Today’s HVAC industry offers a number of choices when it comes to providing heating and cooling in a large building. The three basic methods to provide comfort and move Btu around a building are by using water, air or refrigerant.
This editorial is the first in a series of articles that will compare these types of comfort systems. In this month’s column, we’ll look at the energy efficiency.
The energy consumption of any HVAC system is comprised of two components: equipment that generates heating or cooling and equipment that distributes it. The energy needed to generate heating and cooling commands the majority of energy consumption in an HVAC system, but the energy required for distribution is significant. It can take 40% of total electrical cooling energy demand to move Btu in an air system, 30% in refrigeration systems and 20% in hydronic systems.
The challenge of comparing the energy efficiency of HVAC systems always has been to take both the distribution and generation components into account while using the same set of test criteria. New ratings for variable refrigerant flow equipment have been developed by the Air-Conditioning, Heating and Refrigeration Institute in conjunction with the American National Standards Institute and American Society of Heating, Refrigerating and Air-Conditioning Engineers (Standard 1230 Rating of VRF Equipment).Earlier standards have been available for chillers (Standard 550-590 Rating of Water Chilling Packages) and heat pumps (Standard 13256 Water Source Heat Pumps Rating for Performance).
These AHRI standards have attempted to simplify the effort required to compare equipment efficiencies by developing a single number that can be used to compare various manufacturers’ equipment, especially part load performance.The part load number is necessarily a weighted seasonal average of efficiency for various climate (ambient) conditions and part loads.
For chiller equipment this is an IPLV, or Integrated Part Load Value. For air-side equipment this is an IEER, or Integrated Energy Efficiency Ratio. For water source heat pumps no single part load rating number is promulgated by AHRI.Basically, the IEER data for air-side equipment takes into account the distribution energy from fans. The IPLV data for water-side equipment does not take into account the distribution energy for pumps. The IEER and IPLV information is published in the AHRI Directory of Certified Performance and can be found at www.ahridirectory.org/ahriDirectory/pages/home.aspx.
Even with these rating standards it is still difficult to compare the performance of these different HVAC systems because of the different distribution system energy that is included or not included. Fortunately, a real-world comparison exists for comparing a water-based system with a refrigerant-based system. The ASHRAE headquarters building in Atlanta is equipped with a geothermal heat pump system on one floor and variable refrigerant flow system on another.
Apples to apples
Several years ago, the ASHRAE building went through an HVAC retrofit to upgrade its heating and cooling. A geothermal ground source heat pump system with constant-speed compressors was installed to serve the second floor; a VRF system with variable-speed compressors was installed to serve the ground floor. Both systems use no backup heat and rely solely on the electric energy to the compressors to both heat and cool the building, affording an apples-to-apples comparison.
Data on the energy consumption of the two systems were collected between 2010 and 2012 using actual metered electrical energy consumption.
The data for the Atlanta building show the VRF system consumes 60% to 85% moreenergy thanthe geothermal heat pump system. The reason for this is the energy consumed in heating the building. The AHRI ratings show that the constant-speed geothermal heat pump system is slightly more efficient than the variable-speed VRF system in cooling.
Proponents of VRF systems claim the systems do not need backup heat, even in heating climates. However, the systems achieve this performance by speeding up the compressor, up to double the speed, to produce higher heating capacities at lower ambient temperatures. This occurs at the expense of efficiency. If a variable-speed compressor has a higher efficiency at reduced speed it will have a lower efficiency at increased speed. This can be seen in the ASHRAE building’s 2011monthly breakdown for the heating months.
For heating, AHRI Standard 210/240 developed an average or seasonal energy efficiency ratio called the Heating Season Performance Factor, or HSPF. It is, again, an attempt to rate compressorized equipment for various climate (ambient) conditions and part loads.
The biggest difference in energy consumption of the geothermal and VRF systems is heating, not cooling, and the difference in energy consumption for heating is more than AHRI’s HSPF ratings would indicate.
Comparing energy consumption in heating for water, air and refrigerant systems is not as simple as comparing different HSPF ratings for compressorized equipment, as can be done for the ASHRAE building. Most heating generation equipment for water and air systems usesnatural gas-fired boilers. Comparisons should be done on the basis of the cost of producing a Btu of heat taking into account the local climate (heating hours), local cost of electricity and natural gas.
As an example, let’s look at a VRF system with an HSPF of 8 using electricity at an average cost of $0.11 per kWh from the U.S. Energy Information Agency. The unit cost of delivered heat is $13.74 per million Btu. A 90% efficient boiler using natural gas at an average cost of $8.50 per mcf ($0.85 per therm) from the EIA, the unit cost of delivered heat is $9.44 per million Btu. This is a savings of 30% in heating costs.
The VRF manufacturers have recognized this difference in heating costs between air source heat pumps and natural gas boilers in heating climates. The problem is that the coefficient of performanceofan air-source heat pumpdecreases with lower ambient temperatures; in other words, the heating COP of an air-source heat pump decreases with decreasing heat sink or outside air temperatures. The COP of a VRF unit decreases even faster because the compressor is speeded up to maintain heating capacity. While VRF manufacturers may claim their equipment doesn’t need backup heat, it does. This is actually electric heat but run through the compressor at decreasing COPs rather than through an electric strip heater.
To get over this hurdle, VRF manufacturers have suggested that their outside condensing units be installed inside a building in a heated space using natural gas unit heaters as the back-up heating source. As an example, if the space can be maintained at 40°F then the COP of the condensing unit remains high. The cost of heating is lower because cheaper natural gas heat replaces the higher cost electric heat from the lower COP at lower ambient temperatures.
In this example, the outside air dampers are open in the summer for heat rejection to the outside air and closed in the winter for heat addition from the natural gas unit heater. This configuration negates the advantage claimed by VRF manufacturers that their equipment doesn’t need inside mechanical rooms for their equipment since it is mounted outside.
Most HVAC systems are designed to keep a building cool on the hottest days and warm on the coldest days. That being the case, an HVAC system needs to work at full capacity on only the hottest and coldest days of the year. For the rest of the year, the HVAC system should operate at a reduced capacity to save energy.
This is where a system equipped with variable-speed technology can be used to match system fluid flow to actual heating and cooling demands. Variable-speed systems of any kind (water, air or refrigerant) pump less mass flow resulting in less horsepower to move the fluid. In addition, at part load the heat exchanger is oversized for the lower mass flow rate since it was sized for full load. The system is therefore more efficient.
U.S. chiller and heat pump manufacturers now offer variable-speed compressors similar to VRF systems. All variable-speed equipment has similar performances. The differences are in the heat sink temperatures that the equipment rejects heat to, the result of the Second Law of Thermodynamics. These are the earth, wet bulb air temperature and dry bulb air temperature. Geothermal open loop (earth) is the most efficient followed by geothermal closed loop (earth), water-cooled chillers and heat pumps (wet bulb air temperature), air cooled chillers, VRF and rooftop units and air-cooled condensing units (dry bulb air temperature).
The EER of a typicalconstant-speed chiller is approximately 12. However, using the AHRI part load rating conditions for chillers at lower ambient temperatures yields a substantial increase in integrated part load value for constant speed chillers to 16,an increase of four points. A typical VRF unit has an EER of approximately 13 and an integrated energy efficiency ratio of 19, an increase of six points.Therefore, the increase in the IEER for VRF is due primarily to being able to rate part loads at lower ambient conditions, not variable-speed operation. Approximately two-thirds of a VRF unit’s higher IEER is the result of this lower ambient rating for part load, not variable-speed efficiency.
Another way to look at this is that the increase in efficiency of variable speed over constant speed is two points, (6 – 4 = 2). This is two points out of 13, or 15%. Therefore, the increase in efficiency of a variable-speed unit over a constant-speed unit is approximately 15%, a nice increase, but certainly not the amount being claimed by VRF manufacturers.
With the use of new variable-speed chillers and heat pumps and variable-speed pumps, hydronic systems provide the most efficient method of generating and distributing Btu in a building. However, comfort still is what the HVAC industry is selling, and hydronic systems provide the best comfort including control of humidity.