# Method for optimised functioning as to power of motor-driven pump with positive feedback

FIELD: engines and pumps.

SUBSTANCE: invention relates to a method for optimised functioning as to power of a motor-driven pump in a hydraulic system with at least one self-adjustable consumer. Predetermined head (H_{soll}) of the pump is controlled depending on its volumetric flow rate (Q) according to the controlled basic characteristic curve, which is determined by means of pre-determined specified value (H_{K}) of the characteristic curve. Volumetric flow rate (Q) pumped with the pump is determined, and its trend (δQ) is determined, and depending on volumetric flow rate (Q) and/or its trend (δQ) the specified value of characteristic curve (H_{K}) is increased when volumetric flow rate (Q) is increased, or decreased when volumetric flow rate (Q) is decreased.

EFFECT: invention is aimed at optimum matching of hydraulic power of the pump with its corresponding working point in a hydraulic system.

21 cl, 13 dwg

The invention relates to a method for optimized power operation of the pump driven by an electric motor, a hydraulic system with at least one self-regulating consumers, with specified pump head is adjusted depending on its volume in accordance with the adjustable base of the characteristic curve, which is defined by a predefined setpoint characteristic curve. In addition, the invention relates to a pump driven by electric motor, c management and control electronics, which is capable of implementing the method corresponding to the invention. The invention also relates to a computer program product with instructions for execution of the relevant invention of the method when it is executed on the management and control electronics of the pump.

In the regulation of circulating pumps for heating installations in the prior art regulation according to a predetermined characteristic curve, for example, so-called Δ-v characteristic. Such Δ-v characteristic describes the linear relationship between the pumped volume flow Q and produced by them differential pressure Δ or his head N. Pump regulation according to this characteristic cu�howl adjusts the hydraulic power of the pump depending on volume pressure. The disadvantage with this solution is that the characteristic curve is preset, that is, may change only slightly. Really know the performance of pumps with manual setting of the characteristic curve at which the position and/or the steepness of the characteristic curve in the family of characteristic curves, in the General case, can be selected discretely or may change. However, beyond that, the correction capacity of the pump is not made.

In General, and for calculating optimal and random shape of the characteristic curve provided by the pump of the hydraulic power for the regulation along similar hard not characteristic curve in each operating point corresponds to the needs of the installation, as the desired pressure depends not only on volume flow, but also from that of the hydraulic consumers in the network that require this volumetric flow rate. For this reason, the calculation of the pump should always either be inflated because it is selected by the weakest link in terms of "worst case", or should be understated so that it can lead to the insufficient provision of individual consumers in the hydraulic system.

Therefore, the object of the present invention is to provide a method which ensures Opti�social harmonization hydraulic power pump with its corresponding working point in the hydraulic system.

This problem is solved by a method with signs of paragraph 1 of the claims. Preferred embodiments of the invention are presented in dependent claims.

In accordance with the invention, a method for optimized power operation of the pump driven by an electric motor, a hydraulic system with at least one self-regulatory consumer, wherein the predetermined pressure of the pump is regulated depending on its volume flow adjustable along the base of the characteristic curve, which is defined by a predefined setpoint characteristic curve, and is defined pumped by pump volume flow and is defined by its trend, and depending on volume flow and/or trend of the setpoint characteristic curve is increased, when the volumetric flow rate increases or decreases, the volumetric flow rate decreases.

The idea underlying the invention is that by means of the hydraulic system to maintain a predefined change of the volume flow, in addition to the common control Δ-v characteristic by adjustment of the characteristic curve and, thereby, the capacity of the pump. If the volume flow in the hydraulic system decreases, this change�tion is supported not only by reducing the pump power based on the control characteristic curve, but additionally by reducing the setpoint characteristic curve. If the volume flow is increased, is increasing the pump power. From the point of view of technique, the regulation of this fundamental method of action is referred to as positive feedback.

The change in volume flow in the hydraulic system caused by self-regulating consumers. Self-regulatory consumer in the sense of the proposed invention is such a consumer, own volume flow of which is regulated by means of the actuating mechanism, for example, temperature-controlled valve on the consumer. If the hydraulic system includes a plurality of such self-regulating consumers, they all have an impact on the required total volume flow needs to pump pump. If this volumetric flow rate is not achieved, then there is insufficient supply of at least one consumer, and on the contrary, exceeding the required volume flow, excessive supply, whereby unnecessary power consumption for the pump, as the pump works against a partially closed valve.

By an appropriate invention of the method named cases the functioning of those excluded, Thu� hydraulic pump power changes gradually. Is the deviation from classical regulation along hard characteristic curve. Moreover, the setpoint characteristic curve that defines the characteristic curve changes gradually to approximate the hydraulic pump output to the actual working point.

Specified value of N_{K}the characteristic curve is a value that indicates the position of the characteristic curve in the family of characteristic curves (parametric surface) of the pump, i.e. on the so-called H/Q-diagram for a known or previously established by the slope (steepness). In case Δ-constant characteristics with a slope of zero, that is, such characteristics, along which the pressure of the H_{Soll}the pump should be maintained constant by the volumetric flow rate Q, the value specified for N_{K}the characteristic curve indicates that supported constant pressure H_{Soll}pump. If, alternatively, applied Δ-variable characteristic, that is such a characteristic that describes the linear dependence of the pressure of the H_{Soll}the pump volumetric flow rate Q, this characteristic may be determined, for example, through the point of intersection of the curve with its maximum speed, which then corresponds to a given value of N_{K}characteristice�coy curve.
The slope of the curve may, for example, be determined by the fact that at a volumetric flow rate equal to zero, there is a pressure, which corresponds to half the specified value of the characteristic curve.

Increase or decrease the setpoint characteristic curve may be the fact that c is a predefined set value H_{K,alt}the characteristic curve is summed value M of positive feedback, where a value of M of positive feedback is positive when the volume flow Q increases, and is negative when the volumetric flow rate Q falls. This means that the specified value of N_{K}characteristic curve with a positive trend δQ increases, negative trend δQ decreases. The trend of the volumetric flow δQ is supported, therefore, by means of the relevant invention of the method that regulates the action of a simple regulation of the characteristic curve, in particular Δ-v characteristic is enhanced. A predefined set value H_{K,alt}the characteristic curve can be set manually reference a given value of H_{K,ref}that is crucial when commissioning the pump, or it may be the last specific regulation given value of H_{K}. This means that predefined�th previously set value H_{
K,alt}the characteristic curve of a regulator is the latest predefined set value H_{K}the characteristic curve.

The proposed invention is thus with this type of positive feedback is the usual extension of regulation Δ-v characteristic. In contrast, the regulation corresponding to the invention, the adjustment of the pump power leads to the regulation on the hard characteristic curve, and to the mode of operation that coincide with the needs. The actual operating point of the pump is not installed on the front of this manual or in the factory of the reference characteristic curve and moves along it. It moves rather along any path relative to this set reference characteristic curve. It should be noted that in the framework of the invention are not necessarily in the basis should be based on a regulation by Δ-v characteristic. In contrast, the characteristic curve can have any shape, in particular, also can be permanent.

Volumetric flow rate Q can in particular be measured by means of a volumetric flow sensor. The preferred manner it can be determined from the internal electrical parameters of the pump or its motor. The definition of the volume flow can be carried out continuously�but or discretely in time.
Consequently, the definition of a trend δQ volume flow can be carried out continuously or discretely in time. In the sense of the proposed invention under the trend δQ refers to a temporary change in volumetric flow rate Q. It can particularly easily be calculated from the derivative dQ/dt of temporal characteristics of the volumetric flow Q(t), if the volumetric flow rate Q(t) is continuously recorded. In discrete time the measurement of the volume flow Q(t_{v}) instead of the derivative to apply the differential ratio ΔQ/ΔT to determine the temporal variation of the volume flow rate Q. since the derivative or differential of the ratio of measured values volume flow lead to too loud noises, is especially preferred as a measure of the change in volumetric flow rate to apply a current difference of the volumetric flow Q and its arithmetic mean (

Further, it is preferable that a certain volumetric flow rate Q �to mnouth to zero
if it is relatively smaller than the specified minimum value of Q_{min}. Similarly, preferably, a certain trend δQ multiply by zero, if it is relatively smaller than the specified minimum value δQ_{min}. This causes suppression of small values of the volume flow rate or volumetric flow changes. This method can filter out small fluctuations in the volume flow or fluctuations in the trend relative to the zero point. Filtering can be performed by multiplying the volumetric flow rate or trend window function whose values are in the interval between the respective minimum value of Q_{min}or δQ_{min}and his pair complement of Q_{min}and-δQ_{min}equal to zero, and off the unit. This can be implemented through pre-filtering of the measured volume flow or a certain trend. As the minimum value of Q_{min}for volumetric flow rate Q can be used, for example, a value between 0.005 and 0.02 m^{3}/hour, preferably about 0.01 m^{3}/h. In addition, as the minimum value of δQ_{min}for trend δQ can be used, for example, a value between 5 and 10 m^{3}/hour for 10 minutes.

The determination value M is a positive feedback can be implemented in different ways. It can be calculated, for example, regardless of obyemno� flow Q(t) and/or its trend δQ function f(Q), f(δQ) or f(Q, δQ). Preferably, the calculation is based on the regardless of the trend function f δQ(δQ) or on the basis dependent on the volumetric flow Q and the trend function f δQ(Q, δQ).

A particularly simple form of positive feedback is proportional to the trend δQ positive feedback according to the function M(δQ)=k·δQ, and k is a positive constant, with which the change in volumetric flow rate δQ is scaled and relatively consistent physical units. Alternatively, the value M of positive feedback may be determined based on a function M(δQ)=k·(δQ)^{3}. This function defines a cubic functional relationship between the trend and δQ positive feedback M. In another alternative form of execution, the value M of positive feedback may be determined based on a function M(δQ)=k·arctan(δQ). Also in both of the latter embodiments, k is a positive constant, the change in volumetric flow rate δQ is scaled and relatively consistent physical units. The arc tangent function has the advantage consisting in the fact that it is for positive and negative trends δQ asymptotically approaches a through certain limiting value k, which is achieved by limiting the magnitude of the value of positive feedback, catroulette stability regulation.

Called functions have the property consists in the fact that they are symmetric, in particular, possess the symmetry of the points relative to the zero point, so that positive and negative trend δQ with the same values respectively associated with the same absolute value M of positive feedback.

According to another alternative formula for the value of positive feedback, it can be calculated from an asymmetric function. Asymmetric function has the advantage consisting in the fact that for positive and negative trend δQ with the same quantities associated respectively commensurate with different values of M positive feedback. In this way, for positive and negative changes of the volume flow can be determined by different magnitude of positive feedback. Thus preferably the value of positive feedback is selected proportionately large for positive trends δQ than for negative trends δQ to quickly respond to the increase in volumetric flow rate, i.e., increased need for volumetric flow rate.

A preferred way, the calculation is performed from the asymmetric function, which describes the superposition of two shifted relative to each other, in different ways weighted �of uncci of arctangent. This may be done, for example, according to the following function positive feedback:

where M is the value of positive feedback, δQ is the trend, and_{1}and_{2}b_{1}and b_{2}respectively positive scaling factors, s_{1}with_{2}, d_{1}and d_{2}respectively the positive coefficients of the displacement and E - shift for the correction of the zero point, and and and_{1}not equal to a_{2}. Shift E corresponds to the value of the sum of the above-mentioned functions of the arc tangent for the trend δQ is zero. Natural point of symmetry of the functions of the arc tangent of zero point shifted relative to each other to offset coefficients C_{1}with_{2}.

In a particularly preferred embodiment, the implementation of the relevant invention of the method of the scaling factor a_{1}shifted to the right of the arctangent function is selected larger than the scaling factor and_{2}shifted to the left of the arctangent function. This means that most positive feedback M applies to positive trends δQ, and the least positive feedback M applies to negative trends δQ. Thereby provides a faster response regulation of the pump to increase the volume flow compared to the response to reduced volumetric RA�stroke.
This, in turn, prevents insufficient supply of consumers, in particular, at the opening of the Executive mechanisms regulating their flow.

The above example function M(δQ) have effect, consisting in the fact that at a constant volumetric flow rate Q, that is, when the trend δQ equal to 0, the positive feedback M is equal to 0, that is calculated according to these functions M(δQ) positive feedback M at a constant volumetric flow rate Q leads to the maintenance of current a given pressure N_{K}.

In some cases, however, in the hydraulic system may be nonlinear effects, which can have the effect of stopping the flow, for example, in the case of thermal fluctuations or in the case of a closing valve reverse flow in one or more parts of the hydraulic system. Stop currents can also occur when there is a need for a volumetric flow of individual consumers, which can no longer be ensured. To avoid stopping the flow and, thereby, to increase the stability of the relevant invention of the method with respect to such non-linear effects, preferably by a positive feedback M add shift M_{0}if the trend δQ is positive or zero.

When the above-mentioned approximate the functions M(δQ) �good feedback M is calculated solely depending on the change in volumetric flow rate δQ.
However, it appeared that in the General case with a small volumetric flow of Q positive feedback q can be chosen greater than at high space costs. The change in volumetric flow rate δQ when you change a given pressure H_{Soll}it can be calculated directly on the basis of a parabola piping: H=d·Q^{2}since the volume flow is calculated according to Q=√(H/d). Because the resistance of d network of pipelines is in the denominator of this expression, with a steep characteristic curves units with high resistance d pipe network, changing of set pressure H_{Soll}causes a smaller change of the volumetric flow Q, than the more "gentle" characteristic curves units with less resistance d network of pipelines. So is a rational positive feedback M at low volumetric flow rates Q to select more than at high volumetric flow rate Q. Therefore, in accordance with the invention, it is possible to calculate positive feedback M advanced to apply the current volume flow Q according to the function M=f(Q, δQ).

In a simple form of execution of the previously calculated depending on the change in volumetric flow rate δQ positive feedback M is multiplied by dependent on the volumetric flow Q the zoom function, for example, S(Q)=S_{max}/(1+Q/Q_{0}), so that M(Q, δQ)=S(Q)·fδQ).

An additional measure to increase the stability of the relevant invention of the method can be implemented by limiting the value M is a positive feedback in proportion to her height. It is thus possible to avoid too much changes characteristic curves. The preferred way to value M of positive feedback is assigned the maximum value M_max, if it exceeds the upper limit value. Accordingly, the value M of positive feedback can be assigned to the minimum value M_min, if it falls below the lower limit value. Thus, the current calculated value M of positive feedback can be compared with the upper limit M_max, and with a lower limit of M_min and in excess M_max upper limit or falling below the lower limit M_min be installed on M_max upper limit or lower limit M_min.

Alternatively, restricting the values of the positive feedback can be a simple way through the above function in a positive feedback. Due to this eliminated the additional steps of comparing and assigning values. As the arc tangent function for increasing values asymptotically converge to the value π/2, and for falling values - the value of-π/2, then by sootvetstvuyuschaya constants k or scaling factor and_{
1}for a shifted to the right of the arctangent function can be implemented with an upper limit of the range for values of M of positive feedback, and by an appropriate choice of the scaling factor a_{2}for a shifted to the left of the arctangent function to implement the lower limit of the range of values for M a positive feedback. The preferred way for a symmetric function M(δQ) a positive feedback type of the arc tangent of the constant k is chosen as k=M_max·2/π. The preferred way of limitation under asymmetric function M(δQ) a positive feedback type of arctangent is achieved in that the scaling factor a_{1}is selected as the maximum value M_max, and the scaling factor a_{2}as the minimum value M_min.

Alternative or in combination with the limitation value M is a positive feedback resistance of the relevant invention of the method can be improved due to the fact that increase or decrease a given value of N_{K}the characteristic curve is carried out only within the specified operating range. This operating range may be determined, for example, the band around the set reference characteristic curve K, which can be installed for the pump at the factory or manually. It should be noted that in �the idea of the proposed invention "operating range" should be understood not as the working range of the pump,
but rather as a working range corresponding to the invention of the principle of regulation, which can be graphically represented as the operating range of the pump H/Q diagram.

The preferred manner similar operating range is formed so that the set value of N_{K}the characteristic curve is limited to a value within the range between the maximum specified value of H_{K,max}and minimum specified value of H_{K,min}and the reference set value H_{K_ref}to an identified or identifiable reference characteristic curve To the lies inside this range. Since the change of the target value of N_{K}the characteristic curve for a basic regulation on the characteristic curve on the basis of the initially set reference characteristic curve K, causes the shift of the characteristic curve K, then the working range (band) around the reference characteristic curve K, which from above is limited to the characteristic curve, which is defined by a maximum given value of H_{K,max}from the bottom is limited to the characteristic curve, which is defined by a minimum set value H_{K,min}and the pump, respectively, is regulated by the current characteristic curve inside dia�of azone.

Alternative to limit the operating range by means of a band around the set reference characteristic curve K, the working range can be defined so that it is below the set reference characteristic curve K. This has the advantage consisting in the fact that the required for the operation of the pump energy is minimized. As shown by the experiments with commonly used at the present time Δ-v characteristics, in General case there is insufficient supply of the hydraulic system, so you can refuse to work in a range above a pre-set reference characteristic curve C. Therefore, the preferred manner specified value of N_{K}the characteristic curve is limited to a value within the range between the maximum specified value of H_{K,max}and minimum specified value of H_{K,min}and a maximum specified value of H_{K,max}corresponds to reference a given value of H_{K_ref}to an identified or identifiable reference characteristic curve K.

In a simple case, the lower limit of the operating range is formed by a straight line. For example, this straight line may correspond to a straight line, obtained by a parallel shift of the reference characteristic curve at a certain value down. If this limit is, by contrast, is determined by the minimum �adanim a value of H_{
K,min}it can be obtained direct, which not only moved, but also its slope also becomes larger. This, in particular, it would be in the case when the set value of N_{K}characteristic curve that determines a characteristic curve that she is under head of H_{K}cuts the curve maximum speed and at 0.5*N_{K}suppresses the axis of the head. In a preferred further development of the invention, the lower bound of the operating range, however, formed not rigidly set straight or direct, depending on the reference characteristic curve, and is determined dependent on the volumetric flow Q is a function of H_{K,min}=f(Q).

Further, it is preferable to carry out the limit of relatively large volume flow Q. Therefore, in accordance with the invention increase or decrease the specified value of N_{K}the characteristic curve can be carried out only when the volumetric flow rate Q is below a predetermined reference value of the volume flow Q_ref. The preferred way is the reference value of the volume flow Q_ref essentially corresponds to half the maximum volume flow rate Q_max, i.e. the volumetric flow rate, which occurs in the operating point, which lies at the intersection of the pre-set reference product�eroticheski curve curve with maximum speed.
It has the following prerequisites:

The design of the hydraulic system designer calculates the so-called design point, i.e. the estimated volume flow Q_A and corresponding to the rated pressure, see Fig. 4A, 4b on which a calculation point indicated by the reference position 4. Subject to the application of the pump is selected by the designer so that the design point lies within a family of characteristic curves (parametric surface) of the pump. Since not all of the parameters of pump are available, the estimated point lies, as a rule, considerably lower curve 2 maximum number of revolutions of the pump. Manual setting of the setpoint Δ-v characteristics of this pump is controlled so that adjustment of the characteristic curve To pass as possible after a definite point, and, due to the discrete features of the installation adjustment of the characteristic curve, in a typical case, there are small deviations. So for pump operation near the design points can be assumed that based on the designer's calculations, the pressure of the preset adjustment of the characteristic curve corresponds essentially to the needs of the installation. For this reason, it is rational to operate near design points of the pump boat ride along� preset adjustment of the characteristic curve, that is, the reference characteristic curve, and decrease the setpoint characteristic curve below that of the reference characteristic curve to run just below the reference value of the volume flow Q_ref, and the reference value of the volume flow Q_ref preferably slightly below or equal to the volumetric flow rate Q_ in the calculated point in the hydraulic system.

In another preferred development of the relevant invention of the method is a gradual return of the operating point of the pump in the correct range, if this operating point is out of range. Therefore, in accordance with the invention, the specified value of N_{K}characteristic curve gradually, the speed will be reduced if it exceeds the maximum specified value of H_{K,max}, stepwise or gradually increased, when it fell below the minimum specified value of H_{K,min}. The preferred way, in the case of out-of-range, positive feedback can be deactivated or deactivated. "Gradually" in this connection means that is only a minor change given value of N_{K}the characteristic curve. If, for example, the out-of-range based on the operating point at low volumetric flow rates Q and small heads of N, due to the fact that additional �LAPAN open
so that the working point is moved from the operating mode to high volume costs, the specified value of N_{K}the characteristic curve in accordance with the invention not abruptly increases to a high value. On the contrary, this is done by gradual return of the specified value in the working range. Due to this, may be excluded unpleasant noises due to the rapid changes of speed in the hydraulic system.

Then, if the operating point of the pump out of range, can be tracked by comparing with determining the maximum and minimum values. Return speed can be set either by the height of the step (step) and/or the width of the step, that is, the time duration of the step. The preferred way a step change in the set value of N_{K}the characteristic curve is in the range from 1 cm to 3 cm, preferably 2 cm per minute. In the case of discrete time determine the volumetric flow Q step width may correspond to the sampling interval or multiple of the sampling interval value. So step width may be 30 seconds, one minute or to be more. Can be used and any other value step width.

Change the set value of N_{K}the characteristic curve can be carried out in this way for�PSBs for each subsequent time interval, or for each subsequent time step,
until the current operating point of the pump is still out of range. This means that the specified value of N_{K}the characteristic curve of the pump running slightly adjusted if the operating point at the next time step continues to be out of range. Therefore, in accordance with the invention, a step change in the set value of N_{K}the characteristic curve is repeated so long until it again will not be inside the range between the maximum specified value of H_{K,max}and minimum specified value of H_{K,min}. The advantage of this method of action is to continue the harmonization of the working point of the pump without causing undesirable abrupt changes of the system state that may lead to preregulatory and noise currents.

The proposed method is particularly preferably applied for controlling the circulation pump, in particular a circulating pump of the heating system, in a closed hydraulic system. In this case, the hydraulic system may be a heating system with at least one heating element which is supplied by the circulating pump of the heating system. Alternatively, the hydraulic system may be a cooling system, to�ora supplies cooling units as consumers coolant, which is pumped by a coolant pump.

The preferred image of the proposed method is implemented in the management and control electronics of the pump, in particular such of the circulation pump, so that it can be implemented in that the control and regulating electronics.

According to this application, corresponding to the invention method is formed by software instructions that form a computer software product, which accordingly is intended to complete method and can be performed on the control and regulating electronics of the pump to actuate the pump. Therefore, the invention also relates to a computer program product with instructions for performing the method of operation of a pump driven by an electric motor when it is running on the management and control electronics of the pump.

Other advantages, features and characteristics of the relevant invention of the method are explained below with reference to the accompanying drawings, which show the following:

Fig. 1A is a schematic representation of the method of regulation according to the first embodiment,

Fig. 1b is a schematic representation of the method of regulation according to the second embodiment,

Fig. 1C is a schematic representation of the method of regulation according� third embodiment with a return in the range

Fig. 1d is a schematic representation of the block return in the range

Fig. 2A is a schematic representation of the pre-processing of the measuring signal of the volume flow according to the first variant,

Fig. 2b is a schematic representation of the pre-processing of the measuring signal of the volume flow according to the second embodiment,

Fig. 3A - determining the significance of a positive feedback according to the linear trend of the volumetric flow,

Fig. 3b - determining the significance of a positive feedback according to the linear trend of the volumetric flow to account for the shift,

Fig. 3C - definition of positive feedback based on asymmetric functions,

Fig. 3d representation of the scaling function S(Q),

Fig. 4A - H/Q-diagram working range in the form of a strip and the trajectory of the operating point,

Fig. 4b - H/Q-chart with a limited working range,

Fig. 4C - H/Q-diagram working range in the form of clouds.

Fig.1 shows the scheme of regulation, which is implemented corresponding to the invention method for optimized power operation of the circulating pump driven by electric motor, in the heating system. The circulation pump is a component of the pump unit 11, which includes the pump and leading �th motor.

Injection pump unit 11 volume flow Q is measured and fed to regulation 9 on the characteristic curve. According to the preset adjustment of the characteristic curve, which according to the example of Fig. 1A is Δ-v characteristic, with a volume flow of Q is mapped and given a specified value of H_{Soll}pressure for the pump. This set value H_{Soll}pressure is subsequent control action of the control loop and is fed to the controller 10. Simultaneously measured pressure and with a negative sign is supplied by feedback to the input of the regulator so that the regulator input is applied an adjustable deviation in the form of a difference from the given value of H_{Soll}the pressure and the current pressure N.

The controller 10 is designed as a PID (proportional-integral-differential) controller. He gives as managing exposure voltage, which is proportional to a given set number of revolutions n. This control action n set the pump unit 11 or causing the pump to the motor. Depending on the number of revolutions n of the pump unit 11, it is set differential pressure Δ or his head N. In addition, the number of revolutions of the pump unit 11 is also set volume flow Q, but the amount�th flow Q depends on the hydraulic resistance of the heating system; that is, the degree of opening of the regulating valves of the consumer. This regulation described by the characteristic curve corresponds to the level of technology.

In accordance with the invention is a control characteristic curve is extended by the fact that pre-installed characteristic curve in regulation 9 of the characteristic curve when the pump unit 11 is continuously adjusted according to its position on the H/Q diagram. For this, based on the measured volumetric flow Q, is defined by its trend, and, depending on the trend δQ, the value specified for N_{K}the characteristic curve increases if the volume flow Q increases, or decreases, if the volumetric flow rate Q falls. In the factory or manually on the pump is set to the reference characteristic curve with reference To a given value of H_{K_ref}the characteristic curve along which the first adjustment when commissioning the pump unit 11.

The trend δQ is determined in the preprocessing 6. Then, in the computing unit 7 is determined by the value M of positive feedback, which subsequently cascade 8 positive feedback is summed with the current set value of N_{To alt}the characteristic curve. This amount forms a new target value�of N_{
K}the characteristic curve for the subsequent regulation 9 on the characteristic curve. The value M of positive feedback is positive for positive trend and δQ is negative for a negative trend δQ. Originally installed adjusting characteristic at the expense of it is shifted by H/Q-chart up or down and forms a new, temporarily valid adjustment of the characteristic curve along which the pump unit 11 is controlled by regulation 9 of the characteristic curve. This is carried out until, until you set a new preset value N_{K}the characteristic curve.

Fig. 1b shows an alternative form of the scheme of regulation, which differs from the first embodiment according to Fig. 1A unit 7' computing and control 9' on the characteristic curve. Input parameter to calculate the value of M is positive feedback for the block 7' computing is not only a trend δQ, but also the current volume flow Q. In block 7' calculations first calculated depending on the trend value δQ M=f(δQ) positive feedback is multiplied by dependent on the volumetric flow of the scaling function S(Q)=S_{max}/(1+Q/Q_{0}). Fig. 3d shows a corresponding view of the scaling function for S_{max}=2 and Q_{0}=1 m^{
3}per hour.

In addition, in Fig. 1b in regulation 9' on the characteristic curve is set Δ-with characteristic that throughout the range of the volumetric flow Q maintains a constant pressure of H_{Soll}the pump unit 11. In this case, for a predefined regulation 9' on the characteristic curve given value of N_{K}the characteristic curve corresponds to a given value of H_{Soll}pressure, as specified value of N_{K}the characteristic curve without changing is forwarded to the output regulation 9' on the characteristic curve. The output of the cascade 8 positive feedback could therefore, in this implementation of connecting directly to the input of the regulator 10. It should be noted that shown in Fig. 1b both changes don't necessarily have to be present simultaneously in one embodiment. So one variant of execution may differ from that shown in Fig. 1A in that it positive feedback is computed only from the trend δQ, and the following is the basic regulation on Δ-v characteristic according to Fig. 1A. Alternatively, in another embodiment, the positive feedback can only be determined on the basis of the trend δQ, is the basic regulation on Δ-with the characteristic, as in Fig. 1b.

Fig. 1C shows�AET another embodiment of the control circuit, which is different from the first and second option of Fig. 1A and 1b, cascade 8 positive feedback and regulation 9' on the characteristic curve has unit 14 return to the range. It checks whether the current operating point of the pump within its operating range 3 (see Fig. 4A-C).

Fig. 1d shows the function block 14 of return in the range of:

If (Q, H) is above the operating range 3,

the H_{k}=H_{K,alt}-dH;

If (Q, H) is below the working range 3,

the H_{k}=H_{K,alt}+dH;

If (Q, H) is within the operating range 3,

then there is no configuration H_{k}.

If the current operating point Q, H is above operating range 3, it is a gradual, step-by-step reduction of a given value of N_{K}the characteristic curve with the width of the step according to dH H_{k}=H_{K,alt}-dH. If the current operating point Q, H is below the operating range 3, it is a gradual, step-by-step increase given value of N_{K}the characteristic curve with the width of the step according to dH H_{k}=H_{K,alt}+dH. If the current operating point Q, H is within the operating range 3, then there is no adjustment N_{K}.

Fig. 2A and 2b show the implementation of pre-processing 6 according to Fig. 1A, 1b and 1C. In the first embodiment.�ment according to Fig.
2A pre-processing includes filtering 13 the measured volumetric flow Q, the formation of the 12 moving average and calculating the change in volume flow, i.e. the trend δQ. Filter 13 is performed by multiplying the measured volumetric flow rate Q by a window function f(Q), which for values below the specified minimum value of Q_{g}volume flow is zero, and for values larger or equal to this minimum value of Q_{g}volumetric flow equal to one. The minimum value of Q_{g}volumetric flow rate is between 10 and 80 liters/HR. Through this multiplication of small values of the volume flow are suppressed.

Part of pre-processing 6 is, furthermore, the formation of the 12 moving average, which calculates the arithmetic mean (

Fig. 2b shows an alternative embodiment of pre-processing 6. Under this option, there is no suppression of small volume flow Q and the suppression of small changes δQ' volume flow through the filter 13'. In the previous step 12 again first calculates the arithmetic mean value (_{g}'are set to zero, that is not considered further. The filtered trend δQ is an output parameter pre-treatment 6 according to Fig. 2b.

Fig. 3A shows the function M(δQ) positive feedback in the form of direct�Oh, which describes the linear relationship between the value M of positive feedback and trend δQ. According to this linear relationship, for each trend δQ can be determined corresponding to the value M of positive feedback. This function M(δQ) positive feedback can be implemented in block 7, 7' calculations of Fig. 1A and 1b.

An alternative definition of the value M is a positive feedback shown in Fig. 3b. Here positive feedback M additionally has, in comparison with a variant of execution according to Fig. 3A, the shift of M_{0}for zero volume flow trend and positive trends δQ volumetric flow rate.

Another alternative feature positive feedback, which can be implemented in block 7, 7' calculations shown in Fig. 3C. According to this embodiment, the value M of positive feedback is determined on the basis of asymmetric function in a positive feedback. Feature positive feedback according to Fig. 3C has the following mathematical expression:

parameters: | ||

Maximum positive positive feedback | M_max | 0.02 m |

Maximum negative positive feedback | M_min | 0.01 m |

Trend | δQ | is calculated in m^{3}/hpreview processing 6 |

The scaling factor | b_{1}=b_{2}= | 0.01 m^{3}/h |

The zero value of the range | with_{1}=C_{2}= | 0.05 m^{3}/h |

The shear factor | d_{1}=d_{2}= | 0.5 m |

Correction of the zero point | E | 0,000628 m |

Asymmetric function M(δQ) positive feedback in accordance with this overlay consists of two arctangent functions, which are shifted relative to each other at the same value of C_{1}=C_{2}shift. Both functions of the arctangent in accordance with this, in relation to their natural point of symmetry at the zero point of the coordinate system are shifted to the right (by subtracting from_{2}). Between these coefficients shift function M(δQ) positive feedback is approximately equal to zero.

As usual, the arc tangent function has a range of values between +π/2 and-π/2, this range of values is changed by multiplying by 1/π for a range of values from -0.5 to +0.5. In addition to the shifted to the right arctangent function adds the value of d_{1}=0,5, so that the codomain is in the range from 0 to 1. Similarly, from a shifted to the left of the arctangent function is subtracted the value of d_{2}=0,5, so that its value ranges from -1 to 0.

By multiplying the individual functions of the arc tangent to the scaling factor M_max, M_min can set pre-defined limits for values of M of positive feedback, which, respectively, asymptotically approaching the arctangent function in proportion to the increasing trends of δQ. In this way, the value M of positive feedback takes the maximum value M_max, which is achieved with a positive trend δQ, and the minimum value M_min, which is achieved with a negative trend δQ.

If these scaling factors M_max, M_min selected different then positive feedback for positive trends δQ is established otherwise than for negative. For this reason, shifted to the right, the arc tangent function is multiplied by the scaling factor M_max that is greater than the scaling factor M_min, which is multiplied by the shifted to the left, the arc tangent function. M_max here is chosen large enough for positive trends δQ get higher positive feedback, since on the increasing demand for the volumetric flow rate Q should respond faster to avoid insufficient supply.

To feature positive feedback passed through zero, to the sum of the two arctangent functions is added to a negative shift of E, which according to its size, corresponds to the sum of the two arctangent functions for trend δQ=0.

The calculation value M is a positive feedback can be performed numerically on the basis of one of the functions M(δQ) positive feedback in block 7, 7' calculations on the basis of pre-defined trend δQ. Alternatively, an asymmetric function can be maintained by substituting in the position of so-called lookup table in block 7, 7' calculations, in the case of intermediate values for trend δQ between these reference positions can be interpolated.

Fig. 4A shows the H/Q diagram 1 pre-set reference characteristic curve K, colorazione the value of N_{
K}the characteristic curve is where there is a characteristic curve cuts the curve To its maximum speed. At this point of intersection is the maximum volumetric flow Q_max, which can be achieved with regulation along this reference characteristic curve K. the Steepness of the characteristic curve is determined by the fact that its point of intersection lies at half the value of 0.5·H_{K,ref}.

Around the reference characteristic curve To established operating range 3 in the form of strips, in which the positive feedback trend δQ volumetric flow rate. Arrow 5 describes the path along which the working point of the variable-displacement pump could, for example, to move, when executed corresponding to the invention method. Operating range 3 is limited to the upper limit of the characteristic curve, with which is associated the maximum specified value of H_{K,max}the characteristic curve. Accordingly, the operating range is limited to 3 lower limit of the characteristic curve, which is associated to the minimum specified value of H_{K,min}the characteristic curve. Under the relevant invention of the regulation sets the specified value of H_{K}the characteristic curve between the limit specified values�and H_{
K,max}, H_{K,min}and , based on the initial reference characteristic curve K, given the past through regulation characteristic curve is shifted.

In addition, on the H/Q diagram 1 in Fig. 4A presents the calculated point for the heating installation, which, although it lies within the operating range, but not on a pre-set reference characteristic curve K, since this reference characteristic curve For the model pump unit 11 can be installed manually only discretely, and therefore the calculated point with the calculated volume flow Q_A and its design pressure, as a rule, lies next to the selected characteristic curve K. For this reason, the optimal operating point on a conventional fixed characteristic curve It is never reached.

Fig. 4b shows the H/Q diagram with alternative 1 operating range 3, in which the upward direction is limited to the reference characteristic curve K, that is, below this lies exclusively with the characteristic curve To and in addition in the direction of increasing volume flow Q is limited reference value Q_ref volumetric flow rate. Corresponding to the invention a positive feedback trend δQ in this example, execution is attempted only when the operating point of the pump unit 1 is below the reference value Q_ref volumetric flow rate and at or below the reference characteristic curve K,
that is, in the working range 3. Operating range 3 also is limited in the downward direction of the approximate straight line, which at zero volume flow rate is the pressure to one-sixth of H_{K,ref}. Alternatively, any function H_{K,min}=f(Q) may limit operating range 3 in the downward direction.

Shown in Fig. 4A and 4b operating ranges 3 is limited to simple functions in the form of a straight line. In the General case is possible and preferred significantly more difficult to describe the range limit 3. From mathematical modeling, for example, it is known that the operating points of the pump are required to cover the heating demand of the building. Rational operating range 3 for the relevant invention of the method obtained in this example by means of interconnected, framed region in Fig. 4d, in which the vast majority of operating points obtained from numerical simulations. These operating points are sufficient to cover the heat demand is modeled at home. The shaded range inside the framed area 3 indicates the operating points for the night condition. Outside the shaded range, but inside the framed area 2 are the operating points for the day condition.

1. Method for optimized power operation of the pump driven by an electric motor, a hydraulic system with �about at least one self-regulatory consumer
moreover, the specified pressure (H_{soll}) pump is controlled depending on the volumetric flow (Q) is adjustable along the base of the characteristic curve, which is defined by a predefined set value (H_{K}) of the characteristic curve, wherein said determined pump pump volumetric flow rate (Q) and its trend (δQ), and depending on the volumetric flow (Q) and/or trend (δQ) of the setpoint characteristic curve (H_{K}) increase the volumetric flow rate (Q) increases, or decreases, the volumetric flow rate (Q) is decreasing, and c last predefined set value (H_{To alt}) summarize the characteristic curve value (M) positive feedback, and the value (M) of positive feedback is positive, the volumetric flow rate (Q) increases, and is negative when the volume flow (Q) falls.

2. A method according to claim 1, characterized in that trend (δQ) is calculated from the difference of the current volume flow (Q) and its arithmetic mean (

3. A method according to claim 1, characterized in that a certain volumetric flow rate (Q) is multiplied by zero, if it is proportionately less

given m�minimum value (Q_{
min}), or that a particular trend (δQ) is multiplied by zero, if it is proportionately less than the specified minimum value (δQ_{min}).

4. A method according to claim 1, characterized in that the determination value (M) positive feedback is carried out on the basis dependent on the volumetric flow (Q) and/or trend (δQ) functions (f(Q), f(δQ), f(Q, δQ)).

5. A method according to claim 4, characterized in that the value (M) positive feedback is calculated according to symmetric functions, in particular, according to M(δQ)=k·δQ, M(δQ)=k·(δQ)^{3}or M(δQ)=k·arctan(δQ), and k is a positive constant, M is the value of positive feedback and δQ is the trend.

6. A method according to claim 4, characterized in that the value (M) positive feedback is calculated according to an asymmetric function, in particular according to

where M is the value of positive feedback, δQ is the trend, and_{1}and_{2}b_{1}and b_{2}respectively positive scaling factors, s_{1}with_{2}, d_{1}and d_{2}respectively the positive coefficients of the displacement and E - shift for the correction of the zero point, and and and_{1}not equal to a_{2}.

7. A method according to claim 1, characterized in that the value (M) positive feedback proportionately more for positive trends (δQ) than for negative trends (δQ).

8. A method according to claim 4, otlichalis�,
what is the value of (M)

positive feedback adds shift, if the trend (δQ) is positive or equal to 0.

9. A method according to claim 1, characterized in that the value (M) positive feedback is assigned the maximum value (M_max), if it exceeds the upper limit value, or it is assigned a minimum value (M_min) if it falls below the lower limit value.

10. A method according to claim 6, characterized in that the asymmetric function M(δQ) is chosen in such a way that it is for a positive trend (δQ) converges to the maximum value (M_max), and for negative trend (δQ) to the minimum value (M_min).

11. A method according to claim 1, characterized in that the increase or decrease of the values (H_{K}) of the characteristic curve is carried out only in the specified operating range (3).

12. A method according to claim 1, characterized in that the specified value (N_{K}) characteristic curve limit value within the range between the maximum set value (H_{K,max}) and the minimum preset value (H_{K,min}), and the reference setting value (H_{K_ref}) to an identified or identifiable reference characteristic curve (K) lies within this range.

13. A method according to claim 1, characterized in that the specified value (N_{K}) characteristic curve limit value within the range m�waiting for the specified maximum value (H_{
K,max}) and the minimum preset value (H_{K,min}) and a maximum set value (H_{K,max}) corresponds to a given reference value (H_{K_ref}) pre-installed or installed

reference characteristic curve (K).

14. A method according to claim 1, characterized in that the increase or decrease of the set value (N_{K}) of the characteristic curve is carried out only when the volumetric flow rate (Q) lies below a predetermined reference value of the volume flow (Q_ref).

15. A method according to claim 14, characterized in that the predetermined pressure of the pump is controlled along a pre-set reference characteristic curve (K) if the volumetric flow rate (Q) lies above the reference value (Q_ref) volume flow.

16. A method according to claim 12, characterized in that the specified value (N_{K}) characteristic curve gradually reduce speed if it exceeds the maximum specified value (H_{K,max}), stepwise or gradually increase, if it fell below the minimum specified value (H_{K,min}).

17. A method according to claim 13, characterized in that the specified value (N_{K}) characteristic curve gradually reduce speed if it exceeds the maximum specified value (H_{K,max}), stepwise or gradually increase, if it fell below the minimum specified value� (H_{
K,min}).

18. A method according to claim 16 or 17, characterized in that the stepwise change of the target value (N_{K}) of the characteristic curve is in the range from 1 cm to 3 cm, preferably 2 cm per minute.

19. A method according to claim 16 or 17, characterized in that the stepwise change of the target value (N_{K}) of the characteristic curve repeat until, until it is again within the range between the maximum set value (H_{K,max}and

the minimum preset value (H_{K,min}).

20. A method according to claim 1, characterized in that it is used to control the circulation pump of the heating system.

21. Pump driven by electric motor, with the control and regulating electronics, which is arranged to perform the method according to claim 1.

**Same patents:**

FIELD: machine building.

SUBSTANCE: valve has the housing 1 with input 3, output 4 and offtake branch pipes 5. Between internal hollow of the housing 1 and output 4 and offtake branch pipes 5 the seats 6, 7 are located. The housing 1 has a valve block with the valve trays 8, 9, installed on a rotary lever 10 with a possibility of contact of the tray 8 with the seat 6 in one extreme angular position of the rotary lever 10 and the tray 9 with the seat 7 in the other extreme angular position of the rotary lever 10. The axis 11 of the lever 10 is located between output 4 and offtake branch pipes 5 perpendicularly to the plain with the axes of these branch pipes. On the housing 1 fitting is installed, through which in parallel to axis 11 a movable rod of the valve block moving device passes The named facilities also contain the motion booster in the form of double-shoulder lever. The named rod from one end interacts with a heat head thruster, and from another one - with the smaller shoulder of the double-shoulder lever. The greater shoulder of the double-shoulder lever passes through a sealing element. The double-shoulder lever is spring-bias towards the side of pressing of the valve tray 8 to seat 6, adjacent to the output branch pipe 4.

EFFECT: improvement of accuracy of temperature regulation, lowering of hydraulic resistance to the heat carrier flow and improvement of convenience of valve operation.

5 cl, 3 dwg

FIELD: heating.

SUBSTANCE: present invention relates to a method of controlling the maintaining water temperature in the water heater with the heat accumulator controlled by the electronic regulator. The method of controlling the water heater with a heat accumulator in which water heating is carried out by the heating element, controlled by the regulator, which can bring the water temperature to a variable target temperature, and which comprises: defining moment (tONk; t'ONi) of the start of heating to ensure intakes (Pk; Pi) of water comprises the following stages: at short time intervals (δW) all the w intakes are accounted (P1, …, Pi, …, Pw), which moment of start (ti) falls on the specified time window (Δtw) immediately following the current moment of time, and the time window (Δtw) is selected based on the type of water supply system, for which the water heater (1) is designed, and is sufficiently extended to include the moment (ti) of start of all the intakes (Pi), which moments (t'ONi) of the start of imaginary heating presumably precede the moments (t'ON) which correspond to (i-1) preceding intakes (P1, …, Pi-1), at the said moment (ti) of start of intake which falls on the time window (Δtw), the same number of imaginary intakes (P'1, …,P'i, …, P'w) is constructed each of which has the same moment (tw) of start as the start moment of the corresponding real intake (Pi), and the initial temperature (T'set.i) of the imaginary intake determined by adding the initial temperatures (Tset1, Tset2, …, Tset (i-1)) of all water intakes accounted for the time window (Δtw) and preceding the intake itself (Pi), and the corresponding initial temperature (Tset.i) of real intake, on the basis of which each initial temperature (Tset1, Tset2, …, Tset (i-1)) is determined of the optimum temperature (Topt) of discharge according to the formula T'set.i=Tset.i+(Tset1-Topt)+(Tset2-Topt)+…+(Tset(i-1)-Topt), for each of the imaginary intakes (P'1, …, P'i, …, P'w) the moment is calculated (t'ONi) of start of imaginary heating according to the formula t'ONi=ti-(T'set.i-Tm)/VTh, on reaching the earliest of the moments (t'ONi) of start of heating the target temperature (Ttarget) is set at an initial temperature level (T'set.i) of the corresponding imaginary intake (P'i), at that it is understood that the upper limit of the said target temperature (Ttarget) is the maximum set temperature (Tset.max), and to achieve the earliest of the moments (t'ONi) of the start of heating the temperature is maintained (Ttarget) equal to the maintaining temperature (Tstand-by), and the said maintaining temperature (Tstand-by) is the temperature maintained at moments of time remote from the moments of the intake.

EFFECT: invention enables in the planned mode to change with the passage of time the temperature in the water tank.

29 cl, 4 dwg

FIELD: heating.

SUBSTANCE: essence of information-measuring and control system of optimisation of production and consumption of heat energy at the distributed facilities of heat supply comprises a first circuit with a heat source (gas boiler), a heat exchanger, a second circuit of the heat network, a temperature sensor in the straight pipeline of the first circuit, a temperature sensor in the return pipeline of the second circuit, a pressure sensor in the straight pipeline of the second circuit, a gas supply regulator, a gas flow sensor, a fan, an air temperature sensor, an air flow rate sensor, a temperature sensor of waste gases, a metre of produced heat energy, a multichannel microprocessor control unit of energy saving in production of heat energy, a memory unit, a control centre of receiving the information, a unit of control the combustion process in the boiler, a heat supply system, a control unit of heat energy consumption, and the first circuit with a heat source (gas boiler), the first output of which is connected to the input of the temperature sensor of waste gases and through the heat exchanger is connected to the second circuit of the heat network, is connected to the input of the temperature sensor in the straight pipeline of the first circuit, three outputs of the second circuit are connected to the inputs of the temperature sensor in the return pipeline, the pressure sensor in the straight pipeline, the metre of produced heat energy, the outputs of which are connected to the inputs of the multichannel microprocessor control unit of energy saving in production of heat energy, the output of the gas supply regulator by the of gas flow rate sensor is connected to the first input of the boiler, the output of the fan through the air temperature sensor, the air flow rate sensor is connected to the second input of the boiler, the outputs of the gas flow rate sensor, air flow rate sensor, air temperature sensor, temperature sensor of waste gases are connected to the inputs of the multichannel microprocessor control unit of energy saving in production of heat energy, the first output of which is connected to the input of the memory unit, the second output is connected to the input of the control centre of receiving information, the second, third, fourth inputs of the control centre of receiving information are connected to the outputs of the heat supply system by the control units of heat energy consumption, which fourth, fifth, sixth outputs of the second circuit are connected to the inputs of heat supply systems, the output of the control centre of receiving information by the control unit of the combustion process in the boiler is connected to the inputs of gas supply regulator and the fan. Thus, the information-measuring and control system of optimisation of production and consumption of heat energy at the distributed facilities of heat supply enables to optimise the process of production and consumption of heat energy at the distributed facilities of heat supply and to improve energy efficiency of operation of the presented facilities.

EFFECT: enhancing the technological capabilities of the device by controlling a variety of distributed facilities of heat supply in order to increase their efficiency in accordance with the concept of best available techniques.

1 dwg

FIELD: heating.

SUBSTANCE: information and measuring system for monitoring of energy saving at production of thermal energy includes the first circuit with a heat source (a gas boiler), a heat exchanger, the second circuit of a heat network, a temperature sensor in a direct pipeline of the first circuit, a temperature sensor in a return pipeline of the second circuit, a pressure sensor in the direct pipeline of the second circuit, a gas supply control, a gas flow sensor, a fan, an air temperature sensor, an air flow sensor, a waste gas temperature sensor, a produced thermal energy metre, a multi-channel microprocessor energy saving monitoring unit at production of thermal energy, a memory unit, a dispatch information receiving centre; besides, the first circuit with the heat source (gas boiler), the first outlet of which is connected to the inlet of the waste gas temperature sensor and through the heat exchanger is connected to the second circuit of the heat network, is connected to the inlet of the temperature sensor in the direct pipeline of the first circuit; three outlets of the second circuits are connected to inlets of the temperature sensor in the return pipeline, a pressure sensor in the direct pipeline, a produced thermal energy metre, the outlets of which are connected to inlets of the multi-channel microprocessor unit for monitoring of energy saving at production of thermal energy; the outlet of the gas supply control is connected by means of the gas flow rate to the first boiler inlet; the fan outlet is connected by means of the air temperature sensor, the air flow sensor to the second boiler inlet; outlets of the gas flow sensor, the air flow sensor, the air temperature sensor, the waste gas temperature sensor are connected to inlets of the multi-channel microprocessor unit for monitoring of energy saving at production of thermal energy, the first outlet of which is connected to the inlet of the memory unit, and the other outlet is connected to the inlet of the dispatch information receiving centre.

EFFECT: invention allows optimising a thermal energy production process at distributed heat supply facilities and improving energy efficiency of operation of the presented items.

1 dwg

FIELD: power engineering.

SUBSTANCE: control system includes a source of heat, supply and return pipelines, a unit of coolant flow rate control, comprising a flow rate controller and sensors of flow rate, temperature and pressure, installed on supply and return pipelines, a circulating pump, a heat energy processor, linked to sensors and the controller. To achieve the technical result, the unit of coolant flow rate control is equipped with sensors of temperature of external and internal air, at the same time the unit of coolant flow rate control, the circulating pump and the heat energy processor are installed on a load with higher thermal load, other loads of the system are equipped with sensors of coolant flow rate and sensors of internal air temperature, connected to the heat energy processor.

EFFECT: control of heat consumption of a group of loads without installation of a full complex of automatics devices with preservation of the temperature mode, which are connected to heat networks of buildings, which makes it possible to save capital costs, service costs, saving of thermal and electric energy.

1 dwg

FIELD: machine building.

SUBSTANCE: first output of the first circuit with heat source, a gas boiler, is connected with discharge gas temperature gage input and, via heat exchanger, with heat network second circuit. Second circuit three outputs are connected with return pipeline pressure age, forward pipeline pressure gage, their outputs being connected with inputs of multichannel microprocessor unit for control over power saving control in heat power production. Gas feed controller output is connected via gas flow rate metre with boiler first inlet. Blower outlet is connected via air temperature gage and air flow rate gage with boiler second outlet. First output of said microprocessor unit is connected with memory unit with its second output connected to dispatcher data acquisition centre input. Output of the centre is connected via boiler combustion control unit with gas feed and blower controller inputs.

EFFECT: optimised heat production and higher efficiency.

1 dwg

FIELD: machine building.

SUBSTANCE: proposed system comprises at least two temperature control circuits 2, 3, 4. Pressure control unit 18, 19, 20 is arranged to simplify and to optimise power consumption in every circuit 2, 3, 4. Pressure control units 18, 19, 20 allow invariable pressure difference in appropriate circuit 2, 3, 4. Pressure control units 18, 19, 20 equalise pressure difference in all said circuits.

EFFECT: power savings, better convenience.

11 cl, 4 dwg

FIELD: power engineering.

SUBSTANCE: device to adjust and control the flow in heating and cooling systems, in which the flow is controlled with a complete valve, which is a combination of a differential pressure valve (5) and a flow control valve (6). In this device the design of the complete valve provides for flow/passage of water via that piping system, in which this valve is mounted. At the same time the levels of pressure difference P1 at the inlet (2), P2 in the intermediate chamber (4) and P3 at the outlet (3) are measured with metering nipples (27a and 27b), while the pressure difference of P2 and P3 during operation may be controlled.

EFFECT: improved characteristics of a device.

8 cl, 7 dwg

FIELD: machine building.

SUBSTANCE: three-way valve includes body 1 with inlet 2, outlet 3, discharge and valve 5 branch pipes and controlled valve block 6 with sleeve 7, stock 8 and valve plate 9. Inlet 2 and outlet 3 branch pipes of housing 1 are located on one and the same axis and separated with solid partition wall 10. Discharge branch pipe is located at a right angle to branch pipes 2, 3 and interconnected with cavity 11 of inlet branch pipe 2. Valve branch pipe 5 is located perpendicular to the plane of axes of inlet 2, outlet 3 and discharge branch pipes. Its cavity 12 is interconnected through hole 13 with cavity 11 of inlet branch pipe 2, and through channel 14 with cavity 15 of outlet branch pipe 3. On surface 16 of inlet branch pipe 2 inside cavity 12 of valve branch pipe 5 there is valve seat 17 for fitting of valve plate 9. Stock 8 of valve block 6 is installed in sleeve 7 with possibility of back-and-forth movement with projection of its end 18 on one side of sleeve 7 and with projection of end 19 on the other side. Valve plate 9 is fixed on end 19. Stock 8 is spring-loaded in sleeve 7 in the direction of displacement of end 18 from sleeve 7. Sleeve 7 is rigidly fixed in valve branch pipe 5 with possibility of contact of valve plate 9 with valve seat 17 at movement of stock 8 inside body 1 and provided with section 20 of external thread located on the outside to fix an element controlled by the valve. Minimum cross sectional area of channel 14, as well as cross sectional area of hole 21 is less than cross sectional area of hole 13 attaching cavity 11 of inlet branch pipe 2 to cavity 12 of valve branch pipe 5.

EFFECT: enlarging the number of devices for smooth adjustment of a heating degree of a heating appliance, and improving reliability.

6 cl, 5 dwg

FIELD: heating.

SUBSTANCE: single-pipe heat supply system with heat carrier flow control, in which control means of flow rate and supply of heat carrier to the stand pipe of the single-pipe system of typical arrangement are used, for example for building cooperatives, for heat supply to radiators in compartments. The proposed control method relates to control of heat carrier temperature in response to changes of external parameters (temperature) and flow rate in response to changes of heat carrier temperature in return pipeline.

EFFECT: use in the single-pipe heat supply system of double control makes this single-pipe heat supply system high-efficient with power consumption depending on load.

15 cl, 6 dwg

FIELD: engines and pumps.

SUBSTANCE: group of inventions can be used in turbines, pumps or turbine pumps. Device (1) controls movement of cylindrical gate (2) of a hydraulic machine between an opening position and a shutting-off position. Device (1) includes at least four hydraulic cylinders (11, 12, 21, 22, 31, 32), stocks (11.3, 12.3) of which have a possibility of being connected to cylindrical gate (2) in places located along perimeter (c2) of cylindrical gate (2). Additionally, device (1) includes at least two hydraulic synchronisation elements (10.1, 20.1, 30.1) of pistons (11.4, 12.4). Synchronisation elements (10.1, 20.1, 30.1) are connected to hydraulic cylinders (11, 12, 21, 22, 31, 32) so that two different groups (10, 20, 30) can be formed. Each group (10, 20, 30) combines at least two hydraulic cylinders (11-12, 21-22, 31-32) connected at least with one synchronisation element (10.1, 20.1, 30.1), with that, two hydraulic cylinders (11, 12, 21, 22, 31, 32) belonging to two different groups (10, 20, 30) are not connected with synchronisation element (10.1, 20.1, 30.1).

EFFECT: inventions are aimed at simplification of adjustments and maintenance operations of the device and creation of a reliable control device, which is easy to adjust.

13 cl, 8 dwg

FIELD: physics, computer engineering.

SUBSTANCE: apparatus comprises a processor and memory including a computer program code, configured to respond to signalling containing information about instant pressure and a flow rate of fluid being pumped in a pumping system, and obtain an adaptive control curve based on the instant pressure and flow rate using an adaptive moving average filter. The adaptive moving average filter may be based on controlling system flow relating to the adaptive moving average filter (AMAF), flow rate and differential pressure of the system, respectively.

EFFECT: processor, memory and computer program code are also configured to obtain an optimal control pressure point based on the adaptive control curve with respect to an instant flow rate or a moving average flow rate to obtain the desired pump speed through a PID control.

22 cl, 8 dwg

FIELD: engines and pumps.

SUBSTANCE: set of inventions aims at determining the working machine working point and/or that of an induction motor driving the latter whereat the working point is characterised by the power consumed by the said machine and/or by its efficiency. The working machine measured variables depending on the said working points are registered by transducers to evaluate the measured magnitudes and to store them in the machine operation. The working point is defined without the application of the induction motor variables derived by electric measurements. Note here that frequency linearly proportional to the primary tone of the working machine is defined by the analysis of the signal, particularly, by the frequency analysis via one of the variables obtained by mechanical measurements. The said variables include pressure, pressure difference, power, vibration, sound propagating in the solid body or sound propagating in air. The motor rpm (n) is defined to define, therefrom, the working point characterised by the working machine consumed power and/or its efficiency using the ratio (M(n)), that is, the rpm/torque of the induction motor.

EFFECT: inventions aim at the simplified design, reliable determination and current control of the working point.

20 cl, 16 dwg

FIELD: electricity.

SUBSTANCE: electric pump unit comprises a metal body, a contactless direct-current motor installed at the body with an integrated electronic switch, impellers mounted at the motor shaft, a metal pressurized enclosure installed outside the contactless direct-current motor with an electric connector mounted on it. Between leads of one of two power supply poles and electronic switch there is an in-series group of n (n=2, 3, etc.) parallel resistors interconnected by highly heat-conductive materials with pressurized enclosure and placed inside it.

EFFECT: cost-effective control of parameters for the electric pump unit.

3 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed electronic unit can be used for control over borehole motor. It comprises cylindrical case 1 closed at ends by base 3 and head 2 facing the motor, electronic circuit components arranged in sealed compartment, cable glands for connection of electronic components with motor circuits and plug-in terminal of contacts 7, 9. Said unit comprises chassis 11 of segmental cross-section made of material that features high heat and electric conductance. Chassis 11 is arranged to get in thermal contact with inner surface of case 1. Electronic circuit power components 12, particularly those fitted at the chassis 11 flat surface are electrically connected with cable glands. Joint between case 1 and base 3 and head 2 are sealed to sustain high pressure and to make sealed compartment with base 3, head 2 and case interior.

EFFECT: expanded operating performances.

5 cl, 2 dwg

FIELD: engines and pumps.

SUBSTANCE: invention relates to control systems of centrifugal pump units and can be used at liquid pumping. The centrifugal pump control system includes control parameter setting unit (1), the outlet of which is connected to the first inlet of comparison unit (2). The comparison unit outlet is connected to a calculation unit of required speed (3). The outlet of the calculation unit of required speed (3) is connected to frequency and voltage control unit (4). Outlets of frequency and voltage control unit (4) are connected to inlets of frequency converter (5). Outlet of frequency converter (5) is connected to asynchronous electric motor (6) inlet. Outlet of asynchronous electric motor (6) is connected to centrifugal pump (7) inlet. The first outlet of centrifugal pump (7) is connected to the inlet of adjustable parameter sensor (8), and the second outlet is connected to flow transmitter (9) inlet. Outlet of flow transmitter (9) is connected to the second inlet of adjustable parameter calculation unit (10). Adjustable parameter sensor (8) outlet is connected to the first inlet of adjustable parameter calculation unit (10). Outlet of adjustable parameter calculation unit (10) is connected to the second inlet of comparison unit (2).

EFFECT: improving energy efficiency of centrifugal pump plants with frequency rpm control owing to considering hydraulic characteristics of the main line and the pump and minimising powder losses in a centrifugal pump - asynchronous motor power channel.

1 dwg

FIELD: engines and pumps.

SUBSTANCE: control station includes rectifier 1 and DC link filter 2, inverter 3, controller 4 and outlet filter 5, the first 6 and the second 7 units of current sensors, current sensor 8. Inputs 1 - 3 of controller 4 are connected to phase power inputs of the control station. Inputs 4 and 5 of controller 4 are connected to outputs of DC link filter 2, which are connected to power inputs 8 and 9 of inverter 3. The sixth input of controller 4 is connected to output of current sensor 8, through which a conductor is routed, which attaches one of rectifier 1 outputs to the corresponding input of DC link filter 2, inputs 7-9 and 10-13 of controller 4 are connected to outputs 1-3 of the first 6 and the second 7 units of current sensors; with that, each unit of current sensors can contain 2 or 3 current sensors. Conductors are routed through current sensors of the first unit of current sensors 6, which attach output 1-3 of inverter 3 to the corresponding inputs 1-3 of output filter 5, and conductors are routed through current sensors of the second unit of current sensors 7 from outputs 1-3 of output filter 5 to outputs of the control station. Control outputs 1-7 of controller 4 are connected to the corresponding inputs 1-7 of inverter 3. Rectifier can be controllable 10, the control inputs 4-6 of which are connected to control outputs 1-3 of the control unit by rectifier 9, which is connected with its inputs 1-3 to control outputs 6-10 of controller 4 respectively. Use of current sensor 8 provides the possibility of disconnection of inverter 3 at emergency excess current, which is determined by failure of capacitors of the filter or breakdown of DC link buses 2, power modules of inverter 3, which improves reliability. Connection of informative inputs 1-3 of controller 4 to three phase power inputs of the control station (A, B, C) provides protection of inverter 3 when supply voltage exceeds allowable threshold, which improves reliability.

EFFECT: connection of informative inputs 4 and 5 of controller 4 to outputs of DC link filter provides possible voltage stabilisation at inverter 3 output by correction of pulse-width modulation, as well as provides protection of power modules when DC voltage exceeds allowable norms, which improves reliability and enlarges functional capabilities.

2 cl, 4 dwg

FIELD: engines and pumps.

SUBSTANCE: system of control (dwg.1) of a submersible electric centrifugal pump and a group pumping station comprises a unit 1 of setting a dynamic liquid level, a unit 2 of setting of a rotation frequency, lag filters 3 and 4, proportionate-integral controllers 5 and 6, frequency converters 7 and 8, a submersible electric centrifugal pump 9, a group pumping station 10, a sensor 11 of dynamic liquid level.

EFFECT: system of control of a submersible electric centrifugal pump and a group pumping station makes it possible to stabilise oil well debit.

4 dwg

FIELD: machine building.

SUBSTANCE: turbine unit automatic control system comprises a centrifugal pump, an electric motor, a device to change the speed of the centrifugal pump rotor, an automatic control system providing for the specified centrifugal pump rotor speed, a switch unit for frequency input signals, a pressure sensor at the pump inlet and a pressure sensor at the pump outlet, a liquid flow metre, a parameter calculation unit, a unit to set the form of head-capacity curve of the compressor, a unit to set the form of pump efficiency factor, a unit to form the pump operating parameters, a detector of the actual operating parameters of the pump and the pipeline, a unit to calculate the actual rotor speed, a unit to set the design characteristic of the pipeline, a detector of design operating parameters of the pump and the pipeline, a unit to calculate the design rotor speed.

EFFECT: providing operation of turbine units with maximum possible efficiency coefficient irrespective of variation of pipeline characteristic.

1 dwg

FIELD: machine building.

SUBSTANCE: turbine unit optimal control system comprises: a centrifugal pump, an electric motor, a device to change the speed of the centrifugal pump rotor, an automatic control system providing for the specified centrifugal pump rotor speed, a centrifugal pump rotor speed summer, an automatic controller unit, a pressure sensor at the pump inlet and a pressure sensor at the pump outlet, a centrifugal pump head metre, a liquid flow metre, a heads' comparing element, a unit to define the maximum efficiency lines of the centrifugal pump, a calculator of the maximum efficiency of the centrifugal pump, a unit for the approximation of the efficiency characteristic of the centrifugal pump, a unit for the approximation of the head characteristic of the centrifugal pump.

EFFECT: providing their operation with maximum possible efficiency coefficient irrespective of variation of pipeline characteristic.

1 dwg

FIELD: artesian wells.

SUBSTANCE: invention relates to general-purpose regulating and control systems and it can be used to control electric pumps of artesian wells. Proposed control device contains switching element connected by inputs to supply voltage terminals and by outputs, to electric pump terminals, water level transmitter in water tower and electric pump check and control unit connected by first input with output of water level transmitter and by first output, with control input of switching element, voltage comparator, like inputs of first and second groups of inputs of voltage comparator being connected, respectively, with supply voltage terminal and with electric pump terminal connected with like phase, and voltage measurement unit whose inputs are connected with supply voltage terminals. Outputs of voltage comparator and voltage measurement unit are connected, respectively, with second and third control inputs of check and control unit of electric pump.

EFFECT: improved reliability of water supply.

2 cl, 3 dwg