chemical and Pollutant Source Control). This credit is generally achievable with a VAVR system since it requires that all supply air be filtered, but not with an ACB system because the secondary air induced through chilled beams is unfiltered.
Thermal Comfort. When the zone minimum cooling output exceeds the cooling load then the zone is overcooled and driven to the reheating setpoint (e.g., 70[degrees]F [21[degrees]C]). When the minimum zone output is less than the zone load, the space temperature drifts up to the cooling setpoint (e.g., 74[degrees]F [23[degrees]C]). Most people are more comfortable at the cooling setpoint than at the heating setpoint in the summertime when they are wearing summer attire. (7) Therefore, reducing the zone minimum cooling output improves comfort. As discussed earlier, the ACB+DOAS design has a higher minimum zone cooling output than the VAVR design and is likely to be less comfortable.
In this competition, VAVR is the clear winner, but are there other applications or designs for which ACB+DOAS or a hybrid design using ACB would be lower first cost or lower energy cost?
Lower Primary Airflow. An ACB+DOAS primary airflow rate of 0.3 cfm/[ft.sup.2] (0.14 L/[s x [m.sup.2]]) instead of 0.5 or 0.6 cfm/[ft.sup.2] (0.24 or 0.28 L/[s x [m.sup.2]]) would reduce the cooling load in hot weather, and the reheat load in cold weather but it would increase the cooling load in mild weather (less free cooling). The net result would likely be a lower annual energy use than 0.6 cfm/[ft.sup.2] (0.28 L/[s x [m.sup.2]]), but would lowering the primary airflow rate allow the beams to achieve the necessary cooling capacity and provide sufficient latent capacity and meet the air quality objectives?
Two-Pipe Chilled Beams. Using a two-pipe beam that can switch between heating and cooling, rather than a four pipe beam, would reduce first costs but not enough to make ACB less expensive than VAVR, and it would have no real impact on energy performance.
ACB+Recirculation. What if an airside economizer was added to the ACB+DOAS design so that the system remained constant volume at 0.5 cfm/ [ft.sup.2] (0.24 L/[s x [m.sup.2]]), but the outside airflow component could be modulated between 0.15 cfm/[ft.sup.2] and 0.5 cfm/[ft.sup.2] (0.07 L/[s x [m.sup.2]]) and (0.24 L/[s x [m.sup.2]]) to minimize the heating and cooling penalty of the higher flow rates? This scenario was simulated with EnergyPlus during the competition. As expected, the ACB+Recirculation energy use went down but still was considerably higher than the VAVR energy use, and the ACB+Recirculation is even more expensive with the economizer. And, of course, the system is no longer DOAS and, therefore, loses most of the supposed advantages of DOAS.
Heat Recovery. What if, instead of an air economizer, the ACB design included a heat exchanger between the exhaust air and the outside air? In many climates, like most of California, the added supply and exhaust fan energy from the added pressure drop of the heat exchanger would outweigh most or all of the energy savings from heat recovery. Even if heat recovery was a net energy saver it would not save as much as the previous ACB+Recirculation option, which is still less efficient than VAVR. And, of course, adding heat recovery only makes ACB+DOAS more expensive.
Waterside Economizer. A waterside economizer will not help the ACB+DOAS design catch up to VAVR in terms of fan energy or mechanical cooling load, but it will allow the ACB+DOAS to meet the cooling load more efficiently. However, a waterside economizer is usually less efficient than an airside economizer due to the cooling tower and pump energy required and due to the fact that it has three temperature approaches (compared to no approaches for an air economizer) that determine when the economizer is available and what fraction of the load it can serve. There is the approach of the tower to the ambient wet bulb (which gets worse as the wet bulb goes down), the approach across the heat exchanger, and the approach from the chilled beam to the supply air. Chilled beams also generally have a low chilled water [DELTA]T (e.g., 6[degrees]F [3[degrees]C]), which limits waterside economizing.
Multiple Chillers. To have any chance of competing with a VAVR system on energy use, the ACB+DOAS design must have separate high and low temperature chillers--low temperature (e.g., 45[degrees]F [7[degrees]C]) chillers to serve the air handlers and high temperature chillers (e.g., 57[degrees]F [14[degrees]C]) to serve the chilled beams. This will improve the mechanical cooling efficiency of the ACB design, but will also significantly increase the first cost and complexity of the system.
Other Hybrid Designs. The hybrid design in this competition failed to compete with the VAVR design on energy or first cost, but there are other hybrid designs that might fare better. Livchak suggests adding parallel or series fan-powered boxes to the ACB to reduce primary air. (8) Although this will reduce the heating/ cooling penalties associated with high primary air, it will also increase fan energy and maintenance (due to all the small fans) and will likely not result in lower total energy than VAVR and will reduce indoor air quality. It will also significantly increase the first cost of the ACB design, which as noted earlier would already take 80 years to pay for itself even if it used no energy at all.
In this competition, VAVR was the clear winner versus ACB+DOAS. VAVR had much lower first costs, much lower energy costs, and similar floor-to-floor heights. These conclusions strictly apply only to the analyzed systems and this building, which is in a relatively mild climate. However, in the last five years the authors' firm has conducted detailed life-cycle cost analyses comparing several ACB variations to VAVR for several buildings across the country and has yet to come across a single case where ACB was more efficient or lower cost.
The authors' firm has also reviewed life-cycle cost analyses by other firms that appear to have gone out of their way to make VAVR look bad by using unnecessarily high design flow rates and static pressures, single maximum zone controls with high minimums, fixed supply air temperature, etc. A common technique to inflate the VAVR energy use is to make it minimally compliant with Standard 90.1-2004 or 90.1-2007, conveniently ignoring the facts that 90.1 has raised the bar for VAVR since 2007 and that a good VAVR design can far exceed 90.1. A well-designed VAVR system (including dual maximum zone controls, supply air temperature reset, duct static pressure reset and C[O.sub.2] controls in high density spaces) is hard to beat. Many others engineers have come to similar conclusions. (9)
It is possible an ACB design with low primary airflow and with medium temperature chilled water and a waterside economizer might be more efficient than VAVR in some applications, such as a building with high sensible loads in a more extreme climate where outdoor air economizers are not as effective. But, it is doubtful ACB can ever compete with VAVR on a first cost or life-cycle cost basis. The added costs of the piping and beams for ACBs are simply too high and well-designed VAVRs are simply too efficient.
(1.) Simmonds, P. 2013. "To beam or not to beam?" Engineered Systems (1).
(2.) Hastbacka, M. 2012. "Emerging Technologies: DOAS, radiant cooling revisited." ASHRAE Journal (12).
(3.) Rumsey, P. 2007. "Chilled beams in labs: eliminating reheat & saving energy on a budget." ASHRAE Journal (1).
(4.) Weidner, S. 2009. "Cooling with less air using underfloor air distribution and chilled beams." ASHRAE Journal (12).
(5.) Taylor, S., et al. 2012. "Dual maximum VAV box control logic." ASHRAE Journal (12).
(6.) Taylor, S. 2007. "Increasing efficiency with VAV system static pressure setpoint reset." ASHRAE Journal (6).
(7.) ASHRAE RP 1515, Thermal and air quality acceptability in buildings that reduce energy by reducing minimum airflow from overhead diffusers. Center for the Built Environment, Taylor Engineering LLC, Price Industries. In progress.
(8.) Livchak, A. 2012. "Don't turn active beams into expensive diffusers." ASHRAE Journal (4).
(9.) Murphy, J. 2011. "High-performance VAV systems." ASHRAE Journal (10).
Jeff Stein, P.E., Member ASHRAE; and Steven T. Taylor, P.E., Fellow ASHRAE
Jeff Stein, P.E., and Steven T. Taylor, P.E., are principals of Taylor Engineering in Alameda, Calif. Stein is a consultant to SSPC 90.1 and a member of SPCs 155P and 195. Taylor is a member and former chair of SSPC 90.1 and is vice chair of TC 4.3, Ventilation Requirements and Infiltration.
Table 1: Design fan power. ACB + DOAS VAV (0.5 cfm/ Reheat [ft.sup.2]) cfm 30,000 * 50,000 cfm/[ft.sup.2] 0.53 0.88 External Static Pressure 1.8 2.3 Internal Static Pressure 2.0 1.7 Total Static Pressure 3.8 4.0 Fan Efficiency 69% 69% Brake Horsepower 26 44 * There was some confusion as to the primary airflow rate in the GSB ACB + DOAS design. 30,000 cfm (0.5 cfm/ [ft.sup.2]) was used in the energy model but 36,000 (0.6 cfm/[ft.sup.2]) was used in the cost model. Had the energy model used 0.6 cfm/[ft.sup.2] then the ACB+DOAS energy performance would have been slightly worse. Had the cost model used 0.5 cfm/[ft.sup.2] then the ACB+DOAS costs would have been slightly better. In both cases the difference is most likely "in the noise." Table 2: HVAC cost model results. VAVR Hybrid ACB + DOAS Total HVAC Cost ($) 1,371,000 1,980,000 3,341,000 Total HVAC Cost ($/[ft. 25 37 62 sup.2]) Parameter Comparison Material Cost ($) 215,179 279,703 576,496 Labor Cost ($) 584,058 877,138 1,509,349 Equipment Cost ($) 319,695 380,297 608,118 Subcontractors ($) 252,067 442,862 647,037 Pounds of Ductwork 38,000 lb 33,224 lb 28,612 lb Linear Feet of Chilled Water 310 ft 5,963 ft 10,244 ft Pipe Linear Feet of Heating Hot 2,085 ft 2,330 ft 9,630 ft Water Figure 9: Simulated HVAC energy use intensities (site energy). ACB Design Hybrid ACB/VAVR VAV Reheat District Cooling 17.9 13.6 12.8 Heating 5.1 2.6 1.5 Fans 2.3 0.7 1 Pumps 0.1 0.1 0
|Printer friendly Cite/link Email Feedback|
|Title Annotation:||TECHNICAL FEATURE|
|Author:||Stein, Jeff; Taylor, Steven T.|
|Date:||May 1, 2013|
|Previous Article:||Modeling and 90.1.|
|Next Article:||A stable whole building performance method for Standard 90.1.|