DE2350001A1 - Heat pump system for combined heating and cooling of houses - has heat exchanger whose flat components cover outside walls with exception of windows and doors - Google Patents

Abstract

The heat pump has plate shaped heat exchanger elements fitted on the outside wall of the building to prevent insulation losses. Openings are left for windows and doors. Additional heat exchangers can be formed by balcony railings, fencing and other parts not directly associated with the house itself. Heat exchanger panels are fitted on the side walls an on the roof. The coolant circulates through the heat exchanger, a valve, a compressor and a second valve. It passes through the heat exchanger nonreturn valve storage tank an overflow valve, a nonreturn valve and the heat exchanger. The coolant in the heat exchanger absorbs the heat flowing from inside the house which is usually lost to the environment. The evaporation temperature is not freely adjusted but it is subject to thermal equilibrium conditions.

Description

Lch Ullrich ■ 35C1 Ahnatal, September 29, 1975 -Ing. X & ssuler Si; ra-ie 25

Heating system, alternatively cooling system 23buUUl

The invention relates to a system for heating, alternatively and if necessary for cooling of buildings, especially residential buildings, according to the principle of the 'heat pump.

Such systems primarily pursue the purpose of being outside to extract freely available ambient medium ".v'ärme" of the target area and to use this as heating energy do. The equipment required for this is also suitable, as an alternative and, if necessary, also the cooling of rooms to a temperature below the ambient temperature.

Keben have this possibility of bifunctional use Such systems have the favorable property that their operation does not pollute the environment, a storage of fuels is not required and in particular direct energy costs only for a comparatively low, process-related necessary share of the total heating energy to be drawn from the electrical power grid.

The operation of such systems assumes, however, that sufficient favorable conditions for heat exchange exist on the media side and economic efficiency also under Consideration of the investment costs is given. These requirements exist in known systems, which Use a natural or artificial body of water as a "heat transfer medium. Because of the location dependency, the However, there are narrow limits to the application of such a solution. It is also known to be the atmospheric available regardless of location To use air as a heat transfer medium. However, the heat exchange with air requires large exchange surfaces, which may still have to be ventilated, which has a detrimental effect on the system costs and also Problems of accommodation raises. So it is, for example '

509815/0721 g ^ ^, awai ^{/ 2}

. Heating system, alternatively cooling system

.difficult, open-air systems, which are still more natural / lonvection, .could to build in residential areas. The arrangement of a heat exchanger within a building, however, requires additional enclosed space and in principle Forced ventilation, which in addition to increased investment " and operating costs still cause noise. co

Finally, it is "at least theoretically still known to carry out the heat exchange with the surrounding soil.

O This procedure is also due to the large _a 3en construction costs not very satisfactory; it also sets requirements for floor area and floor space that cannot be met in general And makes the system unfriendly to repair.

The circumstances described are the reason for the fact that heat pumps, despite their excellent properties so far as heating systems have not found widespread use, as was the case with respect to environmental protection ■ and the Conservation of energy reserves, but also for the benefit of the user, would be desirable.

The invention has set itself the task of removing these obstacles and making an economically competitive one Use of the heat pump for heating, alternatively and if necessary for cooling, of buildings, in particular V / without buildings, independent of the edge of the beach.

The solution is based on the basic idea of the invention of replacing the media heat used in known systems with insulation losses emerging on the building surfaces and thus virtually thermally passivating most of the building surface by recovering the insulation losses. This is inventively achieved in that the switched as an evaporator in heating mode the heat exchanger of a heat pump at least the protruding out of the ground portion of the outer surface of a heated, alternately and as required full area to be cooled building with the exception of windows, doors and other passages as ^possible: chig covered and shielded from the environment.

509815/0721

ORIGINAL

Ksinrich Ullrich, Aimatal;
Heating system, alternatively cooling system

• ι. ⁼

The invention also provides, not directly Flat structures belonging to the building surface such as balcony railings, property fencing, privacy screens and the like, if necessary and in the alternative, to be designed as a heat exchanger and for the exchange of heat with the surrounding air. Further embodiments of the invention are in the following CD the following description and listed in the claims. . -.

The description of the subject matter of the invention goes assume that the structure and mode of operation of a heat pump are known per se.

In Figure 1 is. an inventive arrangement of the heat exchanger (1), consisting of individual parts (1a) and (1c), shown using the example of a V / ohnhaus.

It is particularly advantageous to design the individual parts (1a) and (1c) in a plate construction known per se. The individual parts (1a) cover the wall and roof surfaces of the building and at the same time replace conventional forms of the Wall surface design (external plaster, facade panels) and roof covering. ·.

It is economically advantageous to use the The modular principle of using individual parts (1a) and (1c) of standardized dimensions and individual parts (1a) to be attached only to such surfaces, which allow an uncomplicated arrangement due to their geometry. Remaining If necessary, remaining areas are used to achieve a uniform overall appearance dressed and disguised dummies that are passive with regard to the heat pump process. A possibly in purchase Any waiver of an effective heat exchange surface can, if necessary, be done by attaching additional individual parts (1c) outside the actual building surface area be balanced. The division of space and occupancy takes place in individual cases according to the aspects of the Expediency. The invention makes in this regard no str -: -:;:; en regulations and iä3t der architektonioche-i .ι ο j val; in ~ extensive "leeway.

509815/072 1 BATH

Heinrich Ullrich, Ahnatal;
Heating system * alternatively cooling system

Figures 2 to 6 serve for derivation and explanation ier thermal relationships of an invention System; show it

Figure 2: the circuit diagram of a system according to the invention, in section through a residential building.

Figure 3: the block diagram of the heat flow during heating cd operation. __ ^

Figure 4: the T / S diagram of the cycle of the heat pump in heating mode.

Figure 5: the block diagram of the heat flow during cooling operation.

Figure 6: the T / S diagram of the cycle of the heat pump in cooling mode.

The abbreviations used in the representations and derivations mean:

ρ F total external surface of a building (m)

F building surface covered by the heat exchanger (1) (m)

F not covered by the heat exchanger (1)

2 building surface (2o), loss area (m)

F _L Air-side surface of the heat exchanger (1) (m)

k Heat transfer rate interior (17) - heat exchanger • (1) (Kcal / m -h-grd)

k _T Heat transfer coefficient, environment (21) - heat dissipation

exchanger (1) (Kcal / m «h-grd)

k V heat transfer rate of the loss area (20)

(Kcal / m ² h.grd)

509al 5/0721 SAD original / 5

Heinrich Ullrich, Ahnatal; . -Jjs.

Heating system, alternatively cooling system

k. Thermal flow rate indoor (17) - environment (21)

on the v / andflachen (18), in the case of one not according to the invention Plant (Kcal / m · h «grd)

t _D room temperature (deg. G) N5

ty ambient temperature '(degrees C) ^

ty, evaporation temperature (refrigerant) (deg C)

t ₂ superheating temperature (refrigerant) (deg C)

t, condensation temperature (refrigerant) (degrees C)

tr subcooling temperature (refrigerant) (deg C)

T .. absolute temperatures (degrees Kelvin)

p ^ saturation pressure in the evaporator (ata)

Pp saturation pressure in the condenser (ata)

i ^ l Enthalpy of the dry saturated refrigerant vapor at the evaporator outlet (Kcal / Kg)

ip enthalpy of the superheated refrigerant vapor (Kcal / Kg)

i, - Enthalpy of the supercooled refrigerant condensate (Kcal / Kg)

ig enthalpy of the liquid / vapor mixture

Throttling at the evaporator inlet (Kcal / Kg)

Q _R the interior space (17) for heat (Kcal / h) resp. withdrawn heat

Q heating demand of a building with not

heating system according to the invention (Kcal / h)

^C "" ^{1R / n} " ¹ WMWlL

Heinrich Uliricn,

Heating system, alternatively cooling system

6-

) ν

exchanged heat (Kcal / h)

Q between interior (1?) And heat exchanger (1)

heat exchanged between environment (21) and heat exchanger (1) (Kcal / h)

Q _T r from the refrigerant in the heat exchanger (1) to ge ^!

Heat taken or given off (Kcal / h) CD

Q Heat lost from the interior (17) directly to the surroundings (21) '' (Kcal / h)

L electrical absorbed by the motor (3)

Power (Kcal / h)

L effective compaction performance (Kcal / h)

jn resulting efficiency of

Motor (3) and compressor (2) '(Kcal / Kcal)

7 Efficiency of a combustion heating system (Kcal / Kcal)

£ Heat index in heating mode (Kcal / Kcal)

£ _k Cooling factor in cooling mode (Kcal / Kcal)

The mode of operation of a system according to the invention is the following:

In heating mode, the heat exchanger (1) is connected as an evaporator; the valves (8) and (9) stand up Passage, the "valves (TO) and (11) are closed. The refrigerant circuit follows the one fully drawn out in FIG Line in the heat exchanger (1)

- valve (8) - compressor (2) - a - b - valve (9) heat exchanger (4) - Check valve (12) - Storage tank (6) - 3xpension valve (7) - Check valve (13)

- heat exchanger (1).

■. 's

^v 5098-15 / 07 21 bad ORIGINAL · / 7

Heinrich Ullrich, Ahnatal;
Heating system, alternatively cooling system

The compressor (2) is driven by the motor (3).

The refrigerant in the heat exchanger (1) absorbs, through its side facing the building surfaces, the V / poor that flows out of the interior space (17) and is normally lost to the environment (21), while on the side facing the environment (21) the (jj heat exchanger (1) a heat exchange with the environ- £? bung (21) takes place. the heat exchange with the environ- ο bung (21) may in this case, depending on evaporation and environmental __ ± gebungstemperatur, positive or -negative The evaporation temperature is not freely selectable, but, as will be shown, adjusts to a certain value as a result of thermal equilibrium conditions Interior space (17), where it, increased by the compression capacity, is delivered to the heat exchanger (4) and by means of a conventional secondary circuit (16) the individual needs is supplied. The thermal equilibrium is established when the sum of the heat supplied by the heat exchanger (1) and the power grid covers the losses that occur on the building surfaces (20) that are not shielded by the heat exchanger (1) and through convection at the outlets.

The .quantitative connections of the steady state are derived below. The derivation goes in favor of the clarity and emphasis of the for the Invention characteristic relationships of the following Simplifications from:

1. Let the building be covered by media (air, earth) on all sides (21) uniform ambient temperature t "surrounded.

2. The products ^ \, F _y · k _y , P ^ k _L are to be understood as integral mean values.

509815/0721

Heinrich Ullrich, Ahnatal;
Heating system, alternatively cooling system

3. The temperature on the surfaces of the heat exchanger (1) is the same as that of the refrigerant it contains.

4. All interior rooms of the building are heated _{to a uniform room temperature t D.} It is therefore sufficient to summarily as a single compartment (17) loading _<J1

. Act. ^<=)

5. Compressor (2) and motor (3) are considered to be arranged in this interior (17). The one in terms of compaction performance L portion (1 - ^) 'L of the electrical power L, which is initially considered a loss, therefore falls as Heat can also be used. This corresponds to the concern of the invention, heat at any location within to provide a building; the question of their distribution is only of limited relevance for them.

6. The convection losses at the passages such as windows and doors are considered to be due to a fictitious area in the Product F · k taken into account.

7. Heat exchanged by radiation with the surroundings (21) is not applied.

8. The compression of the dry saturated refrigerant vapor successes adiabatically.

The heat coefficient B is defined as the ratio of

usable heat 'Q' for the electrical power used L, so

The usable heat Q "is made up of the longitudinal the line 2-3-4-5 (Fig. ^) at the Y / heat exchanger (4) Heat i ~ - ic plus that which is immediately converted into heat Share (1 - ^) »L of the electrical power L,

509815/0721 ^{/ 9}

Heinrich Ullrich, Ahnatal; "

Heating system % alternatively cooling system ¹ J '', '

Q _R = i ₂ - χ, + (1 -7 "). L; (2)

Hence £ through the state variables £ Les Kälre-Tiittels determined in the cycle.

From the balance of the quantities of heat supplied and removed it follows (see Fig. 3) « _tSJ

Q _R = Q _k + L (6)

Q _k = Q _w +. Q _L. (8th)

and according to Eq. (1)· *

3 _h = £ _w -l. ■ (9)

509815/0721

since the enthalpy remains constant when throttling from 5 to 6, this also applies

Q _R = ip - i ₆ + (1 -?) - L; · (2a) <o

^c ° ^L - - cn

in it is - ".

i ₂ - I ₁ = / 2 ' ^L (3)

equal to the effective compression power L and supplied along the line 1-2

i, - i ₆ - Q _k

same as along the line 6-1 'on the heat exchanger (1) absorbed heat. From the equations. (1) to (4) follow

_{/ 1f)}

Heinrich Ullrich, Ahnatal;
Heating system, alternatively cooling system

-40.

The approach to heat transfer delivers

-V ⁽¹⁰⁾

= VV ^(t R - V

From the equations. (6) to (7) follows. The evaporation temperature

(g _w -D- (WW _t ,

^{) #t} V ^k L> ^E " ^ü

and the required electrical "power

τα- ^ V ^k w + VVf ^{1 +} / F ₁ Z _1. ) (WJ

For the characteristic case with F _T = F, one can use Eq. (13) and (14) still simplify

^{s u}

= (t _R -

ti

In order to arrive at a generally valid statement, it is useful to apply the power requirement to the total area of the Building.

509815/0721

/ 11.

Heinrich-Ullrich, Ahnatal;
Heating system, alternatively cooling system

"Years of attention from

? = F _w + P _v ■ (17)

you get

(F / FVk ₊ (1- F / F) - (I + V ^k L ^{)> k} v

L / F = (t - t _u ) - ^Ji

^{K u} c + ¹

From equ. (18) can already be a number of more practical Derive measures to minimize the power requirement:

--j cannot be influenced as a meteorological variable; t ^ is one that is determined by the task at hand Constant and cannot be influenced either. Low values of k, i.e. one as possible, have a favorable effect good insulation of the loss areas -F (20).

Maximum values are to be aimed for for B, as already w

The possible interventions with regard to €. result from equation (5) · In this, »is given by the state of the art, t * is essentially predetermined by t« and tg according to equation (15). Optimal values for ip and Ir- result when t ^ and t ^ _{strive towards the limit value t R. The} prerequisite for this are low gradients on the heat exchanger ('4) at low flow and return temperatures of the secondary circuit (16). The latter is better with a warm air circuit than with a hot water circuit.

The influence of the other parameters can be seen better if one looks at the partial differential quotients of Eq. (18) forms. It is

_ct · _ty ^k w- V
- ^lt H u ^; a +

5 0 9 815/0721 ΒΛΟ OHlQiWAi ^{/ 12}

Heinrich Ullrich, Ahnatal; '

Heating system, alternatively cooling system

. _{(t τ} V (, HV) V \ ₍

V ^F - ^(£ w - ^{1) # (1} -

is also, the differential quotient according to Eq. (21) equals zero, that is, k _L is then no longer relevant with respect to L. If one leads the condition of this case into equation. (15) and (16), then t _/] = ty and L * (t _R - ty) -I ¹ ^ k ₇ .. Since there is no heat exchange between the heat exchanger (1) and the environment due to the lack of temperature gradient (21) can take place, the heat exchanger (1) in this state has the character of total insulation from the Us-febmi with regard to the building surfaces (18) it covers; (21), and the electrical power grid

according to the fact that exterior walls .otezs a better one Effecting thermal insulation as windows and doors is also k - k · (1 + k / k-r) and thus the differential is quorient according to equ. (19) always negative, i.e. i.e. increasing values from 3? / F are assigned falling values of L. the end

This relationship is followed by the practical consequence of shielding as large a part of the building surface as possible by means of the heat exchanger (1), although inevitably 'F _w / F must always remain less than 1.

The differential quotient according to Eq. (20) is because of £> 1 always positive, so that minimum values are to be aimed for for k. This requirement can easily be met by placing the heat exchanger (1) in a space (19) forming a spacing from the wall surfaces (13) and optionally also with the intermediate space (19) Insulating material provides.

The GIg. (21) makes differentiated and for the invention at the same time characteristic statements.

In the case

509815/0721 B.

^L (k _L = 0) = ^L max

and

τ τ w * w ⁺ ν 'ν. , -> ^L (k _L = 1/0) = ^L min = J ^ ₁ ^(t R ~ V

So it turns out that even with infinitely great Fluctuation of ic. the system only with a finite

Il

Heinrich Ullrich, Annatal; ,
Heating system, alternatively cooling system

only needs the equivalent for the to the not from the '.varmeaustauscher (1) covered building surfaces (20) resulting losses Q = (t ,, - t * j) * F. »K. In such a case, the system works completely independently of the media; Medium in this sense is, so to speak, the one Part of the building itself which, due to its finite insulation properties, essentially meets the heating requirement

borrowed in the first place.

In general, however, Eq. (22) must not be fulfilled - ^x already because it is _{not indifferent with regard to t f} , so that an influence of k _T remains. The tendency of this influence must be checked on the basis of concrete data.

In practice, you can calculate with the following values:

F / F = 0.4-0.7; k / k = 1 to 2; £ = 3 to 6.

W "V W W

For the function according to equation. ' (22) result in values between +0.1 and -5.4-, so that the differential quotient according to Eq. (21) is consistently negative. Therefore, for kr to strive for maximum values. For the GIg. (15) and (16) follows-from it

t ^ less than / equal to t ^; L less than / equal to (t ^ -t-g) F k.

Overall, however, the influence of k _{T is} small, as a consideration of the -physically unrealizable-limit values k / = 0 and kr towards infinity shows:

With L = f (k _L ), Eq. (16) over in

509815/0721

Heinrich Ullrich, Ahnatal;
Heating system, alternatively cooling system

and relatively small fluctuations in performance requirements L reacts. ·

In practice, this means that the heat exchanger (1) - in the sense of low construction costs - on mine the surface facing the surroundings (21) is not white Should have isolation, but such if it is desired or unavoidable for any reason N>

is not particularly harmful. Oi

This fact is of particular importance when the surfaces of the heat exchanger (1) tend to freeze or are covered with snow under the influence of ο low evaporation temperatures t * and high relative humidity. Even if the heat exchange with the environment (21) is almost completely prevented, the system works with a power requirement in the range between the values of the GIg. (23) and (24) lying still economical. The less heat then supplied by the environment (21) is compensated for by the fact that the evaporation temperature t, * with an associated decrease of 8 and the associated increase of L decreases until it is equalized.

These relationships make it clear that an inventive Plant basically no special surrounding medium at all is required for heating operation and can advantageously be used without restriction if only the product F · k can be kept sufficiently small. The idea of the invention finds its general confirmation in this. The limit value according to Eq. (23) also provides a rule of thumb for the maximum expected power requirement of a according to the invention and provides the product F · k as one of the, major extras.

The above-described icing of the heat exchanger (1) can of course also occur on the building surfaces (18) facing side occur. At this point, however, it is completely harmless and actually even cheap because it leads to lower values of k.

BATH ORIGINAL 509815/0721 / 15

Heinrich Ullrich, Ahnatal;
Heating system, alternatively cooling system

If one compares the performance sea demand of an inventive System air that of a conventional system, which the usable heating energy entirely from fuels or must convert electrical energy, the following results :

The heating demand of a not heated according to the invention

th building is cn

% = ^(t R - V- (V ¹ W ⁺ VV ^; ■ - ⁽²⁵⁾

taking into account a system efficiency η is then the power requirement

'■ o "

From the equations. (16), (25) and (25a) then results as Performance ratio

> -ce _{w +}

however, in the case of purely electrical heating, ^ ₀ = 1 must be set.

The distinction between 'k _w and k _WQ is first necessary because the two comparative cases have different conditions for heat transfer on the building surfaces (18). exist. ·

For a clear and rough estimate, however, one can approximately set k _WQ = k _w and also _{neglect k w} / kr compared to 1 and £ _w and get as an approximate value

_(2Sa)

If the comparison is made under the most unfavorable conditions for a system according to the invention according to Eq. (23) on, one obtains as a minimum \ '

509815/0721

Heinrich Ullrich, Ahnatal; Heating system, alternatively cooling system

ge

L _o / L = 4.8 / 0.8 = 6

synonymous with the fact that in this case a system according to the invention only requires one sixth of the energy requirement caused by the furnace heating compared to it with the expenditure of energy costs. A comparison of the Pure energy costs must of course also take into account the different delivery prices of the individual forms of energy.

That by GIg. (26) defined performance ratio under the influence of those not taken into account in Ans & fcz Basically improved solar radiation in favor of a system according to the invention, in which the Radiant heat does not serve to heat up the irradiated surface as is usually the case, and thus partially back to the Environment (21) is lost, but from the heat exchanger (1) recorded and fed directly to the Iloiz process will.

To illustrate the order of magnitude, the statement the GIg. (26a) can be demonstrated using a practical example:

If you run the refrigerant, z. S. difluorodichloromethane, co Heat in the heat exchanger (1) at a temperature of t "= 0 ° C and in the heat exchanger (4) at temperature

'ο ο

If the temperature drops between t ~ = 60 C and te = 4-0 C, then with an efficiency of motor (3) and compressor (2) of ti = 0.8 according to Eq. (5) a heat coefficient of £ = 4.8.

:>: with a system efficiency of a combustion heating system of = 0.8 then according to Eq. (26a)

509815/0721

'Ioinricr. ".llrich, Ahnatal;

: .ci ^ · -. :: "c & nla = 'e, alternatively cooling system

Ji: - erii: .d.ur: 5or = 3rr, the external system can - like any other heat pump intended for -V-izzwecL'ie - alternatively and if necessary, the heat exchangers (1) and (^ i- ) can also be used as a cooling system as soon as the "JiT:> buntstem c era door t _f j is above the desired ßaumternoerabur t _: -. ~ t. To do this, the valves (10) and (11) are opened, (8) and ( The refrigerant circuit then follows the line of FIG. 2 in the order heat exchanger (4) - valve (11) - compressor (2) - a - b - valve (10) - ^; .7 heat exchanger (1) non-return valve (14) - storage tank (6) - expansion valve (7) - non-return valve (15) - heat exchanger

Deriving the quantitative relationships is based on the? I _; -ur 5 and 6 and uses the simplifications introduced on pages 7 and 3 of this description with the exception of item 5 p. 8; instead it is assumed and in Fl ':. 5 shows that the loss component (1 -> p) * L · of the electrical power L is dissipated directly to the environment (21) and the cycle process is applied. The cycle process is fundamentally qualitatively the a-corpse v / io in Fig. 4, but the absolute position of t ,, · and the relative position of tp in Pi ?. G sic: i re ^ inlert.

The cold coefficient results from

(27)

Compared to 6 , the additive term +1 is missing.

speaking of the changed requirements regarding, (1 - * 9) · Ιι From the heat balance it follows (cf. «i'ig« 5)

5098 15/0721 BAD Of ^ IÖfNAI *

Heinrich Ullrich., Annatal;
I-Ieizungsanläze, alternatively IIii ':: l ^ nlaf: e

is according to the definition

; V = f _fc l (31)

The approach for the V / arm passage provides

From the equations. (25) to. (5 ^) follows the condensation temperature t ^

(t "- t,

and the required electrical power

For the characteristic case with F _T = F one can

Yy w

lie GIg. (35) and (36) still simplify

/ F). (K / k _L )

^ - ^ '^ u-V C37)

L ¹ ft t)
L = -. (T _n - t _R )

509815/0721

BAD ÖftlGWAL

ieinrich Ullrich, Ahnatal;
-ii'un-o'anlace,? .lternar.iv ICühisr-lag

.- "/ and Mv) ϊο! ~ ζ the flat egg speciic

? ^{ϋ il £} k ¹ V ^ L cn

SIg. (39) allowed; an immediate classification of the q laraneter in terms of performance minimization, "*

According to this, for £ -, and k _{T are} as high as possible, for k, and k

as low as possible, fourth cheap. With regard to F / F: r.sn v; egeii the analogy to the statement of equ. (19), according to which a maximum value is to be aimed for.

The power requirement according to equ. (39) can be further reduced by this be that the building surface (16) facing side of the heat exchanger (1) 'of the ambient air exposes by the gap (19) by means of openings (22) allowing free convection with the 7 "area (21) is connected. The ambient air is brushed Then, as a result of the chimney effect, the rear of the heat exchanger will open to you (1), what in effect and with regard to equ. '59) equates to an increase in k-r. At Pleizbetrieb The openings (22) can be allowed to prevent them from occurring Convection through movable flaps or slides (23) getting closed.

l "in a comparison of the relationships between heating and cooling operation shows perfect agreement of the qualitative influence of all parameters. This agreement is significant because they basically allow the bifunctional use of a system according to the invention without the constraint Compromises allowed.

The gig. (18) and (39) are now to be appreciated from the point of view: the provision of services. Both Cileichun-ren have actual <learning approach to the condition that the vcm electric power network provided in performance. Eggs Au ~ er.r-1 i ^n., But changing

509815/0721 / 20

BAD ORlQfNAL

Heinrich Ullrich, Ahnatal;
Heating system, alternatively cooling system

Power requirement. The power requirement is not - as it initially appears - the prevailing temperature gradient t _TT - t-, or t-, - t _TT propor-

u it η. υ (Ji

tional, but because of the temperature-dependent S? dependent influencing variables £ or £ ,, k, k ", and k a CD

approximately parabolic course.

An exact power adjustment would make the continuous one Require operation of the compressor (2) with stepless and needs-based regulated power of the motor (3) and lead to an inappropriately high regulatory effort. In principle, however, it is sufficient to increase the installed capacity according to the expected peak demand L. dimension and the demands of the gig. (18) and (3?) According to normal practice by intermittent Operation - e.g. B. by means of two-point control - to meet on average over time, f-iit consideration of the at least It is advantageous to use the nominal power of the Kotors (3) at least in rehearsal stages the seasonal Adjust as needed in order to meet the most favorable conditions with regard to GIg. (18) and (39) as well as the Repelunfrsdynamik. A further embodiment of the invention therefore provides before, the compressor (2) by means of at least two selectable Anriiebsdrehcahlen enabling i-.otors ($ "), for example a pole-changing motor to drive. In times of high demand, the system then works in such a way that the compressor operates in a quasi-continuous manner (2) is alternately driven with a higher and a lower speed, which one each ι · performance above or below the momentary requirement! is equivalent to. If there is a need for performance in times of low demand drops below the value corresponding to the lowest speed, then there is only intermittent operation at the lowest Speed switched. The Umschaltune on the individual Power levels can be set manually or by disturbance

the ; ^: rr; ~ eburj ^ stemperature t- take place.

509815/0721 gAD - ORIGINAL

Heinrich Vllrich, Ahnatal; -?

: -Ioizur:; -: sanl5 "e, alternatively cooling system

Λ * ·

3chlie31i;: 'r. I: sr.n an eri ^v i: iIurL. "- s -_: emäß AnIa,: - j 5; ov / ohl with heating as well as with r" Ihlbo: rubbed in v'irbirilun-; ? .it airier l / ar.T.wasser '/ ei ^ sor.jun ^ bee to be rubbed. . jsj

It isr appropriate to the service water ζit using the ^ω heat pump only to a specific, preheat between about i'p and -ο T, lying I'experatur _t and optionally ς-y by means of a nachgeschaltefcsn, including electrical Hei · - * ■ Bring the tongue (24-) to the desired final temperature. Such a procedure is therefore advantageous ^; because sons ζ ier shown in FIGS · '+ and 6: "r: -eispi ozsss regarding the temperatures Tp and f under tarry aaf r.aximale £ Uird £ ■, according to the requirements?

W IV

the domestic water temperature would result, d. h., with higher le: r.reraruren? p and T- than read the main purpose • Ier plant required.

The maximum preheating temperatures are obtained without harm in this respect, if one - - in the poorer (5) of the service provider (5) chests in such a way that he is in the area of the overheated mal- l'emi ^ töidair.pfes 3us candspunkren 2 and 3 'Jer ^ iruruii ^ and 5 works. The 3rauchwasservorwär.T »er (5) is then switched in" igur 2 instead of the continuous connection between the connection points a and b of the Xälteinit- · telkreislaufes.

The decisive advantage of an inventive system is yours based on the equation. (18) to (24) proven, extensive and, if necessary, complete independence from the media in heating mode; it allows it, while preserving all other, known and typical advantages a 7 / heat pump, this a wide and location-independent To make the application accessible in the sense of the task at hand. . · The invention creates through the consistently possible use of standardized, commercially available and series manufacturable parts. as well as the elimination of conventional construction measures in terms of facade protection and roofing at the same time, prerequisites which, even in the case of smaller units, e.g. single-family houses, have an economic Enable creation of the system.

5098 15/0721 _{/ 22}

BATH

Claims (1)

Heinrich Ullrich, Ahnatal;
H-3Jzuni: s? Nla "e, alternatively cooling system ρ a ^.: τ a :: ä ρ R O c H s ., miia: e zur ^ eheizunp ;, alternatively and if necessary for cooling, of buildings, in particular residential buildings, according to the principle of the .v'ärT.epumpe ¹ , characterized in that the heat exchanger (1) switched as an evaporator during heating operation a heat pump at least the part of the outer surface (18) of a building that is to be heated, alternatively and as required to be cooled, with the exception of the windows, doors and other passages i;. if possible it; covered. 2. System according to claim 1 --.- ekennZ ύ rejects, -Zai:: ± τ heat exchanger (1) in -iaukastenbauweice from before - :; eggs ~ irten, preferably 'standardized, flat: iir: zülteile (1a) to an envelope simulating the building contours in sample lashing is joined together. 3. Plant according to claim 2, characterized in that 'ia .; : lie Individual parts (1a) of the heat exchanger (1) are designed in a conventional plate construction. 4. Plant according to one of claims 1 to 5 characterized in that the heat exchanger (1) is in a space (19) forming distance from the building surfaces (18) covered by it. 5. Plant according to claim 4, characterized in that the Intermediate space (19) in connection with the surroundings (21) by means of openings (22) which enable free convection stands. 6. Plant according to claim 5, characterized in that 'that the Openings (22) can be closed by means of flaps or slides (23). 7. Plant according to claim 4-, characterized in that the Verseheil intermediate space (19) with a heat-insulating filling is. 509815/0721 BAD ORIGINAL / 23 Heinrich'Ullrich, Ahnatal; e, alternatively räihlanlage 5. System according to claim 2 and 3, characterized in that the -individual parts (1a) of the '.VänueaustauscLers - (1) on the j he lebautenocerflache (18) facing side with a -A ^ rnreisolierenden covering are provided. OO ?. Plant according to one of Claims 1 to 8, characterized in that the heat exchanger (1) on the environment 21) facing side with a weather-protective and decorative Surface is equipped. » "O. system according to one of claims 1 to 9 characterized characterized in that the heat exchanger (1) in the sense of claims 1 and 2 not covered fixed surfaces of the building surface, 3 :: e (18) by means of dummies prepared as required (1b) are disguised. Ά * System according to one of claims 2 to 10, characterized in that the individual parts (1a) of the 'heat exchanger /' ^{Λ are} integrated components of prefabricated building elements t: z in the sense of prefabricated construction. 12. Plant according to 'one of claims 1 to 11 characterized, in that additional items (1c) of the heat exchanger (1) using railings. o Light protection screens and similar planar structures or in their place outside the area of the building surfaces (18) are arranged. 13 · Plant according to one of claims 1 to 12 in that the compressor (2) by means of a motor (3) which enables at least two drive speeds » preferably a pole-changing motor, is driven. 509815/0721