A METHOD AND A METER FOR MEASURING QUANTITIES OF HEAT

Abstract: A method and a meter for measuring the quantity of heat abstracted from a circulating flow of liquid by a consumption unit based upon the indirect measurement of the volume flow rate of the liquid, while maintaining a sub heat flow (Q shunt) from or to the main heat flow transported by the flow of liquid and measuring the temperature at some points by means of temperature sensors (4), whereby the volume flow rate of the flow of liquid is determined on the basis of the flow rate dependent heat transfer in the boundary layer (7) of the flow of liquid at the location, where the sub heat flow (Q shunt) leaves or enters, by determining the temperature differential (//cT<ui>u,<ub>u) across the boundary layer, and the sub heat flow (Q shunt) passing through said boundary layer (7), while at least one absolute temperature of the flow of liquid is measured for correcting the temperature dependency of the material constants of the liquid involved in said determination of the volume flow rate.

Description: - A method and a meter for measuring quantities of heat. The invention relates to a method and a meter for measuring the quantity of heat abstracted from a circulating flow of liquid by a consumption unit based upon the indirect measurement of the volume flow rate of the liquid, while maintaining a sub heat flow from or to the main heat flow transported by the flow of liquid and measuring the temperature at some points by means of tempera¬ ture sensors. Such a heat meter may for instance be provided in city heating networks for consumption on small scale by the con¬ sumers. In future, city heating networks will be used in a pro- gressively increasing number of towns and districts in which each house will obtain a connection to a public heating network in¬ stead of its own boiler for central heating. From this connection the consumer will obtain the hot water for his home heating sys¬ tem and tap water supply either directly or indirectly by means of a heat exchange. It has become evident that the consumption in total of this city heating decreases when the amount of heat consumed is mea¬ sured at every separate consumer. From the heat quantity meter the consumer will than have an idea of the cost of his heating, rϊOx this reason the installation of heat quantity meters for con¬ sumption on small scale is considered to be useful. The existing meters often have the drawback that they are not accurate enough, such as for instance evaporation meters, or that the initial cost and/or maintainance cost are too high such as in case of meters including turbine parts. The object of the invention is to provide a method and a heat quantity meter not exhibiting the above mentioned drawbacks among other things by the complete absence of moving parts or measuring flanges in the flowing liquid so that there are no obstructions in the supply and return conduits. This will lead to a consider¬ able decrease in maintainance of the meter. In accordance with the invention this object is attained in that the volume flow rate of the flow of liquid is determined on the basis of the flow rate dependent heat transfer in the boun- dary layer of the flow of liquid at the location where the sub heat flow leaves or enters, by determining the temperature dif ferential across the boundary layer and the sub heat flow pas¬ sing through said boundary layer, while measuring at least one absolute temperature of the flow of liquid for correcting the 5 temperature dependency of the material constants of the liquid involved in said determination of the volume flow rate. The operation of the heat quantity meter is based solely on the measurement of a number of temperatures. Therein use is ma of the fact that the heat transfer between the heat carrier or ■ Q flowing liquid and a body, in which or along which this liquid is transported, is dependent among others on the flow rate of the liquid at the pertaining location. The more this flow rate increases the better the heat transfer will become. It is now aimed at measuring this coefficient of heat transfer. r c. When employing this method well measurable temperature diffe¬ rentials occur without being accompanied by large and conseque ly inadmissable heat losses in the main flow as will be the cas in a thermal flowmeter. In a known flowmeter as is for instance known from the French Patent Specification 2,353)045 one ' tries 20 "to minimize the influence of the laminar sub or boundary layer among others by a special shape of the wall surrounding the flo of liquid. In the present method and meter precisely a measure¬ ment is performed of the coefficient of heat transfer of the la mi ar sύb layer of the flow of liquid considered to be turbulen 25 Where this measurement can not be performed directly a sub or leakage heat flow is allowed to form which is dependent on the coefficient of heat transfer. For this purpose there is provide an energy connection or in particular a thermal connection betwe the supply and drain or return conduit. 30 In the connection thus provided there will occur a heat flow dependent on the difference in temperature between the hot wate in the supply conduit and the cooled water in the return condui as well as on the total heat resistance. This total heat resis¬ tance consists of a fixed component determined by the thermal j c connection possibly in combination with the walls of the con¬ duits, and of a variable component mainly determined by the flo of the liquid in the thermal boundary layers. The magnitudeof - J this branched heat flow may be measured by means of a tempera¬ ture differential measurement. The magnitude of the temperature differential across one or both of the boundary layers together with the magnitude of the heat flow through the connection de- ter ine the coefficient of heat transfer in situ. In the general case of an energy connection- apart from the heat flow by conduction, radiation or convection there may also occur a heat transport due to thermo-electric effects if the con¬ nection is electrically conductive. The electric current genera- " ted in this case possibly by the Seebeck effect will than be a measure for this form of energy or heat transport. The absolute temperatures of the flows of liquid at the loca¬ tion of the boundary layers are also of importance, because the relevant material constants, like the coefficient of heat conduc- tion, the specific heat c (weakly), and the vicosity γ> (strong¬ ly), are dependent on temperature. The coefficient of heat transfer together with the several ma¬ terial constants fixedly determine the velocity gradient in the boundary layer. If moreover the velocity profile in the conduit is yet also governed and reproduceable than there will be an un¬ ambiguous relation between several temperatures and the volume flow rate of the liquid and consequently " between these tempera¬ tures and the net ' heat flow rate; * * The signals supplied by the temperature sensors are processed in accordance with an empirically determined relation by an elec¬ tronic unit into a quantity of heat per each unit of time or a time puls per quantity of heat. By employing an integrating, sum¬ ming or pulse counter circuit in the electronic unit one will ar¬ rive at a total supplied quantity of heat per each chosen period of time. By having the meter constructed symmetrically both the volume flow rate in the hot supply conduit and in the colder drain con¬ duit may be determined and compaired with each other. The present invention will now be elucidated further with re- fererce to an embodiment as an example disclosed -in the annexed drawings, in which: Fig. 1a shows a basic sketch of the conduit sections including a thermal shunt connection of the heat quantity meter; OMPI Fig. 1b shows a side elevation of a part of a conduit section having a bar shaped shunt connection according to Fig. 1a faste ned thereto by means of an angular junction; Fig. 1c discloses a diagrammatical view of the heat quantity meter including its temperature measuring points and the imagi¬ nary heat resistances R1 to R4, inclusive; flow rate Fig. 1d discloses the relation between the measured volume/an the measured temperatures; Fig. 2 shows a " side elevation of a production embodiment of t heat quantity meter; Figs. 3a, b, c and d show a side elevation of four variants o the junction of the shunt connection to a conduit section; and Fig. 4 shows a side elevation of a variant of the location of a temperature sensor. With reference to Fig. 1a there has been shown a basic sketch of the meter in which the reference numeral 1 indicates the sup ply conduit, the reference numeral 2 indicates the drain or re¬ turn conduit and the reference numeral 3 indicates the bar sha¬ ped thermal shunt connection. The temperatures Tl. , T,b,' To,' Tu o temperature differentials may be measured by means of sensors 4 > such as thermo-couples, to which a sensitive amplifier is con¬ nected. The thermo-couples may be solded onto or into the ma¬ terial. With reference to Fig. 1b there has been shown a side eleva- tion of a cross section of the angular junction of the termal shunt connection 3 "to one of the conduits 1 or 2. Likewise the laminar boundary layer 7 of the liquid at the tube wall of the conduits has been indicated. The referenc numeral 4 denotes the junction contact of the temperature differential sensor. This temperature differential sensor may also consists of two separat absolute temperature sensors. For this type of heat transfer problems as in the boundary layer one may apply a theory known in the theory of flows as the so called "film theory". In the turbulent flows of liquid as will occur in the supply and the drain conduits one may conside the larger part of the velocity gradient and the entire tem¬ perature gradient to be in the laminar sub layer at the wall. I general one may start from the empirical relation: G 0,14 Nu = 0,024 (1 + §) °' 6β • Re 0 ' 8 - . Pr 0,33 (1) in which: Nu is the Nusselt number which is a measure for the coef¬ ficient of heat transfer of the boundary layer, ( * ♦ is a correction factor accounting for the inlet or starting area of the thermal boundary layer and in¬ cluding therein the ratio of the conduit or pipe dia¬ meter D and the distance L over which the heat trans¬ fer occurs. Re is the Reynolds number relating the specific mass f , the rate of flow v and the conduit diameter D with the viscosity Α. of the liquid. Pr is the Prandtl number indicating the ratio between impulse transport (friction) and heat transport. This is an assembly of material constants, such as the spe¬ cific heat c, the viscosity η. and the specific conduc¬ tivity Λ of the liquid. This therefore is a (tempera¬ ture dependent) material constant per se. I i-— J is a correction term for the fact that the viscosity of the liquid in the turbulent center portion differs from that directly at the wall where a different tem¬ perature will prevail. The relation (l) indicates that the coefficient of heat transfer α is about proportional to the output or volume flow rate to the power 0.8. To the heat quantity meter there applies yet a second relation, i.e. the generally known relation: in which Q, is the quantity of heat that the meter will have to m indicate f is the specific mass of the liquid c " is the specific heat capacity φ is the output or the volume flow rate Δ Tl. ,u the difference in temperature between supplied and discharged flow dt is the factor time to which the integration is per- formed. When one ignores the integration as yet because this also im¬ plies a simple electronic operation, and combines both the rela tions (l) and (2) the result will be m = f( λ, , η w , c, D, ) 1 ' 2 . 5 Δ T^ (3) in which 0. is the first derivative of the quantity of heat, i.e the heat flow per each unit of time •af.λ iT. J O.wJC J K J ) is a function of the aforesaid meterial con- stants and of the dimensions of the meter. When used iinn pprraaccttiiccee ff wwiillll bbee Dmainly a function of T. and to a lesser degree of Δ Tι.,u α is the really to be expected coefficient of heat transfer. Δ T. is the difference in temperature between the supplie and discharged flow. Consequently relation (3) may also be written as follows This makes it clear that for determining it suffices to de termine T. , α and Δ T. . This may be performed by measuring fo temperatures in the meter box. Fig. 1c diagrammatically shows the supply and the return con¬ duit including the thermal shunt connection. In these parts ther have been drawn the imaginary heat resistances R. to R. inclu¬ sive while it has been indicated diagrammatically at which poin the four temperatures T1.,' Tu,' T,b,' To are measured. Therein: R is the heat resistance of the boundary layer at the hot side, R- is the heat resistance of the tube raw material and -7- the composite body, R, is the heat resistance of the thermal shunt connection, and R, is the heat resistance of the boundary layer and the material resistance at the colder side which within the scope of the present application does not need fur¬ ther consideration as only a measurement is performed on the supplied flow and not on the discharged flow. The first resistance 1 , the boundary layer resistance, is formed by the coefficient of heat transfer α which has to be de¬ termined and the surface area F across which the thermal shunt connection abstracts heat from the flow in the conduit. This surface area is substantially fixed by the dimensioning of the ■ meter. The edges are subject to some displacement beyond the original area when the heat transfer by the pipe walls outside the composite body also will play a role upon decreasing flow of liquid. This increase of surface area will be indicated below as the border (line) effect. The second indicated resistance R ? is formed by the intermedia- te material because a direct measurement of the wall temperature is difficult. The third resistance R-, is that of the shunt con¬ nection with _ T, , which resistance determines the heat trans- b,o' port by the first two resistances. The co'efficient of heat transfer may be determined by measu-- ring Δ T. , and the heat transport in accordance with α = FR; (5) and which may be combined as follows _1 l\ T \ a ____ ( PR x —i* _ m \ (7) b,o By combining the relation (7) with the relation (4) the follo¬ wing is obtained «m = f 1 ' *- - ' *x,u> * f 2 ' ^y b , o i ) - "i . '- ' (8 ) -Based on this theory it appears to be possible indeed to dete mine the heat consumption by measuring four temperatures. From these temperatures the differential values Λ T . , _lT. , " ι,u' ι,b and Δ T, as well as the quotient of the latter two may be cal culated. Subsequently these arguments are translated with the a of tables and the two above mentioned function values, whereupo two times multiplying suffices for obtaining the momentaneous heat consumption Q . m It has been tried to determine the function curves empiricall In order to elucidate this test, elation (2) should again be compared with relation (δ). It then appears that it will be ne¬ cessary to investigate the relation between on the one hand <ξ> c and on the other hand ^, T . and T D , O Fig. 1d shows the relation between the measured volume flow rate and the measured temperatures when performing this type of tests. Along the ordinate the normalized value of the product c φ has been plotted and along the absciss the quotient of t measured temperature differentials Δ T. , and ήT, , while the ι,b b,o' temperature T. occurs as parameter. These measurements have bee performed at a fixed value of Δ T. . Based on a number of test ι,u in which first of all special attention was paid to the repro- ducability it could be concluded that it is possible to record the course of the function of ' c φ ' and Δ T.,,b m. one t,a,b.le b,o and that for compensating the influences of T. and Δ T. simple corrections of arithmetical nature could be introd---ueed in the table values. By correctly shaping the shunt connection as regards length and cross section in connection with the choice of the types of material of the connection and the tube together with the asso¬ ciated coefficients of heat conductivity it„appeared to be pos- sible to keep the course of the quotient of the volume flow rate within the measuring range of 1 to 40, between the limits of 1/8 to 8 such leading to acceptable mea¬ surable temperature differentials Δ T. , or _T. yet at a given 1, D D,o minimum temperature differential between supplied and drained flow of Δ T. ■ of 10°C. The calculation of the differences, quotients, products and the handling of the * table including the introduction of arith¬ metical corrections of the results is performed in this instance by a micro computer in IC-format. With reference to Fig. 2 there has been shown a possible embo¬ diment of the heat quantity meter according to the invention. In this figure the reference numerals 1 and 2 indicate the supply and drain conduits, respectively, the reference numeral 10 the housing of the meter, the reference numeral 8 the electronic processing unit, the reference numeral 9 the electric power unit and the reference numeral 11 the reading panel. An electronic signal processing unit capable of computing the total heat flow from four absolute temperatures on the basis of relation (8) has been realized by means of micro electronics as already used in pocket computers. In view of the micro electro¬ nics already present this meter will possess additional posssi- bilities such as telemetric reading, control of system functio¬ ning, day/night/season tariff, etc. Also within the scope of the invention the meter may be applied solely for the determination of volume flow rates of liquids. Some important aspects with regard to the measurement princi¬ ple of the present heat quantity meter are among others: a. The dimensions of the heat transferring surface area within the conduits and the dimensions or nature of the thermal shunt connection. b. No requirement of a shunt connection " for " creating a partial or sub heat flow. Even a (measurable) heat exchange with the surroundings offers the possibility to determine the proper¬ ties of the boundary layer and consequently the volume flow rate via temperatures. c. The influence of foreign components in the water circulation that might deposit on the wall and might consequently influ- OMPI WIPO ^&£ l ence the heat resistance of the boundary layer. d. The flow profile of the flows of liquid and the contacting o the heat transferring surfaces. e. The choice of the temperature measurement points in or on th thermal shunt connection and the choice of the shape by mean of which the shunt connection is coupled to one or both of the conduits. Ad a. The surface in which the thermal connection is joined to the conduit, is limited. The heat transport by this connection is continued not only at the location of this junction but also in the surrounding conduit walls. The influence of this border ef¬ fect is dependent on the wall thickness of the conduit, the co¬ efficient of heat conductivity of the materials used and the co efficient of heat transfer of the flowing liquid to the conduit wall and consequently on the volume flow rate. The border line effect is conducive to a deterioration of the non-linear relation between the temperatures to be measured and the heat flux to be determined. The influence of this border ef¬ fect may be restricted by thinning the conduit wall at the lo- cation of the edges with the thermal connection or by providing a piece of insulating material (5 in Fig. 4). With reference to Figs. 3 and b there have been shown two examples of a conduit section including a shunt connection fas¬ tened thereto by means of a point junction and a conduit sectio including a shunt connection 3 fastened thereto by means of an annular junction. In both the embodiments the border effects will act differently. For that matter the ratio of edge length to transfer area is larger for the point junction than for the annular junction. Moreover the point junction possesses edges i the longitudinal direction of the flow whereas the annular junc tion possesses only edges in the transverse direction. With reference to Fig. 3c there has been shown a further vari ant of the annular junction in which the block shaped shunt con nection is brought in contact with the flows over a greater length than width. The participation of the edges is thereby re latively small. The junction pieces 14 and 14 consist of a good heat conductive material, such as coppper, whereas the fixed re¬ sistance part 3 between the junction pieces 14 is made however of a bad heat conductive material, such as stainless steel, so that within a small volume efficient heat resistance is provided. The well conductive junction pieces 14 and 14 lessen the critical character of mounting the temperature sensors for measurement of T and T, . o b With reference to Fig. _>ά there has been shown a side eleva¬ tion of a coupling body 6 arranged coaxially within a conduit section 1 , 2 at the end of the thermal connection 3- The coaxial arrangement has the advantage that the flow rate in the center of the conduit contributes most to the output. Moreover the flow contacting form of the coupling body may be chosen in such a manner that there will be a simple relation between the heat transport through the conduit and the temperature differential measured across the thermal connection. It has therein clearly been indicated that a thermal insulationring 5 may be provided between the thermal connection 3 and the wall of the conduit 1 , 2 in order to suppress an optional heat transfer from or to the wall of the conduit. Ad b. In those systems in which the supply and the drain do not near each other close enough and the heat transport for the sub flow by mean's of Peltier effects is impossible or is hampered by practical considerations, it it possible to make the desired heat transport occur from the supply conduit to the surroundings by means of a cooling body. In that case the drain conduct is not necessary anymore for determining the volume flow rate of the liquid and/or the heat output. However, the sub heat flow to the surroundings will have to be measured because this flow keeps -playing a roll in the electronic signal processing. The same may be performed with the drain conduit, however, in that case the temperature differential with respect to the surroundings will be much smaller and the direction of the sub heat flow will also run from the inside to the outside. Ad c. To the circulating water of the city heating network substan¬ ces are added for preventing corrosion while in future presum ably yet other substances may be added in order to operate at lower stowing force of the pumps (drag reduction). It may be possible that some substances will influence the heat transfe properties of the liquid boundery layer to the walls. No indi- cations of this sort have, however, been found up till now by tests including oxide particles, salt solutions and suspension This means that the fear for such effects has been removed for a good deal. Ad d. The relation between the water output or volume flow rate of the water and the variable heat resistance is determined by physical effects in the boundery layer. In a turbulent flow of liquid as is the case in the present heat meter one may presum that substantially the main part of the flow rate gradient and the entire temperature gradient is to be found in this laminar boundary layer. This boundary layer has a thickness in the mag nitude of some tenths of micrometers. The profile of the flow determines the relation between the output and the flow rate gradient at the location of the boun- dary layer. ' The profile of the flow should therefore be contro ledin order to maintain the relation between temperatures and heat flux.Bends, valves, couplings, etc have there own influen on the profile of the flow so that the length of the conduit o the heat meter is bound to a minimum, presently ten times its own diameter. The interfering influences of the above mentione accessories may be suppressed by correctly shaping the inlet opening so that a shorter length of the conduit of the heat me ter may suffice. Ad e. In a connection constructed like represented in Fig. 4 the field of. isotherms by means of which the heat flow via the boundary layer manifests itself in the material of the conduit wall and of the shunt connection, is not radial symmetric. Suc of course is impossible because the heat has to flow finally i one direction, for instance towards the other conduit. The hea flow occurring in the head side of the connection (at 4 in Fig 4) will have to flow via the sides to the central middle por- tion. Consequently there will occur an additional fall of tempe- ratur in the sides. This additional fall of temperature appears to be dependent on the flow as will be clear because upon increa¬ sing volume flow rate of the liquid the boundary layer resis- tance becomes smaller so that the material resistances will beco¬ me of greater influence on the heat flow lines in the sides. As a result thereof there will occur a different temperature dis¬ tribution. Emprirically it has been found possible to give the junction according to Fig. 4 such dimensions that the change in the T 1. ,,D signal, by measuring at the head side (point 4) » causes such a chang°e in the q^uotient Δ Tι.,,b/' T,b,o that the relation between this quotient and the volume flow rate or output of liquid may be straigthened within acceptable limits over the entire measu- ring range from 1 to 40. The term "acceptable" should thereby be understood as Λ% within the final answer.

Claims: C L A I M S 1. A method for measuring the quantity of heat abstracted fro a circulating flow of liquid by a consumption unit based upon t indirect measurement of the volume flow rate of the liquid, whil maintaining a sub heat flow from or to the main heat flow tran- sported by the flow of liquid and measuring the temperature at some points by means of temperature sensors, c h a r a c t e r ¬ i z e d i n that the volume flow rate of the flow of liquid is determined on the basis of the flow rate dependent heat transfer in the boundary layer of the flow of liquid at the location, where the sub heat flow leaves or enters, by determining the tem perature differential across the boundary layer, and the sub hea " flow passing through said boundary layer, while measuring at least one absolute temperature of the flow of liquid for correc¬ ting the temperature dependency of the material constants of the liquid involved in said determination of the volume flow rate. 2. The method of claim 1, c h a r a c t e r i z e d i n that the sub heat -flow passing through the boundary layer is deter¬ mined by measuring the temperature differential across a fixed heat resistance in a part of the path of the sub heat flow out- side said boundary layer. 3. The method of claims 1 or 2, " c h a r a c t e r i z e d i n that the quotient of the temperature differential across the fixed heat resistance and the temperature differential acros the boundary layer is determined by means of an electronic compu tation circuit as a measure for the flow rate dependent heat transfer in the boundary layer. 4. The method of claim 3 ? c h a r a c t e r i z e d i n that the quotient thus determined is used in the electronic computa¬ tion circuit for determining the volume flow rate while employin a relation also determined by the shape of a heat quantity meter to be used and the material constants of the liquid. 5- The method of claim 4 wherein the flow of liquid is supplie to and drained from the consumption unit via a supply conduit an drain conduit respectively, c h a r a c t e r i z e d i n that for obtaining the momentaneous heat consumption the said volume flow rate is multiplied in the electronic computation circuit with the difference in temperature of the flow of liquid in the supply conduit and in the drain conduit, respectively. 6. The method of anyone of the preceding claims solely applied for determining volume flow rates of liquids. 7. A heat quantity meter for performing the method of anyone of the preceding claims c<τ.mprising a conduit section for the flow of liquid to be supplied, a conduit section for the flow of liquid to be drained, a shunt connection between both said conduit sec- tions for the sub heat flow, and a number of temperature sensors, one of which on the supply conduit section and a second one on the drain conduit section, c h a r a c t e r i z e d i n that furthermore two temperature sensors are provided on the shunt connection on both sides of the heat resistance thereof and that the shunt connection is arranged to have such a length, cross section and junction surface area at least at the supply conduit section and the material of the shunt connection and of at least the supply conduit section at the location of the junction with the shunt connection possesses such a coefficient of heat con- ductivity, that the quotient of the temperature differential across the fixed heat resistance of the shunt " connection and the temperature differential across the boundary layer of the flow of liquid at the location of the junction with the shunt connec- tioh lies between 8 and 1/8 for the entire operative measurement range of volume flow rates of the liquid thus warranting reason¬ ably measurable temperature differentials. 8. The heat quantity meter of claim 7 ? c h a r a c t e r ¬ i z e d i n that at least the supply conduit section is coup¬ led to the shunt connection by means of an annular junction, the shape of the end, turned away from the middle portion of the shunt connection comprising the fixed heat resistance, being such that mainly in case of higher volume flow rates of the li¬ quid the transferred sub heat flow leads to an additional tem¬ perature difference in this end, while one of the two tempera- ture sensors destined for measuring the temperature differential across the heat resistance is provided on this end, so that this additional temperature difference will contribute in compensa- ting a possible non-linear relation between the quotient and th volume flow rate of the liquid. 9« The heat quantity meter of claim 7 or 8, c h a r a c ¬ t e r i z e d i n that the conduction of heat through the wal at least of the supply conduit section outside the annular junc tion with the shunt connection is restricted by the selection o the material of the supply conduit section outside the annular junction sothat the sub heat flow in the shunt connection is governed by the heat transfer of the boundary layer at the loca tion of the annular junction. 10. The heat quantity meter of anyone of claims 7- » c h a ¬ r a c t e r i z e d b y an electronic computation circuit ϊoτ termining the temperature dif erentials, for determining the said quotient, for deriving the volume flow rate of the liquid from the quotient in accordance with a predetermined relation, for correcting the temperature dependency of the material con¬ stants, and for multiplying the volume flow rate thus obtained with the temperature differential between the flow of liquid in the supply conduit and in the drain conduit. 11. The heat quantity meter of claim 10, c h a r a c t e r ¬ i z e d i that the electronic cpmputation circuit includes an integrating circuit for determining the quantity of heat transferred per each time unit to the consumption unit. 12. Thg heat quantity meter of anyone of claims 7-11 > c h a - r a c t e r i z e d i n that the electronic computation cir¬ cuit is provided with further circuits for tele etric reading, control of the functioning of the meter, for recording casu quo indicating day/night/season tariff, etc.

Inventors: BEUSE R, JANSEN J, VAN ITERSON H, WICHERN P
Applicants: BEUSE R, ITERSON H VAN, JANSEN J, KEMA NV, WICHERN P, TOT KEURING VAN ELEKTROTECHN MATERIALEN NV, VAN ITERSON H
Application year: 1980
Main classification: G01K17
IPC codes: G01F1, G01K17