JP2010275688A - Boost water supply system for high-rise building - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a boost water supply system for high-rise building operating a plurality of variable speed pumps arranged in parallel and driven by an electric motor controlled by variable voltage-variable frequency power supply and controlling their pressure by a discharge pressure constant control method or an inferred terminal pressure constant control method. <P>SOLUTION: This boost water supply system for high-rise building is divided into a low pressure system for first-fourth stories and a high pressure system for fifth-eighth stories. In this boost water supply system, a water supply unit for the high pressure system for fifth-eighth stories corresponds to a water supply unit for the low pressure system for first-fourth stories, and a composite booster unit composed of two sets of water supply units in total is applied to dispense with a water supply system for first-fourth stories and a pressure reducing valve owing to this design. The water supply unit for the low pressure system for first-fourth stories can be operated by the pressure set lower than pressure for the water supply unit for the high pressure system for fifth-eighth stories. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  In the present invention, a plurality of variable speed pumps driven by an electric motor controlled by a variable voltage / variable frequency power source are operated in parallel, and the pressure is controlled by a constant discharge pressure control or an estimated terminal pressure constant control method. It relates to the increased pressure water supply system for high-rise buildings. According to the present invention, the pressure increasing water supply unit controlled by the constant discharge pressure control or the estimated terminal pressure-constant control is combined with a high pressure increasing unit (for H system) and a low pressure increasing unit (for L system). High-rise building pressure booster configured to supply the required amount of water at the required pressure to all floors of medium- and high-rise buildings by connecting multiple units of the above-mentioned complex pressure boosting units in series. It relates to the water supply system.

  As for the conventional pressurized water supply system for high-rise buildings, for example, Japanese Patent Application Laid-Open No. 2008-223269 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2008-240276 (Patent Document 2) assume that the pressurized water supply units are arranged in series. is there. However, the high-pressure building water supply system for high-rise buildings is configured as one set, and the water supply system is also configured as one system. For this reason, the pressure-increasing water supply system for high-rise buildings in Patent Document 1 and Patent Document 2 requires a pressure reducing valve in the water faucet on the lower floor.

  In addition, in the case of 6-story buildings and 9-story buildings, the increased-pressure water supply system for high-rise buildings solves multiple pressure-increasing water supply units in series by the zoning method. However, the pressure-increasing water supply system for high-rise buildings is one set, and the water supply system is also composed of one system.

JP 2008-223269 A JP 2008-240276 A

  The present invention provides a low-pressure water supply unit for a low-floor floor faucet by configuring the pressure-increasing water supply unit as a combined pressure increase unit of a high-pressure water supply unit (for H system) and a low-pressure water supply unit (for L system). The pressure reducing valve is omitted by supplying water. Further, according to the present invention, the set pressure of the low-pressure water supply unit or the target curve pressure of the estimated terminal pressure constant control can be set lower than in the case of the conventional l water supply system, so that the energy saving effect can be increased.

  In the present invention, the booster pump unit is composed of a high pressure water supply unit and a low pressure water supply unit composite pressure increase unit, and a low hierarchy zone composite pressure increase unit, an intermediate hierarchy zone pressure increase unit, and an upper hierarchy zone composite pressure increase unit. An object of the present invention is to provide a pressure-increasing water supply system for a high-rise building that eliminates the pressure reducing valve on the lower floor and improves the energy saving effect.

  The case where the pressurized water supply system for high-rise buildings of this invention supplies water to an eight-story building is considered, for example. In this case, the water supply system is divided into a low pressure system for 1-4 floors and a high pressure system for 5-8 floors. The present invention applies a composite pressure increasing unit constituted by a total of two sets of water supply units, corresponding to the 5-8th floor high pressure system water supply units and the 1st-4th floor low pressure system water supply units. With such a design, the water supply system on the 1st to 4th floors does not require a pressure reducing valve.

  In addition, the low-pressure system water supply unit for the first to fourth floors can be operated under a lower pressure setting than the high-pressure system water supply unit for the fifth to eighth floor water supply, The energy saving effect is greater than when operating up to the 8th floor with a single water supply unit under a high pressure setting.

  According to the present invention, the pressure boosting pump unit of 0.75 Mpa, which is defined as the maximum pressure in the standards of the current Japan Water Works Association, is adopted for the high pressure system of the composite pressure increasing unit, and the increase for this high pressure system is adopted. A water supply system for a high-rise building can be constructed by connecting pressure units in series.

  According to the present invention, since the low pressure system of the combined pressure increasing unit can be adopted for the low-floor water supply of each floor, no pressure reducing valve is required.

  According to the present invention, since the high pressure system and the low pressure system are divided into two systems, the set pressure of the low pressure system can be set to be smaller than the set pressure of the high pressure system. The capacity is also reduced.

It is the whole block diagram which showed the structure of the composite pressure increase water supply unit series system for high-rise buildings of this invention. (Example 1) It is a detailed block diagram of the composite pressure increase water supply unit of the low hierarchy zone of this invention. It is a detailed block diagram of the pressure controller for high pressure systems of the composite pressure increase water supply unit of this invention. It is a detailed block diagram of the pressure controller for low pressure systems of the composite pressure increase water supply unit of this invention. It is a figure for demonstrating comparatively about energy saving between the pressure increase water supply system for high-rise buildings of this invention, and the conventional system.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is an overall configuration diagram showing a configuration of a combined pressure increasing water supply unit series system for a high-rise building according to the present invention. The composite pressure increasing unit in the pressure increasing water supply system for a high-rise building of the present invention includes three sets of a low-level zone (200-1), a middle-level zone (200-2), and an upper-level zone (200-3). It is configured in series as shown.

  The combined pressure increasing units (200-1), (200-2), (200-3) are composed of water supply units for high pressure system (H system) and low pressure system (L system), respectively. The water taps on the 5th to 8th floors and the water taps on the 1st to 4th floors of each floor are connected separately. For example, the water taps connected to the high pressure system of 5 to 8 floors in the low zone are 20 to 5, 20 to 6, 20 to 7, and 20 to 8. Similarly, the water taps connected to the low pressure system on the 1st to 4th floors are 20-1, 20-2, 20-3, and 20-4.

  Similarly, the water taps connected to the high pressure system of the middle hierarchy zone and the upper hierarchy zone are 2l-5, 21-6, 21-7, 21-8, 22-5, 22-6, 22-7 , 22-8, and the water taps connected to the low pressure system are 21-1, 21-2, 21-3, 21-4, 22-1, 22-2, 22-3, 22-4 It has become. By comprising in this way, it can design so that a pressure-reduction valve is not required for the water supply system from the 4th floor to the 1st floor of each hierarchical zone. In the method of the present invention, the proposed water supply system has the disadvantage that two water supply systems are required rather than the series system of one pressure-increasing water supply unit. In the system of the present invention, the energy saving effect is greater than that of the conventional system, which is offset. Rather, it is an advantage of the present invention.

  First, the composite pressure increasing unit of the present invention will be described. FIG. 2 shows the details of the combined pressure increasing unit 200-1 of the present invention. Each of the high-pressure system and the low-pressure system water supply unit is composed of a pressure-increasing water supply unit of a parallel / alternate operation system with two pumps. First, the high pressure system will be described. The pumps (P1, P2) 11-1 and 11-2 are driven by induction motors 11-15 and 11-16, which are variable voltage / variable frequency controlled by inverters 11-17, 11-18. The check valves 11 to 3 and l1 to 5 and the cutoff valves 11 to 4 and 11 to 6 are respectively provided on the pump discharge side.

  The check valves 11 to 7 for backflow prevention indicate, for example, a double type that prevents backflow from the pump side to the water main. The cutoff valves 11 to 8 and 11 to 9 detect that the pump suction side, and the flow switches 11 to 10 detect that the feed water flow rate is low, for example, 10 to 20 l / min or less. The pressure sensors 11 to 11 detect the discharge pressure of the pump. Further, the pressure sensors 11 to 12 detect the water main pressure, for example, when the main pressure becomes 10 m or more at the head, interlock so that the water supply pumps P1 and P2 can be operated. The pressure tanks 11 to 13 are for holding pressure when the pump is stopped.

  Moreover, the water taps 20-5 to 20-8 show the high pressure system. The pressure controller 31 controls the induction motors 11 to 15 and 1 to 16 that drive the pumps P1 and P2 by the inverters 1 to 17 and l1 to 18, so that the pump discharge pressure is constant. Alternatively, the estimated end pressure is controlled to be constant. The details of the pressure controller for the high pressure system of the embodiment are shown in FIG.

  Next, the structure of the low pressure system water supply unit will be described. The pumps (P8, P4) 12-1 and 12-2 are driven by induction motors 12-15 and 12-16, which are variable voltage and variable frequency controlled by inverters 12-17, 12-18. The check valves 12 to 3 and 12 to 5 are on the pump discharge side, and the cutoff valves 12 to 4 and 12 to 6 are on the discharge side. The check valves 12 to 7 for backflow prevention indicate, for example, a duplex system that prevents backflow from the pump side to the water main. The cutoff valves 12 to 8 and 12 to 9 detect that the pump suction side, and the flow switches 12 to 10 detect that the feed water flow rate is low, for example, 10 to 20 l / min or less.

  The pressure sensors 12 to 11 detect the discharge pressure of the pump. Moreover, the pressure sensors 12-12 detect the water main pressure, for example, when the main pressure becomes 10 m or more at the head, they are interlocked so that the water supply pumps P3 and P4 can be operated. The pressure holding pressure tanks 12 to 13 hold the pressure when the pump is stopped. Moreover, the water taps 20-1 to 20-4 show the low pressure system.

  The pressure controller 32 uses the inverters 12-17, 12-18 to control the induction motors 12-15, 12-16, which drive the pumps P3, P4. Alternatively, the estimated end pressure is controlled to be constant. The details of the pressure controller 32 for the low pressure system conform to the pressure controller for the high pressure system. Several methods have been announced for the constant control of the estimated end pressure.

  In FIG. 3, the control operation of the estimated terminal pressure constant control applied to the present invention will be described. The PI or PID controllers 31 to 1 that perform pressure control compare the pump discharge pressure h1 (pu) detected by the pressure sensors 11 to 1l with the pressure set value hs (pu) set in the pressure controller 31. The deviation is given as input.

The deviation is amplified by the PI or PID controllers 31 to 1, and the output becomes the inverter frequency command fs * (pu). The frequency command fs * gives the frequency commands f1s and f2s to the inverters 11 to 17 and 11 to 18 through the D / A converters 31 to 2 and 31 to 3, respectively. The RUN1 and RUN2 signals given to the inverter from the sequence control blocks 31 to 7 (SEQ) are ON and OFF signals for starting and stopping the inverter. When the inverter is started, "1" is set and "0" is set when the inverter is stopped. give. Therefore, if the RUN1 and RUN2 signals are “1”, the inverters 11 to 17 and 11 to l8 cause the deviation to decrease with the pressure set value hs as a reference value and hI as a feedback value. Induction motor ll ~ 15, speed of 11 ~ 16, therefore pump 11 ~ 1, 11 ~ 2
Adjust the speed and perform pressure control.

Here, the pressure set value hs is given by the sum of the minimum pressure set value ho (pu) set inside the pressure controller 31 and the output Δh (pu) of the friction head calculators 31 to 6 (HEAD). It is done. That means
hs = ho + △ h (pu) (1)
The friction head calculators 31 to 6 (HEAD) receive the estimated flow rate q * (pu) that is the output of the flow rate calculators 31 to 5 (FLOW), and the friction loss lift Δh (pu ) Is calculated.
△ h = Kq · q * ² (pu) (2)
Here, Kq is a friction loss lift coefficient. For example, ho = 0. 7 When set to (pu).

For single pump operation, K q = l. 0 −ho = 1. 0 −0. 7 = 0. Set to 3. Therefore, hs = 0. 7 + 0.3 × q * ² can be calculated. Similarly, when two pumps are operating in parallel,
Kq = (1.0−ho) / 4 = (1.0−0.7.7) / 4 = 0. Set to 075. In this way, a target curve for the estimated terminal pressure constant control can be obtained.

Next, calculation of the flow rate q * (pu) by the flow rate calculators 31 to 5 (FLOW) will be described. The pump head approximation formula can be given by the following formula (3).
hP = a ・ n ² −b ・ q ² (3)
Where hP = pump head (pu) = pump head Hp (m) / pump rated head HN (m)
n = Pump speed (pu) = Pump speed N (rpm) / Pump rated speed Nn (rpm)
q = Pump flow rate (pu) = Pump flow rate Q (m ³ / min) / Pump rated flow rate Qn (m ³ / min) a, b = Pump constant

The discharge head h1 (pu) of the water supply unit is h1 = discharge head H (m) / pump rated head Hn (m) and is given by equation (4).
hI = hP + hs−hsUo−hsul (4)
Where hsu = pump lift on the pump suction side (pu) = push lift on the pump suction side Hsu (m) / pump rated lift Hn (m), hsuo = fixed loss lift of the check valve for backflow prevention on the pump suction side (pu) = Check valve fixed loss lift for backflow prevention on pump suction side Hsuo (m) / Pump rated lift Hn (m), hs · (pu) = Friction loss lift of check valve for backflow prevention on pump suction side (pu) = pump suction side friction loss lifting head Hsul (m) / pump rated head Hn (m). Here, hs. (Pu) can be approximated by equation (5).
hsUL ＝ hLo ・ q ²・ ・ ・ (5)

Here, huo is the friction loss lift coefficient of the check valve for backflow prevention. Substituting equations (5) and (4) into equation (3) and rearranging them gives equation (6).
^{q = ((a · n 2} -h1 + hsu -hSUO) / (b + hlo)) 1/2 ··· (6)
h1 and hsu can be detected by pressure sensors 11 to 11 and 1l to 12, and the fixed loss hsuo of the check valve for backflow prevention and the same friction loss coefficient hlo are used for the pressure drop test of the check valve for backflow prevention. Can be set from the results.

  Therefore, if the pump speed n can be estimated, the flow rate can be estimated by equation (6). Here, a method for estimating the pump speed n will be described. The frequency commands fls and f2s are given as inputs of a soft starter provided in the inverter. This soft starter has a function of converting a stepped frequency command into a ramp-shaped frequency command with an inclination set in a soft scooter. That is, the frequency signal actually supplied to the inverter becomes this ramp-shaped frequency command. For example, if stepped rated frequency commands are given as f1s and f2s, if the acceleration time limited to the soft starter is 1.0 sec, it is converted to a frequency command that ramps up to the rated frequency in 1.0 sec. The

  The output signal fs * signal of PID or PI controllers 31 to 1 does not match the actual spark frequency command. Therefore, in this case, soft starters having the same function as the soft start in the inverter are prepared in the flow rate calculators 31 to 5 (FLOW). Therefore, by making the setting of the soft starter prepared in the flow rate calculators 31 to 5 (FLOW) the same as the setting inside the inverter, the frequency command actually given inside the inverter can be simulated.

Assuming that the output of the soft starter is fls * and f2s *, the frequency of the pump can be estimated by the equations (7) and (8) based on the first-order lag time constant using the frequency command as an input.
n1 = (1 / (Tmls + 1) · fls * (pu) ... (7)
n2 = (1 / (Tm2s + 1) · f2s * (pu) ... (8)
Where n1 = 11 ~ l Pump speed (pu)
＝ 11 ～ 1 Pump speed shame / 11 ～ l Rated speed of pump (rpm)
n2 = 11 to 2 Pump speed (pu)
= 1 to 2 Pump speed (rpm) / 11 to 2 Pump rated speed (rpm)
Tm1 = 1l ~ 15 Induction motor inverter frequency command f1s * Delay time constant from speed n1 (sec)
Tm2 = 11-16 Induction motor inverter frequency command f2s * to time n2 delay time constant (sec)
s = Laplace operator

By the way, the pumps 11 to 1 and the pumps 11 to 2 are usually of the same rating, and the induction motors 11 to 15 and 11 to 16 have the same rating. Also, the soft starters of the respective inverters have the same function and the set time is set to be the same. Therefore, f1s * = f2s * and Tm1 = Tm2 can be set. That is, n1 = n2. Therefore, if the pump speed is n, the delay time constant is Tm, and the output of the soft starter is fns *, equation (9) can be obtained.
n = (1 / Tms + 1)) fns * (pu) (9)

  Here, fns * prepares the soft starter with the same function as the soft starter inside the inverter from the output of PI or PID controller 31 to 1, and sets the flow calculator 31 to 5 (FLOW). Can be detected from their outputs. Therefore, by detecting the pump speed by the equation (9) and substituting the result into the equation (6), the flow rate every moment can be calculated. Here, the estimated flow rate is expressed as q * (p.u.). This q * (p.u.) Becomes an input signal of the friction head calculators 31 to 6 (HEAD), and Δh is calculated by the above equation (2).

  Next, the control operation of the sequence control circuits 31 to 7 (SEQ) will be described. This basic control operation is known as a direct-feed pressure booster pump unit of a parallel / alternate operation system with two pumps. In other words, the sequence control circuits 31 to 7 (SEQ) are sequence control blocks that perform sequence control and protection, interlock, and the like for operation, stop, parallel input, and disconnection of the direct-feed pressure booster pump unit. For example, when the flow switches 11 to 10 detect that the water supply amount has decreased and the time has continued for a predetermined time, it is determined that the picture water amount is almost zero, and the pump is switched to the pressure holding operation control.

  In the pressure holding operation, the pressure setting is switched to the pressure holding pressure (however, not shown in FIG. 3), and the pump is operated for a certain period of time at this pressure, and the pressure water is accumulated in the pressure tanks 11-13. When the set pressure holding operation time has elapsed, the pump is stopped. If the suction side pressure of the pump falls below the specified pressure during the pump operation, RUN1 and RUN2 are set to "0" to stop the pump and protect the pump from cavitation.

  Further, when the pump suction side pressure recovers to a level higher than the restartable pressure with all the pumps stopped, the pump startable interlock circuit is completed. When this condition is completed, if the pump discharge side pressure is set in advance and becomes equal to or lower than the pressure, the selected pump, for example, the later pump is automatically started by the automatic alternate operation control. In this way, the sequence control circuits 31 to 7 (SEQ) execute a control sequence known as a direct feed water pressure booster pump unit required for the parallel / automatic alternating operation method.

  The above is a description of the pressure control and the sequence control for the high pressure system of the pressure controller 31 of 200-1 in FIG. The pressure control and sequence control of the low pressure system of the pressure controller 32 are based on the pressure control and sequence control of the high pressure system. That is, as shown in FIG. 4, the details of the pressure controller 32 are obtained by changing all the drawer symbols 31 to XX to 32 to XX, and the operation thereof is the same as that described for the drawer symbol 3I. However, the controlled inverter, electric motor, and pump are changed to corresponding devices as shown in FIG.

  Inverters are labeled 12-17, 12-18, induction motors are labeled 12-15, 12-16, pumps are P3 pumps 12-1, P4 pumps 12-2, discharge side pressure sensors are labeled 12-11 The suction side pressure sensor is indicated by reference numerals 12 to 12, and the low flow detection flow switch is indicated by reference numerals 12 to 10. In the present invention, the minimum pressure set value ho (p.u.) Of the pressure controller 32 shown in FIG. 4 is smaller than the minimum pressure set value ho (p.u.) Of the pressure controller 31 shown in FIG.

  Next, the reason why the energy saving effect is greater than that of the conventional method according to the combined pressure increasing water supply unit as in the present invention will be described with reference to the qh characteristic of FIG. FIG. 5 is a water supply system for an 8-story building, explaining the operating point of the water supply unit when a low pressure system is applied to the 1st to 4th floor systems and a high pressure system water supply unit is applied to the 5th to 8th floor systems. It is.

  In this example, the rated head of the pump for the high pressure system is 40 m, the rated head of the pump for the low pressure system is 30 m, the pushing head on the pump suction side is 20 m, the fixed loss lifting head of the check valve for backflow prevention is 5 m, and the friction loss The stroke is 2m / l00% flow rate. The water supply load is expressed with the total water supply flow rate on the 1st to 4th floors being 100%, and the total water supply flow rate on the 5th to 8th floors is also 100%.

  In the conventional booster pump unit, the feed water flow rate at full load is 200%. Hm in FIG. 5 is a target curve for the estimated terminal pressure constant control for the high pressure system, and hL2 is a target curve for the estimated terminal pressure-constant control for the L system. When the feed water flow rate decreases from 100% to a certain flow rate, pressure control is performed along the hL1 curve in the high pressure system and along the hL2 curve in the low pressure system. Now assume that the flow rate is 100%. Then, the operating point of the water supply unit is point A in the high pressure system and point A1 in the low pressure system.

  In this case, the head characteristic h1 of the high pressure system is calculated from the pump head of the high pressure system + pushing head-fixing of the check valve for backflow prevention and the friction loss head. Similarly, h2 is calculated from the pump head of the low pressure system + push head—fixing of the check valve for backflow prevention and the friction loss head. Here, hsn1 in FIG. 5 represents the net pushing stroke when the composite pressure increasing pump unit is employed as in the present invention, that is, pushing net lifting height hsun = pushing lifting height hsu—fixing of the check valve for backflow prevention, and friction. Calculated as the loss head (hsuo + hsL).

  Accordingly, the hydraulic power of the pump when the water supply unit is operating at points A and A1 is proportional to the quadrilateral ABCD and quadrilateral A1BCD1, respectively. When the water power w12 (p.u.) of the example of the present invention is calculated and viewed, W12 = (1−0.350) × 1. 0+ (0.750−0.350) × 1. 0 = 1.05 (p.u.). In the conventional system, the rated head is for the 8th floor building, 40 m as in the above high pressure system, but a pump with a rated flow rate of 200% is selected so that the rated lift is achieved at 200% flow rate. Therefore, as shown in FIG. 5, the hL8 is designed to be a target curve.

  The pump head characteristics of the water supply unit are calculated as follows, assuming that the pump head on the pump suction side is 20m, the fixed loss lift of the check valve for backflow prevention is 5m, and the printing loss lift is 2m / 200% flow rate. Therefore, as with the conditions of the present invention, in the case of full load water supply, the operating point of the conventional water supply unit is the Ao point. The hydraulic power of the pump in this case is proportional to the quadrilateral AOBOCD. In other words, the water power Wo (p.u.) Is Wo = (1−0,350) × 2.0 = 1. It becomes 3o (p.u.). That is, if the method of the present invention is adopted, the water power of 1.30−l.05 = 0.25 (p.u.) can be saved, and it can be said that the energy saving effect is high.

Next, it will be described that the equipment capacity is reduced according to the method of the present invention. When the rated flow rate in the above embodiment is Q (m ³ / min), the capacity of the induction motor for pumps of the present invention is
Motor capacity for high pressure system PH = 0,163 x 40 x Q / ηp (KW)
Low pressure system motor capacity PL = 0,163 x 30 x Q / ηp (KW)
It becomes. On the other hand, the capacity of the conventional induction motor for pumps is the capacity of the conventional motor Po = 0.163 x 40 x 2Q / ηp (KW)
It becomes.

Here, ηp is the pump efficiency. Here, assuming that the pump efficiency is equal, the ratio of the total electric field capacity of the present invention and the conventional motor capacity is:
[(0.163 Q / u) (40 + 30)] / [[(0.163 Q / u) 80] = 7/8
It becomes. That is, the installed capacity in terms of the motor capacity is 87.5% in the case of the present invention compared to the conventional system. As described above, the application of the composite pressure-increasing water supply unit of the present invention has the advantage that not only the low-floor pressure reducing valve required in the conventional method can be omitted, but also the energy saving effect can be increased.

  The high pressure system of this compound pressure boosting unit is defined as the highest pressure in the current Japan Water Works Association standard. If designed with a booster pump of 75 Mpa and connected in series as shown in FIG. It will be possible to construct a pressurized water supply system for high-rise buildings that requires a pressure of 75 MPa or more at a low cost. However, in FIG. 1, the compound pressure increasing unit used for the middle layer zone is shown as 200 to 2, and the compound pressure increasing unit used for the upper layer zone is shown as 200 to 3.

  The said structure has a function similar to the pressure increase unit 200-1 for low hierarchy zones demonstrated above. Although not shown in the figure, a sequence control function accompanying serial operation is added to the sequence control block SEQ of each of the high pressure system pressure controllers 31 of 200 to 1, 200 to 2, and 200 to 3. These techniques are ordinary techniques. For example, when a pump higher than the self is automatically started, even if there is no water supply request for the self-hierarchy to be shared, it is automatically started to complete a series water supply system from the water main.

  Further, even when the water supply amount of the self-level is reduced to zero during the series operation, if the upper-level pump is operating, the operation is controlled to continue. By such a sequence control function, the water supply operation of all floors is enabled by the serial configuration of the complex pressure increasing units.

Claims (2)

For high-rise buildings where multiple variable speed pumps driven by an electric motor controlled by a variable voltage / variable frequency power supply are operated in parallel, and the pressure is controlled by constant discharge pressure control or estimated terminal pressure constant control method In the pressurized water supply system,
A first combined pressure increasing unit having a low pressure system pump and a high pressure system pump;
A water supply section for a first lower floor supplied from a pump of the low pressure system of the first composite pressure increasing unit;
A water supply section for a second lower floor located on the lower floor supplied from the pump of the high pressure system of the first combined pressure increasing unit;
A second combined pressure increasing unit having a low pressure system and a high pressure system pump;
A first middle floor water supply unit supplied from a low pressure system pump of the second combined pressure increasing unit;
While increasing the pressure by the pump of the high pressure system of the second combined pressure increasing unit, the second middle floor water supply section located on the middle floor,
A third composite pressure increasing unit having a low pressure system and a high pressure system pump, wherein the pressure is increased by a high pressure system pump of the second composite pressure increasing unit;
A water supply section for a first higher floor supplied from a pump of a low pressure system of the third combined pressure increasing unit;
While increasing the pressure by the pump of the high pressure system of the third combined pressure increasing unit, the second high-rise floor water supply unit located on the high-rise floor,
A high-pressure water supply system for high-rise buildings that consists of   2. The increased pressure water supply system for a high-rise building according to claim 1, wherein the composite pressure increase unit has a number of three or more and can be applied to a water supply section from a lower floor to an upper floor.

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