Heat Pumps in Energy Certification of the Buildings SCOP_SEER_Rel 28 10 2014 rev 01 lz

04/11/20141

TABLE OF CONTENTS:

1. DIRECTIVE 2009/28/EC

2. Italian Law by Decree No. 28/2011

3. UNI EN 14825 – UNI TS 11300/4

4. Seasonal performance index - SCOP

5. Seasonal performance index – SEER

6. Optimized selection of an Heat Pump in Milan, using “SCOPon” approach

HEAT PUMPS IN

ENERGY CERTIFICATION OF THE BUILDINGS:

REFERENCE REGULATORY FRAMEWORK

LUCA ZORDAN - RELEASE 10_2014/00

04/11/20142

WHY DEVELOP THIS DOCUMENT?

� To share knowledge with the Italian consultants in a very complex matter as the internationaland national legislations, in the field of efficiency and renewable energies;

� Because obtained results from this SCOP study provide to the consultants a new point of viewto select heat pumps, based on energy optimization but in the specific city where the buildingis located;

� Because it is a very strong sales tools (USP): creating good feeling with consultant, talking thesame language and entering in their issues.

� Because help to differentiates our Brand from manyother competitors;

Dipl Eng. Luca Zordan

HEAT PUMPS IN

ENERGY CERTIFICATION OF THE BUILDINGS:


RELEASE 10_2014

04/11/20143

Legge 373/76

Legge 10/91

DPR 412/93

EPBD 2002/91/CE

Recast EPBD 2010/31/UE

DIRECTIVE 2009/28/CE D.Lgs. 28/2011

D.Lgs. 192/2005

D.Lgs. 311/2006

D.P.R. 2 aprile 2009 n. 59

D.M. 26 giugno 2009

European Community Italia Law

EUROPEAN LEGISLATIONS RELATED TO BUILDINGS


04/11/20144

EUROPEAN LEGISLATIONS RELATED TO BUILDINGS


With the recast of the EPBD, the principle of “nearly Zero Energy Buildings” will be

decisive for the development of the building sector.

nZEB means a building that has a very high energy performance and the low amount of

required energy should be covered to a very significant extent by energy from renewable

sources.

EPBD/Article 9.1: Member States shall ensure that by 31 December 2020, all new

buildings will be nZEB and after 31 December 2018, new buildings occupied and owned

by public authorities are nZEB.

04/11/20145

On 23rd April 2009, the EU commission published DIRECTIVE 2009/28/EC, also known as

RES Directive (Renewable Energy Sources and part of the implementation of the 20-20-20

targets) on the promotion of the use of energy from renewable sources.

This Directive:

� Sets mandatory national targets for the overall share of

energy from renewable sources in gross final energy

consumption and for the renewable share in transport;

� Requires member states to set out a National Action Plan

for renewable energy and identifies the technologies that

are considered part of the systems powered by

renewable sources for the computation and the

verification of achievement of targets;

� Introduces the obligatoriness of the certification of

installers who work in the renewable energy sector.

DIRECTIVE 2009/28/EC


04/11/20146


PRIMARY ENERGY

ηTηG

ηSηD

ηE

An energy source is called PRIMARY ENERGY when it is present in nature and therefore does

not come from the conversion of any other form of energy. Primary energy is not directly

available for use and must be converted. If conversion has taken place, it is called

SECONDARY ENERGY. If, besides being converted, the energy made available has been

transported to the end users, it is called FINAL ENERGY.

The process of using final energy involves losses such that the USEFUL ENERGY made

available to the system we are interested in is less than the final energy.

SECONDARYENERGY

Generation Storage Distribution Emission USEFUL ENERGY

FINAL ENERGY


DEFINITIONS

04/11/20147

Generation Storage Distribution Emission

Internal Loads

NET ENERGY DEMAND

Solar Energy and/or other non-

fossil sources

ηTηG

ηSηD

DISPERSIONS

DIRECTIVE

2009/28/CE

UNI TS 11300-4


FINAL ENERGY

ηE

USEFUL ENERGY

SECONDARYENERGY

PRIMARY ENERGY

USEFUL ENERGY


DEFINITIONS

04/11/20148

Heat pumps (as technology that uses renewable energy coming from the air, water and the

ground) have been included in the «RES» Directive and they constitute a technology that

has a significant potential for contribution to energy saving.

Heat pumps are one of the few technologies that can cover entire heating, cooling and

domestic hot water production requirements.

THERMAL

ENERGY

TRANSFERRED

TO THE FLUID

ENERGY

ABSORBED BY THE SOURCE

MECHANICAL

WORK

Schematic representation of

the Energy Flow of a

compression heat pump



HEAT PUMPS

9 04/11/2014


CONTRIBUTION FROM HEAT PUMPS TO ACHIEVERES «RES» SHARE


04/11/201410

Italy has undertaken towards the EU to achieve, by 2020, a final

renewable energy consumption level (electricity, heat, transport)

that is 17% of the total final consumption of primary energy, as

well as to promote virtuous consumption strategies aimed at energy

efficiency, to achieve a primary energy saving of 13.4%.

Gross Final Consumption of energy and targets for renewable energy

2005 2008 2020

Consumption

from RES

Gross Final

Consumption

RES/

Consumption

Consumption

from RES

Gross Final

Consumption

RES/

Consumption

Consumption

from RES

Gross Final

Consumption

RES/

Consumption

(Mtoe) (Mtoe) % (Mtoe) (Mtoe) % (Mtoe) (Mtoe) %

6.941 141.226 4.91% 9.001 131.553 6.84% 22.306 131.214 17.00%

SOURCE: Ministry for Economic Development «Summary of National Action Plan for Renewable Energy – June

2010». (abstract)



ABOUT ITALY

04/11/201411

The EU Directive in question has been implemented in Italy with

ITALIAN LEGISLATIVE DECREE No. 28 of 3 MARCH 2011

(the so-called «Romani Decree») published in the

Official Gazette on 28 March 2011.

This Decree has very considerable importance as it significantly

affects the future of the development of «renewables» in Italy..

Besides introducing considerable changes in the sector (in

particular concerning authorizations and as regards incentives

to be assigned to renewables), it changes Italian Presidential

Decree D.P.R. 59/09 and Italian Legislative Decree Dlgs 192-311

in some parts.

ITALIAN LAW BY DECREE No. 28/2011


ABOUT ITALY

04/11/201412

In the case of new buildings or buildings undergoing

considerable renovations, the THERMAL energy production

systems must be designed and made so as to guarantee the

contemporaneous observance of a coverage - using energy

produced by systems powered by renewable sources - of 50% of

the consumption expected for DHW water and of the following

percentages of the SUM of the consumption expected for DHW,

heating and cooling: .

ITALIAN LAW BY DECREE No. 28/2011

A) 20% when the application for the pertinent building permit is presented after 31/05/2012

B) 35% when the application for the pertinent building permit is presented after 01/01/2014

C) 50% when the application for the pertinent building permit is presented after 01/01/2017


ABOUT ITALY – KEY CONTENT

04/11/201413

HEAT PUMPS: RENEWABLE SHARE


ERES = QUSABLE * (1 - 1/SPF)

with:

SPF = Seasonal Performance Factor;

QUSABLE = total usable heat delivered by the heat pump.

QUSABLE is only counted for those heat pumps which achieve 115% efficiency, based on

primary energy:

� Minimum admitted SPF , with the current values of «η»:

SPFmin = 2,5 for electric Heat Pumps (SPFmin = 1,15 for gas heat pump)

SPF for electric Heat Pumps has to be calculated based on SCOPnet (EN 14825:2012)

η = yearly defined by EUROSTAT as average value for EU (nowadays is 0,455)


04/11/201414

The UNI TS 11300 Standards, as enforcing tools of Italian Law by Decree n°28, are for all

intents and purposes to be considered national LAWS and are divided into 4 specifications:

� UNI TS 11300-1/2008 (being revised): Determination of the thermal energy requirement

of the building for summer and winter air conditioning;

� UNI TS 11300-2/2008 (being revised, expired in 2012): Primary energy and efficiency for

winter air conditioning and for domestic hot water production for sanitary use;

� UNI TS 11300-3/2010 (being revised): Primary energy and efficiency for summer air

conditioning;

� UNI TS 11300-4/2012: Energy Performance of buildings: use of renewable energy and

other methods of generation for winter air conditioning and DHW production.

� UNI TS 11300-5: being prepared

UNI TS 11300


THE STANDARD AS A TECHNICAL TOOL…

04/11/201415

TITLE: «Energy Performance of buildings: use of renewable energy and other methods of

generation for winter air conditioning and DHW production»

PURPOSE AND SCOPE OF APPLICATION

The following are also considered:

solar thermal, district heating, biomass,

cogeneration and photovoltaic with

priority as per table alongside:

UNI TS 11300-4

Technical specification UNI TS 11300–4 applies to generation sub-systems that supply useful

thermal energy from renewable energy or with generation methods other than the flame

combustion of fossil fuels covered in UNI TS 11300-2, including HPs (whether aeraulic,

geothermal or hydraulic).

UNI TS 11300-4 PUBLICATION: 10 May 2012 (BEING REVISED)

Prioritya) Generation subsystem Energy production

1 Solar thermal Thermal

2 Cogeneration Cogenerated electrical and thermalb)

3 Biomass combustion Thermal

4 Heat pumps Thermal or refrigeration

5 Fossil fuel heat generators Thermal

a) If the system envisages the use of useful thermal energy from a network (district heating) and

solar energy, priority 1 is assigned to the latter.

b) These specification are applied to cogenerative systems following heat load, that is, adjusted

depending on the heat load. The thermal energy is therefore the basic production.


04/11/201416

Definition of the boundary of the building-plant system

UNI TS 11300-4

Technical specification UNI TS 11300-4 considers as boundary of the building the boundary

that delimits all the areas in which useful thermal energy or electrical energy is used or

produced (energy boundary), in accordance with UNI EN 15603.


Key:1 User2 Storage3 Generator4 Fuel5 Electrical energy6 Energy of auxiliary systems7 Solar thermal collectors8 Photovoltaic panels9 Useful thermal energy from network10 Useful thermal energy removed11 Evaporative tower12 Electrical energy from cogeneration13 Electrical energy from photovoltaic14 Electricity network15 Boundary of the system


04/11/201417

As regards Heat Pumps (aeraulic, geothermal and hydraulic), it is essential to consider, in

11300-4, paragraph 9.4.4 «Performance at reduced load factor CR» and the reference to

UNI EN 14825 (May 2012)

� «System» Standards:

UNI-TS 11300-3

UNI-TS 11300-4

� «Product» Standard:

EN 14825: Air conditioners, liquid chilling

packages and heat pumps, with electrically

driven compressors, for space heating and

cooling - Testing and rating at part load

conditions and calculation of seasonal

performance; EN 14825:2012



UNI TS 11300-4

04/11/201418

� Seasonal performance index (SCOP) should be calculated with the “bin method”

(method of the frequencies of occurrence of the temperature), distributed over the

entire heating season;

� One of the three reference climate conditions stated in the standard must be used:

� A (Average): Strasbourg (France),

� C (Colder): Helsinki (Finland)

� W (Warmer): Athens (Greece),

These climate conditions are considered sufficiently representative of the climate of the

whole of Europe.

EN 14825:2012

THE SEASONAL PERFORMANCE INDEX “SCOP” IN HEATING


04/11/201419

Distribution of hourly average temperatures in the three reference cities

EN 14825:2012

Frequency distribution of the “bin” for the climatic reference conditions, as

specified by the UNI EN 14825

Ho

urs

Temperature (°C)



04/11/201420

� External design temperature (θdesign) according to UNI EN 12831:

� for A (Average) = - 10°C

� for C (Colder) = - 22°C

� for W (Warmer) = + 2°C

� Internal design temperature: 20°C.

� When the external temperature exceeds 15°C, the heating system stops (therefore it is

assumed any heating load Φh when the external temperature is θH,off = 16°C

� balancing temperature).

EN 14825:2012

� It is assumed that load Φh ranges

linearly from 100%, at the design

temperature (θdesign), to 0% at the

balancing temperature (Figure 1)θdesign 16

Φh

T [°C]

(Figure1)

100%



04/11/201421

EN 14825:2012

«PLR» (Part Load Ratio)

PLR is the ratio between the part load (or total load) divided by the full load, and is calculated

using the following formula:

with:

θe = external air

temperature

θdes = design

temperature


04/11/201422

All the standards on the matter and, in particular UNI EN 14825 and UNI/TS 11300-4, require

the heat pump manufacturers supply data regarding at least the operating conditions indicated

in the following table.

EN 14825:2012

Cold Souce

Cold source

temperature

Hot source

temperature,

air heating 1)

Hot sorce

temperature,

hydronic heating 2)

Hot sorce

temperature, tap

water 3)

Air -7 2 7 12 20 35 45 55 45 55

Water 5 10 15 20 35 45 55 45 55

Soil/rock -5 0 5 10 20 35 45 55 45 55

1) Return temperature.

2) For at least one of the indicated temperatures. Other suggested data: 25°C, 65°C.

3) For at least one of the indicated temperatures.

Reference conditions for performance data provided by the manufacturer. Heat pumps for

heating only or combined operation.

Heat pumps Cold source temperature (air) hot source temperature, tap water 1) )

Tap Water production only 7 15 20 35 55

1) For at least one of the indicated temperatures. Other suggested data: 45°C, 65°C.

Reference conditions for performance data provided by the manufacturer. Heat pumps for

domestic hot water production only.



04/11/201423

With these external temperature values A (-7°C), B (2°C), C (7°C), D 12°C) referred to the

reference climate areas, we obtain the following % ratio of the PLR index:

88%

54%

35%

64%

100%

29%

61%

37%

24%15%

11%

EN 14825:2012



04/11/201424

3724

64

So, for Air-to-Water Heat Pumps:

Ext. Air Temp. (Cold source)

°C

Climate

(EN 14825)

PLR

%

Inlet Water Temperature

(warm source) [°C ]



EN 14825:2012

25

EN 14825:2012

In a bivalent heat pump system, in which the

heat demand of the user is not met

exclusively by the heat pump but auxiliary

generation systems operate, the bivalent

temperature (θbival) is defined as the

temperature of the cold source at which load

demand can be covered exclusively with the

heat pump.

As we may see in next slides, in this thermal

conditions heat pump operates with load

factor CR = 1.

BIVALENT TEMPERATURE (Air source)

1 Heat load of the system

2 Design heat load

CR < 1CR > 1


04/11/201426

- COP’ (Coefficient of performance at declared capacity): ratio between the heating

capacity delivered by the HP at full load and the absorbed electrical power, at the

indicated specific external air temperature conditions;

- COPPL (Coefficient of performance at part load): ratio between the heating capacity

delivered by the HP at part load and the absorbed electrical power, at the indicated

specific external air temperature conditions;

- TOL (Operating Temperature Limit): operating temperature limit of the HP (related to

the cold source) declared by the manufacturer – stopping temperature limit.

- P (power required by the system) [kW]

- φφφφ (heating capacity required by the system) [kW]

- φφφφ’H, design (design heat load of the system) [kW]

- (Temperature of the hot well: delivery side of the HP)

- (Temperature of the cold source)

θc

θf

MAIN DEFINITIONS


EN 14825:2012

04/11/201427

- DC (Declared Capacity): Maximum heating capacity of the heat pump in the operating

conditions specified by the manufacturer;

- SCOPnet (Net seasonal coefficient of performance): seasonal coefficient of performance

calculated with reference to just the active operating period excluding consumption due to

any additional electric heaters.

- SCOPon (Active function seasonal coefficient of performance): seasonal coefficient of

performance calculated with reference to just the active operating period including

consumption due to any additional electric heaters.

- SCOP (Seasonal coefficient of performance): seasonal coefficient of performance calculated

with reference to the whole heating period, including consumption due to any additional

electric heaters and including any consumption during periods when there is no demand for

heat, periods of stand-by, consumption due to active auxiliary systems during switch-off

periods, and consumption due to a crankcase heater if there is one.

MAIN DEFINITIONS


EN 14825:2012

04/11/201428

Elbu (Tj) = power of the electric heater [kW]

MAIN DEFINITIONS

Heating Energy Demand (kWh)

Consumed Electrical Energy (kWh)


EN 14825:2012

04/11/201429

NOTE: CR is in general different from the climate factor PLR as the nominal heating capacity of the pump can be

different from the design heating capacity and, in any case, it changes as the temperatures of the sources change.

- CR (Capacity Ratio - Heat Pump Load factor). This is the ratio between the heating

capacity required by the user to the HP «Φ» (load) in the specific operating conditions

and the nominal heating capacity of the HP declared by the manufacturer «DC» in the

same temperature conditions.

External Water Output PLR Power required Max heating capacity

CR

Temperature Temperature (QDESIGN=-10°C)by the system

(Φ)

deliverable by the HP

(DC)

(°C) (°C) % kW kW

ϑDESIGN -10 35 100% 5.00 4.50 1.11

A -7 35 88% 4.40 4.80 0.92

B 2 35 54% 2.70 6.24 0.43

C 7 35 35% 1.77 7.18 0.24

D 12 35 15% 0.75 8.11 0.09

CR = DC

ΦΦΦΦ

Example (bivalent temperature = -8°C)

MAIN DEFINITIONS


EN 14825:2012

04/11/201430

For determination of performance at full load in different temperature conditions from the

declared ones, in the case of refrigerant compression & electrical absorption HPs, it is

possible to:

1) carry out linear interpolation between the declared values, or:

Dependence of the full load COP on temperature

COP in

intermediate

conditions:

Second law efficiency is defined by the relation:

2) use second law efficiency; the maximum theoretical COP

between two sources (ideal Carnot cycle, Figure 2) is in fact given

by the following relation:

Figure 2: Ideal Carnot cycle


EN 14825:2012

04/11/201431

EXAMPLE 1: interpolation between two different temperatures of the hot source, with the

same cold source, using second law efficiency

θf -7 2 7 12

COP1 3,6 4,5 5,4 6,5

DC1 [kW] 8,8 10,2 12 13,6

ηΙΙ,1 0,491 0,482 0,491 0,485

COP2 3,0 3,6 4,1 4,8

DC2 [kW] 7,8 9,3 11,2 13,2

ηΙΙ,2 0,490 0,486 0,490 0,498

ηΙΙ,X 0,490 0,483 0,490 0,489

COPX 3,4 4,2 4,9 5,9

θc,1 = 35°C

θc,2 = 45°C

θc,X = 38°C

EXAMPLE 2: interpolation between two different temperatures of the cold source, with the

same hot source, using second law efficiency

θf -7 -3 0 2

COP1 3,6 3,95 4,26 4,5

DC1 [kW] 8,8 10,2

ηΙΙ,1 0,491 0,487 0,484 0,482

θc = 35°C

Dependence of the full load COP on temperature


EN 14825:2012

04/11/201432

When, due to fixed working conditions, the applied load is

less than the maximum capacity that the HP can supply,

the COP changes and, to determine the performance of

the machine, a corrective factor must be used:

Dependence of the COP on the load factor (CR<1)

the value of the corrective factor can be established:

a) according to the data provided by the manufacturer;

b) according to the calculation models, when these data are not provided.

COPPL = f * COP

where:

COPPL = value of the COP at part load

COP = value of the COP at full load

CR < 1

CR > 1


EN 14825:2012

04/11/201433

a) CR at part load conditins (CR < 1) according to the data provided by the manufacturer;

Followind tags have to be respected (Cfr. UNI EN14825, A ”Average” climate area):

� Desing Temperature: - 10 °C ;

� PLR referred to -7 (A), 2 (B), +7(C), +12 (D);

� Bivalent temperature fixed at -7°C;

� Delacred Capacity(DC) and COP referred to 4 temperatures (A), (B), (C), (D).



EN 14825:2012

04/11/201434

b) Calculation of CR at reduced load (CR < 1) according to the calculation models when

data provided by the manufacturer are not available

In this case, for air/water, water/water heat pumps , we proceed as follows:

Corrective Factor

NOTE: For variable capacity heat pumps (INVERTER HPs) if the data envisaged by UNI EN 14825 are

not available, a corrective coefficient of 1 up to the load factor CR = 0.5 (or up to the minimum

modulation value if this is different from 0.5) is assumed. Below this value of CR , we proceed as in

previous point .


where:COPA,B,C,D COP in conditions A, B, C, D according to prEN 14825:2010COPDC COP at full load, declared in the temperature to which the performance at part load relatesCc Declared correction factor. If not provided, it is assumed to be 0.9CR Capacity ratio

EN 14825:2012


04/11/201435

b) Calculation of CR at reduced load (CR < 1) according to the calculation models when

data provided by the manufacturer are not available



EN 14825:2012

04/11/201436

Calculation of the

SEASONAL COEFFICIENT OF PERFORMANCE (SCOP)

of electrical refrigerant compression Heat Pumps according to EN 14825.


EN 14825:2012

SCOP - SEASONAL COEFFICIENT OF PERFORMANCE

04/11/201437

Climate Condition referred to

the reference city

Declared Performace of the HP

unit

INPUT

SCOPON

SCOPNET

OUTPUTALGORITHM


EN 14825:2012


04/11/201438

Calculation of SCOPON and SCOPNET for an air-water (step) heat pump, used for heating by

radiant panels is presented by way of example.

� Reference climatic conditions A (Average / Strasbourg);

� Design capacity of Φdesign = 5 kW at temperature θdesignA = – 10 °C;

� Bivalent temperature = -8°C;

� Fixed water delivery temperature: 35°C;

� Operating Temperature Limit (TOL): -20°C.

AVERAGEExternal Air

Temperature

Outlet water

Temperature

PLR Heating Capacity

required

by the system

Maximum heating

capacity by the HP

Declared

COP CR fCOP*

COP

part load(QDESIGN=-10°C)

(COPDC) (COPPL)

(°C) (°C) % kW kW

TOL -20 35

ϑDESIGN -10 35 100% 5.00 4.50 2.92 1.11 1.01 2.95

A -7 35 88% 4.40 4.80 3.09 0.92 0.99 3.06

B 2 35 54% 2.70 6.24 3.99 0.43 0.88 3.52

C 7 35 35% 1.75 7.18 4.54 0.24 0.76 3.45

D 12 35 15% 0.75 8.11 5.19 0.09 0.51 2.66

ϑBIVALENT -8 35 92% 4.60 4.65 3.03 0.99 1.00 3.03

Table of the input data and of the main coefficients obtained for calculation of the SCOP according to EN14825

EXAMPLE:


EN 14825:2012


04/11/201439

T design -10 °C

T bivalent -8 °C

T OL -20,00 °C

Pdesign 5,0 kW

Temp Acqua 35,0 °C

CC=0,9

CAPACITY COP*

Phol 3,52 kW 2,34

Phbiv 4,70 kW 3,03

PhA 4,80 kW 3,09

PhB 6,24 kW 3,99

PhC 7,18 kW 4,54

PhD 8,11 kW 5,19

*COP values already integrate degradation for on/off cycling

Distribution of hourly temperatures (bin)

Hou

rs

EXAMPLE:


EN 14825:2012


04/11/201440

BinOutdoor

temperature(dry bulb)

hoursPLR

Heating demand of the building Heating

Capacity of Heat Pump

CRCapacity

of electricalheater

Annual Capacity

of electrical heater COP fCORR,

COPCOPPL

Annual Heating

demand of the building

Annual Heating demand of the

buildingWitout h.e.

Annual power input with electrical

heater

Annual power input without

electrical heater

(Tj-16)/(Tdesign-16)

PLR*Pdesign

j Tj hj(%)

Ph(Tj) elbu(Tj) hj * elbu(Tj) hj*Ph(Tj)- °C hr kW kW kW kWh kWh kWh kWh kWh9 -22 0 146% 7,31 3,32 2,20 7,31 0,0 0,00 1,00 0,00 0,0 0,0 0,0 0,0

10 -21 0 142% 7,12 3,42 2,08 7,12 0,0 0,00 1,00 0,00 0,0 0,0 0,0 0,011 -20 0 138% 6,92 3,52 1,97 3,40 0,0 2,34 1,00 2,34 0,0 0,0 0,0 0,012 -19 0 135% 6,73 3,62 1,86 3,11 0,0 2,40 1,00 2,40 0,0 0,0 0,0 0,013 -18 0 131% 6,54 3,72 1,76 2,82 0,0 2,46 1,00 2,46 0,0 0,0 0,0 0,014 -17 0 127% 6,35 3,82 1,66 2,53 0,0 2,51 1,00 2,51 0,0 0,0 0,0 0,015 -16 0 123% 6,15 3,91 1,57 2,24 0,0 2,57 1,00 2,57 0,0 0,0 0,0 0,016 -15 0 119% 5,96 4,01 1,49 1,95 0,0 2,63 1,00 2,63 0,0 0,0 0,0 0,017 -14 0 115% 5,77 4,11 1,40 1,66 0,0 2,69 1,00 2,69 0,0 0,0 0,0 0,018 -13 0 112% 5,58 4,21 1,33 1,37 0,0 2,74 1,00 2,74 0,0 0,0 0,0 0,019 -12 0 108% 5,38 4,31 1,25 1,08 0,0 2,80 1,00 2,80 0,0 0,0 0,0 0,020 -11 0 104% 5,19 4,41 1,18 0,79 0,0 2,86 1,00 2,86 0,0 0,0 0,0 0,021 -10 1 100% 5,00 4,50 1,11 0,50 0,5 2,92 1,00 2,92 5,0 4,5 2,0 1,522 -9 25 96% 4,81 4,60 1,04 0,21 5,2 2,97 1,00 2,97 120,2 115,0 43,8 38,723 -8 23 92% 4,62 4,70 0,98 0,00 0,0 3,03 1,00 3,03 106,2 106,2 35,1 35,124 -7 24 88% 4,42 4,80 0,92 0,00 0,00 3,09 0,99 3,06 106,2 106,2 34,6 34,625 -6 27 85% 4,23 4,96 0,85 0,00 0,0 3,19 0,98 3,14 114,2 114,2 36,4 36,426 -5 68 81% 4,04 5,12 0,79 0,00 0,0 3,29 0,97 3,20 274,6 274,6 85,7 85,727 -4 91 77% 3,85 5,28 0,73 0,00 0,0 3,39 0,96 3,27 350,0 350,0 107,1 107,128 -3 89 73% 3,65 5,44 0,67 0,00 0,0 3,49 0,95 3,33 325,2 325,2 97,7 97,729 -2 165 69% 3,46 5,60 0,62 0,00 0,0 3,59 0,94 3,38 571,2 571,2 168,9 168,930 -1 173 65% 3,27 5,76 0,57 0,00 0,0 3,69 0,93 3,43 565,6 565,6 165,0 165,031 0 240 62% 3,08 5,92 0,52 0,00 0,0 3,79 0,92 3,47 738,5 738,5 212,8 212,832 1 280 58% 2,88 6,08 0,47 0,00 0,0 3,89 0,90 3,50 807,7 807,7 230,6 230,633 2 320 54% 2,69 6,24 0,43 0,00 0,00 3,99 0,88 3,53 861,5 861,5 244,4 244,434 3 357 50% 2,50 6,43 0,39 0,00 0,0 4,10 0,86 3,54 892,5 892,5 251,9 251,935 4 356 46% 2,31 6,62 0,35 0,00 0,0 4,21 0,84 3,55 821,5 821,5 231,6 231,636 5 303 42% 2,12 6,80 0,31 0,00 0,0 4,32 0,82 3,54 641,0 641,0 181,3 181,337 6 330 38% 1,92 6,99 0,28 0,00 0,0 4,43 0,79 3,51 634,6 634,6 181,0 181,038 7 326 35% 1,73 7,18 0,24 0,00 0,00 4,54 0,76 3,45 564,2 564,2 163,4 163,439 8 348 31% 1,54 7,37 0,21 0,00 0,0 4,67 0,73 3,39 535,4 535,4 158,1 158,140 9 335 27% 1,35 7,55 0,18 0,00 0,0 4,80 0,68 3,29 451,0 451,0 137,3 137,341 10 315 23% 1,15 7,74 0,15 0,00 0,0 4,93 0,64 3,14 363,5 363,5 115,8 115,842 11 215 19% 0,96 7,92 0,12 0,00 0,0 5,06 0,58 2,93 206,7 206,7 70,4 70,443 12 169 15% 0,77 8,11 0,09 0,00 0,00 5,19 0,51 2,66 130,0 130,0 49,0 49,044 13 151 12% 0,58 8,30 0,07 0,00 0,0 5,32 0,43 2,28 87,1 87,1 38,3 38,345 14 105 8% 0,38 8,48 0,05 0,00 0,0 5,45 0,32 1,76 40,4 40,4 23,0 23,046 15 74 4% 0,19 8,67 0,02 0,00 0,0 5,58 0,18 1,03 14,2 14,2 13,8 13,8

Σ ==> 10.328 10.322 3.079 3.073

SCOPon SCOPnet3,35 3,36


EN 14825:2012


04/11/201441

SEER - SEASONAL ENERGY EFFICIENCY RATIO

Calculation of the

SEASONAL ENERGY EFFICIENCY RATIO (SEER)

of electrical water chiller according to EN 14825.


EN 14825:2012

04/11/201442

REFERENCE TECHNICAL SPECIFICATION: UNI TS 11300-3

SCOPE OF APPLICATION

- Deals in a structured and systematic way with the summer behaviour of the building and in

particular of the system installed therein for maintenance of optimal environmental conditions;

- Provides data and methods for the determination:

� of the efficiency and energy requirements of summer air conditioning systems;

� of the primary energy requirements for summer air conditioning;

� Primary energy and efficiency for summer air conditioning;

This applies only to fixed summer air conditioning systems with electrically operated or

absorption refrigerating machines.

These systems can be alternatively:

� newly designed;

� restored;

� existing.



EN 14825:2012

04/11/201443

The Technical Specification identifies system efficiency and relevant energy requirement

proceeding in a similar way to what already takes place for the analysis of heating systems, by

sub-dividing the system into various system sub-systems, with particular attention to the

generation sub-system. The specific energy requirement value for air handling is added to the

basic calculation of energy necessary for cooling.

The primary energy requirement for summer air conditioning is determined as the sum of the

contributions (corrected by the conversion factor from primary energy to electrical energy) of

the electrical energy requirements of the auxiliary systems, of the actual energy requirements

for cooling and for air handling.

CALCULATION METHOD

Cooling Energy Demand (kWh)

Consumed Electrical Energy (kWh)



EN 14825:2012

04/11/201444

� Nominal Chiller Cooling Capacity

(Aria 35°C, Acqua 7°C, DT=5K) ;

� EER at full load, at External Air temperature of

35-30-25-20°C (EERDC)

Calculate «Partial Load Ratio (X)» and

«Capacity Ratio (Y)»

Calcolate required cooling capacity

Pc(Tj)=Pdesignc * Pl(Tj);

Calculate the maximum efficiency expected in the

ideal Carnot cycle: EERMAX= (θf+273,16)/(θc-θf);

Calcolate performance of the second principle

ηΙΙηΙΙηΙΙηΙΙ = EERDC / EERMAX in the 4 Bin point where EERDC are

declaredby manufacture; then interpolate to find

efficiency ratio in all other Bin - EERDC(Tj).

Calcolate EERDC_T(j):

EERDC_T(j) = hII * EERMAX_T(j);

Calcolate indecies:

EERbin_(Tj) = Y * EERDC_(Tj);

Insert the hourly temperatures distribution (bin)

• Colling Energy required to the the building

Qc(Tj)=hj * Pc(Tj) [kWh]

• Elecrtical Energy consumed by unit

Qe(Tj)=hj * (Pc(Tj)/EERbin) [kWh];

SEER = ΣΣΣΣQc(Tj) / ΣΣΣΣQe(Tj)

NB: below 20°C e over 35°C values are considered constant

INPUT



EN 14825:2012

PROCEDURE

04/11/201445

EXAMPLE : SEER Calculation according to EN14825 for a residential building in VenicePdesignc = 6,20kW / Tdesignc = 35°C / Wtemp=7°C, DT=5K

EERDC,20°C = 5,46, EERDC,25°C = 4,67, EERDC,30°C = 3,88, EERDC,35°C = 3,26)

Bin

Outdoor

temperature

(dry bulb)

hours

Partial Load

Ratio (X)

Capacity Ratio

(Y)

Cooling Demand

of the Building

Cooling Capacity

of the Chiller

EERMAX

(Carnot cycle)ηΙΙ EERDC EERbin Annual Cooling

Demand of the

building

Annual Power Input

of chiller(Tj-16)/

(Tdesignc-16) Pl/(CC*Pl + (1-CC)) Pdesignc * Pl(Tj) (θf+273,16)/(θc-θf) ηΙΙ = EERDC/EERMAX

Y * EERDC

j T j hj Pl(Tj) Pc(Tj) hj*Pc(Tj) hj*(Pc(Tj)/EERbin)

- °C hr (%) kW kW kWh kWh

5 17 163 5% 0,36 0,33 7,40 28,02 0,25 7,00 2,50 53,19 21,26

6 18 230 11% 0,54 0,65 7,35 25,47 0,25 6,37 3,44 150,11 43,61

7 19 277 16% 0,65 0,98 7,30 23,35 0,25 5,84 3,81 271,17 71,24

8 20 283 21% 0,73 1,31 7,25 21,55 0,25 5,46 3,97 369,39 93,02

9 21 283 26% 0,78 1,63 7,20 20,01 0,26 5,26 4,11 461,74 112,43

10 22 276 32% 0,82 1,96 7,15 18,68 0,27 5,08 4,18 540,38 129,40

11 23 264 37% 0,85 2,28 7,10 17,51 0,28 4,93 4,21 603,03 143,38

12 24 260 42% 0,88 2,61 7,05 16,48 0,29 4,79 4,21 678,74 161,15

17 25 218 47% 0,90 2,94 7,00 15,56 0,30 4,67 4,20 640,23 152,33

18 26 177 53% 0,92 3,26 6,92 14,75 0,30 4,48 4,11 577,58 140,57

19 27 114 58% 0,93 3,59 6,84 14,01 0,31 4,31 4,01 409,20 101,93

36 28 105 63% 0,94 3,92 6,76 13,34 0,31 4,15 3,92 411,16 104,83

37 29 66 68% 0,96 4,24 6,68 12,73 0,31 4,01 3,83 279,98 73,06

38 30 60 74% 0,97 4,57 6,60 12,18 0,32 3,88 3,75 274,11 73,17

39 31 38 79% 0,97 4,89 6,53 11,67 0,32 3,74 3,64 186,00 51,12

40 32 7 84% 0,98 5,22 6,46 11,21 0,32 3,60 3,54 36,55 10,34

41 33 4 89% 0,99 5,55 6,39 10,78 0,32 3,48 3,44 22,19 6,45

42 34 2 95% 0,99 5,87 6,32 10,38 0,32 3,37 3,35 11,75 3,51

43 35 0 100% 1,00 6,20 6,25 10,01 0,33 3,26 3,26 0,00 0,00

44 36 0 105% 1,01 6,53 6,18 9,66 0,33 3,19 3,20 0,00 0,00

45 37 0 111% 1,01 6,85 6,11 9,34 0,33 3,08 3,11 0,00 0,00

46 38 0 116% 1,01 7,18 6,04 9,04 0,33 2,98 3,02 0,00 0,00

Σ ==> 5.976,47 1.492,80

SEERON 4,01



EN 14825:2012

04/11/201446

HEAT PUMPS IN ENERGY CERTIFICATION OF BUILDINGS:


Release 06_2014

CONSIDERATIONS:

� With UNI TS 11300 there is an Important cultural shift from “punctual” performance &

efficiency concept (not significant), to a "weighted average seasonal“ logic;

� The system must be designed to work efficiently even at part loads;

� By the «product standard» EN14825, it’s possible to implement a method to compare

both products of different companies but also different technologies behave at partial

load (e.g. cps VS cps, hydronic VS direct expansion, etc.).

� In HPs, it is very important to optimally define the bivalent temperature in order to

optimize consumption: SCOPon is therefore a valid tool.


04/11/201447

OPTIMIZED SELECTION OF AN HEAT PUMP IN MILAN

by using “SCOPon APPROACH”


04/11/201448

THE QUESTIONS ARE:

- With reference to SCOP calculation method applied to heat pumps, considering a given

design temperature, it’s better to select a large heat pump or it’s better a smaller with

electrical heater in addition?

- What is the tool that guides us in an energy-conscious selection?

I’VE TRIED TO REPLY THESE QUESTIONS INTRODUCING A NEW ENERGY APPROACH TO

SELECT AN ELECTRIC HEAT PUMP: APPROACH BASED ON SCOPon.

OPTIMIZED SELECTION OF AN HEAT PUMP IN MILAN, by using

“SCOPon APPROACH”


04/11/201449



INTRODUCTION - SCOP

As is known SCOP (Seasonal Coefficient of Performance) describes the heat pump's average

annual efficiency performance.

SCOP is therefore an expression for how efficient a specific heat pump will be for a given

heating demand profile, so in a specific geographical area.

More precisely, it’s defined two different types of SCOP: SCOPon and SCOPnet.

Next slides will show the right definition, but remember that the first one (SCOPon) takes

into account the contribution - in terms of energy consumption - of any additional

electrical heaters.


04/11/201450

INTRODUCTION - Bivalent Temperature

In addition, we have to remember the meaning of «Bivalent Temperature». The point

where the heat pump's capacity corresponds exactly to the heating demand is known as

the bivalent point. At temperatures below the bivalent point, the heat pump's capacity

has to be supplemented by backup heating. In the SCOP calculation this is included as pure



electric heating with a COP value of 1,

regardless of whether or not the heat

pump has an electric heating element.

For higher temperatures the heat pump

will run in part load, which SCOP also

takes into account. These conditions are

illustrated in the figure below


04/11/201451

APPLICATION:

OFFICE BUILDING

LOCATION:

Milan (Italy)Working Days

Saturday

Sunday & holudays

OPERATING TIMES

ON OFF

OPEN

CLOSE




04/11/201452

Daytime

Night

Temperature (°C)

Temperature (°C)

Hou

rsU

R %

Annual Operating

Hours Daytime 2670

Hours Night 291

Totale Hours 2961



APPLICATION:

OFFICE BUILDING


04/11/201453

OPERATING TIMES

ON OFF

OPEN

CLOSE

APPLICATION:

HOTEL

LOCATION:

Milan (Italy)Working Days

Saturday

Sunday & holudays




04/11/201454

Daytime

Night

Temperature (°C)

Hou

rsU

R %

Temperature (°C)

Annual Operating

Hours Daytime 4116

Hours Night 4116

Totale Hours 8232



APPLICATION:

HOTEL


04/11/201455

1. DEFINE VARIABLES NEEDED TO CALCULATE “SCOPon” WITH REFERENCE TO EN 14825

Outdoor

Temperature

Water

temperature

supplied

Partial Load

Ratio (PLR)

Heating

Building

Capacity

(°C) (°C) % kW

TOL -15 45

ϑϑϑϑDESIGN -5 45 100% 58,0

A -7 45 - 63,5

B 2 45 67% 38,7

C 7 45 43% 24,9

D 12 45 19% 11,0



2. IT’S BEEN SELECTED Nr. 5 DIFFERENTE BIVALENT TEMPERATURES:

-5°C / -2°C / 0°C / +2°C / +5°C


04/11/201456

Heating Capacity of Heat Pump

ϑϑϑϑBIV = -5 ϑϑϑϑBIV = -2 ϑϑϑϑBIV = 0 ϑϑϑϑBIV = 2 ϑϑϑϑBIV = 5

Geyser 2 HT 90 Geyser 2 HT 70 Geyser 2 HT 60 Geyser 2 HT 50 Geyser 2 HT 32

[kW]

PTOL [kW] 48,9 36,5 32,0 27,3 19,6

COPTOL 2,36 2,22 2,29 2,36 2,20

PBIV [kW] 60,5 48,4 44,4 38,4 29,5

COPBIV 2,84 2,90 3,11 3,21 3,35

PA [kW] 58,1 43,7 38,4 32,2 23,4

COPBIV,A 2,75 2,62 2,71 2,74 2,63

PB [kW] 70,0 52,4 46,2 38,4 27,9

COPBIV,B 3,24 3,14 3,24 3,21 3,16

PC [kW] 77,4 57,7 51,1 42,3 30,7

COPBIV,C 3,57 3,47 3,58 3,53 3,50

PD [kW] 85,5 63,3 56,3 46,5 33,6

COPBIV,D 3,92 3,84 3,95 3,82 3,84



3. SELECT AIR/WATER HEAT PUMP UNIT “GEYSER 2 HT” - DEPENDING SIZE ON DIFFERENT

BIVALENT TEMPERATURES

� Resulting in selection No. 5 different sizes of Heat Pump:

� Geyser 2 HT 90

� Geyser 2 HT 70

� Geyser 2 HT 60

� Geyser 2 HT 50

� Geyser 2 HT 32


04/11/201457



4. GET Nr. 5 PARAMETRIC STRAIGHT:


04/11/201458

Annual Heating demand of the building

Annual Heat Pump Capacity

Annual power input with electrical heater

Annual power input without electrical heater

Annual Heating demand of the building

Annual Heat Pump Capacity

Annual power input with electrical heater

Annual power input without electrical heater

kWh kWh kWh kWh kWh kWh kWh kWh

35.427 35.427 12.584 12.584 54.368 54.368 19.306 19.306

SCOPon SCOPnet SCOPon SCOPnet

2,82 2,82 2,82 2,82

35.427 35.331 12.161 12.065 54.368 54.260 18.620 18.512


2,91 2,93 2,92 2,93

35.427 34.922 11.810 11.306 54.368 53.745 18.001 17.378


3,00 3,09 3,02 3,09

35.427 33.942 12.292 10.807 54.368 52.313 18.691 16.636


2,88 3,14 2,91 3,14

35.427 30.255 14.522 9.350 54.368 46.746 22.044 14.422


2,44 3,24 2,47 3,24

UFFICI HOTELOFFICE BUILDING HOTEL

ITEM 1

ITEM 2

ITEM 3

ITEM 4

ITEM 5



5. CALCULATION OF “SCOPon” FOR EACH HEAT PUMP SIZE


04/11/201459

2,82 2,91 3,00 2,882,44

1

3

5

7

9

11

13

15

-5 -2 0 2 5

MW

h/y

ea

r

Annual Power Input with Electrical heater and SCOPon

Annual Power Input with Elect heater SCOP_on

• Point of Minimum Energy

consumption

• Point of Maximum

SCOPon value

Application : OFFICE BUILGING



6. RESULTS:

Applying this analytical “SCOPon” approach, it is clear that the selection energetically more

convenient is on model GEYSER 2 HT 60, corresponding of a Tbivalent = 0°C


04/11/201460



7. COMBINED RESULTS: +Application : OFFICE BUILGING Application : HOTEL


04/11/201461

This is an analytical method that could be applied to optimize the heat pump selection.

However, it’s essentially defined only for heating.

In Italy, the application of the reversible heat pump (for combined use in summer and

winter) is much preferred and used in respect to "just heating" applications.

The strong sensible and latent loads in our "beautiful country" during summer, heavily

influence the selection of the size of the unit and very often the summer load is by far

predominant compared to the winter load.



7. REMARKS:


WHAT DO DO?

It’s not a simple question but some proposals or

better, Hypothesys - could be:

- Ice storage Bank

- Multiple HP units (in parallel);

04/11/201462

BIBLIOGRAPHY:

� DIRETTIVA 2009/28/CE del Parlamento europeo e del Consiglio, del 23 Aprile 2009, sulla promozione

dell'uso dell'energia proveniente dalle fonti rinnovabili, recante modifica e successiva abrogazione

delle Direttive 2001/77/CE e 2003/30/CE.

� DECRETO LEGISLATIVO 3 marzo 2011, n. 28. Attuazione della direttiva 2009/28/CE sulla promozione

dell'uso dell'energia da fonti rinnovabili, recante modifica e successiva abrogazione delle direttive

2001/77/CE e 2003/30/CE.

� UNI/TS 11300-3/2010. Prestazioni energetiche degli edifici. Parte 3. Determinazione del fabbisogno di

energia primaria e dei rendimenti per la climatizzazione estiva.

� UNI/TS 11300-4/2012. Prestazioni energetiche degli edifici. Parte 4. Utilizzo di energie rinnovabili e di

altri metodi di generazione per il riscaldamento di ambienti e preparazione acqua calda sanitaria.

� prEN 14825. Air conditioner, liquid chilling packages and heat pumps, with electrically driven

compressors, for space heating and cooling. Testing and rating at part load conditions and calculation

of seasonal performance.

� UNI EN 12831. Impianti di riscaldamento negli edifici - Metodo di calcolo del carico termico di progetto.

� «Il quadro normativo per l’efficienza energetica e la variabilità dei carichi negli impianti di

climatizzazione» - M. De Carli, Università degli studi di Padova, 27 Novembre 2013

� Gazzetta Ufficiale dell’Unione europea 06.03.2013 – Decisione della Commissione del 01 Marzo 2013.




04/11/201463



THANKS FOR YOUR ATTENTION

[email protected]


Heat Pumps in Energy Certification of the Buildings SCOP_SEER_Rel 28 10 2014 rev 01 lz

Engineering

Transcript of Heat Pumps in Energy Certification of the Buildings SCOP_SEER_Rel 28 10 2014 rev 01 lz