JP4954668B2 - Heating system - Google Patents

Description

  The present invention relates to a heating system that generates hot water by heating cold water with a heating fluid such as steam.

  2. Description of the Related Art Conventionally, a hot water supply apparatus that is a type of heating system that generates hot water by heating cold water with steam is known (see Patent Document 1). As shown in FIG. 8, the heating system in this hot water supply apparatus generates hot water M by heating cold water C with heat of a heating fluid S such as steam by a heat exchanger 60, and is supplied from a water supply source WA. The cold water C is led to the heat exchanger 60 by a cold water pipe 61, the heating fluid S from the heating fluid supply source VA is led to the heat exchanger 60 by a heating fluid pipe 62, and the cold water C and the heating fluid are heated by the heat exchanger 60. Hot water M generated by heat exchange with S is led out from the hot water pipe 63. The heating fluid pipe 62 is provided with a regulating valve 64 for adjusting the passing amount of the heating fluid S flowing inside, and the hot water pipe 63 is provided with a temperature sensor 65 in the vicinity of the outlet side of the heat exchanger 60. ing.

  In the hot water supply device, hot water M is generated by heat exchange between the cold water C from the water supply source WA and the heating fluid S from the heating fluid supply source VA in the heat exchanger 60, and this hot water M is opened by the curan 66. It is taken out by the valve. The heated fluid S after the heat exchange that has passed through the heat exchanger 60 is discharged to the outside from the discharge passage 67 as condensate (drain). In this hot water supply apparatus, the temperature of the hot water M generated by the heat exchanger 60 is detected by the temperature sensor 65, and the temperature information of the detected hot water M is fed back to the control valve 64 by the feedback circuit 68. If the temperature is high, the supply amount of the heating fluid S to the heat exchanger 60 is decreased by restricting the adjustment valve 64. Conversely, if the temperature of the hot water M is low, the supply amount of the heating fluid S is reduced by opening the adjustment valve 64. It is made to increase and the hot water M of predetermined temperature is taken out.

JP 2006-127719 A

  However, the hot water supply apparatus requires a complicated mechanism that senses the temperature of the hot water M and feedback-controls the control valve 64 based on the sensed temperature. The temperature of the hot water M is likely to change unexpectedly due to a delay in sensing the temperature of the hot water M or a change in the temperature of the hot water M relative to a change in the supply amount of the heating fluid S. Difficult to generate. Moreover, since the temperature of the hot water M generated by the heat exchanger 60 is always detected by the temperature sensor 65 even when the curan 66 is closed, that is, when the hot water M is not used, this temperature information. Therefore, the feedback circuit 68 feedback-controls the control valve 64 to control the supply amount of the heating fluid S to the heat exchanger 60 so as to keep the temperature of the hot water M at a predetermined value. However, when the temperature of the hot water M decreases due to heat radiation in the hot water pipe 63, the heating fluid S is supplied to the heat exchanger 60 and is wasted.

  The present invention has been made in view of the above-described conventional problems, and can always stably generate hot water at a predetermined temperature while using a simple and inexpensive configuration, and wasteful heating fluid such as steam is consumed. It aims to provide a heating system that will never be done.

In order to achieve the above object, a heating system according to a first configuration of the present invention includes a heat exchanger that generates hot water by heat exchange between a heating fluid and cold water, and the heating fluid from a heating fluid supply source. The heating fluid passage leading to the heat exchanger, the cold water passage leading the cold water from the water supply source to the heat exchanger, and the cold water passage are provided so that the upstream pressure is larger than the downstream pressure by a predetermined value or more. when it becomes, and the pressure valve to open by the pressure difference, the provided heated fluid passage, the supply of heating fluid to the heat exchanger in accordance with the differential pressure between the upstream side and downstream side of the pressure valve An adjustment valve for adjusting the amount, and an orifice provided in a bypass path of cold water that bypasses the pressure valve, and a valve port of the pressure valve and the orifice are formed in a partition wall provided in the cold water passage, The pressure valve opens and closes the valve port A body and a compression spring for pressing the valve body to the valve port, and an adjusting screw the by changing the spring force of the compression spring adjusting the opening pressure. Here, the hot water includes not only hot water of about 40 ° C. to 60 ° C. but also hot water of over 60 ° C.

According to this configuration, for example, when the hot water is not used by closing the curan, the cold water is not flowing in the cold water passage, and between the upstream side and the downstream side of the orifice provided in the cold water passage. No differential pressure is generated. In this case, since the adjustment valve that adjusts the supply amount of the heating fluid to the heat exchanger according to the differential pressure between the upstream side and the downstream side of the orifice is closed, the heating fluid is not supplied to the heat exchanger. The heating fluid is not wasted. On the other hand, for example, when hot water is used with the curan open, the cold water flows in the cold water passage toward the heat exchanger, and the cold water flows between the upstream side and the downstream side of the orifice provided in the cold water passage. Differential pressure is generated. Therefore, a control valve that adjusts the supply amount of the heating fluid to the heat exchanger according to the differential pressure of the cold water upstream and downstream of the orifice is opened, and the heating fluid is supplied to the heat exchanger by this control valve. The At this time, the opening degree of the control valve is adjusted according to the magnitude of the differential pressure. Thus, the heating fluid is not consumed when hot water is not used, and the heating fluid is consumed only when hot water is used, and the supply amount of the heating fluid is controlled according to this differential pressure. Therefore, the heating fluid is used efficiently. Further, since the temperature of the hot water is detected and the control valve is not feedback controlled, there is no delay in temperature detection, and hot water having a stable temperature can be obtained at all times. In addition, the conventional system has a simple and inexpensive configuration as compared with the case where a complicated mechanism for feedback-controlling the control valve based on the temperature of hot water is provided, and as a result, cost reduction can be achieved. Furthermore, the structure is compact, and the differential pressure generated between the upstream side and the downstream side of the orifice can be directly applied to the upstream side and the downstream side of the pressure valve. improves.

  Here, when the flow rate of hot water, that is, the flow rate of cold water is small, cold water passes only through the orifice, and at that time, the differential pressure is generated. On the other hand, when the flow rate of the chilled water is large, the pressure valve opens as a result of the differential pressure across the orifice exceeding a predetermined value, and the chilled water passes through both the orifice and the pressure valve, so that a sufficient flow rate is ensured.

The heating system according to the second configuration of the present invention includes a heat exchanger that generates hot water by heat exchange between a heating fluid and cold water, and guides the heating fluid from a heating fluid supply source to the heat exchanger. A heating fluid passage, a cold water passage that guides cold water from a water supply source to the heat exchanger, and a valve that opens when the pressure on the upstream side is greater than the pressure on the downstream side by a predetermined value or more. A pressure valve that is provided in the heating fluid passage and adjusts a supply amount of the heating fluid to the heat exchanger according to a differential pressure between the upstream side and the downstream side of the pressure valve, and the pressure valve An orifice provided in a bypass path of cold water that bypasses the control valve , and the control valve has a drive section that drives a valve body section that opens and closes the heating fluid path, upstream of the pressure valve via the upstream introduction path. Upstream introduction chamber where the cold water is introduced, and downstream A downstream introduction chamber into which cold water downstream of the pressure valve is introduced via an inlet passage; and a diaphragm that partitions the two introduction chambers; the upstream introduction passage, the downstream introduction passage, and the upstream introduction chamber and wherein the downstream inlet chamber and the bypass passage is formed, the upstream supply chamber and the downstream-side inlet chamber that are communicated by the orifice. According to this configuration, the differential pressure due to the cold water passing through the orifice is generated between the upstream introduction chamber and the downstream introduction chamber that are partitioned by the diaphragm and communicated by the orifice. Thus, the diaphragm can be deformed more effectively and with high responsiveness, and the responsiveness of the control valve is improved.

  According to the heating system of the present invention, when hot water is not used, the cold water does not flow in the cold water passage. As a result, no differential pressure is generated between the upstream side and the downstream side of the orifice. The regulating valve that operates in this manner is closed, and no heating fluid is supplied to the heat exchanger, so that the heating fluid is not wasted. On the other hand, when hot water is used, the cold water flows in the cold water passage toward the heat exchanger, and a differential pressure of the cold water is generated between the upstream side and the downstream side of the orifice. The control valve is opened, and heating fluid is supplied to the heat exchanger by the control valve. At this time, the opening degree of the control valve is adjusted by the magnitude of the differential pressure. Thus, the heating fluid is not consumed when hot water is not used, and the heating fluid is consumed only when hot water is used, and the supply amount of the heating fluid is controlled according to this differential pressure. Therefore, the heated fluid is used efficiently, and there is no delay in temperature detection, and hot water with a stable temperature is always obtained. Further, compared to providing a complicated mechanism for feedback control of the control valve based on the temperature of the hot water, the configuration is simple and inexpensive, and as a result, cost reduction can be achieved.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a system diagram showing a heating system 10A according to the first embodiment of the present invention. The heating system 10A includes a heat exchanger 11 that generates hot water M by heating cold water C that is a fluid to be heated with heat of a heating fluid S such as steam. The hot water M led out from the heat exchanger 11 is higher in temperature than hot water M1 from the hot water / mixing valve 23 described later, and will be referred to as “hot water M” below. As the heat exchanger 11, for example, a plate-type heat exchanger in which a plurality of plates are stacked and a passage of a heating fluid S and a passage of cold water C (not shown) are alternately arranged between the plates via the plates. It is preferable because of its small size and large heat exchange capacity.

  In addition, the heating system 10A includes a cold water passage 12 that guides cold water C supplied from an external water supply source WA to the heat exchanger 11, and a heating fluid S such as steam supplied from a heating fluid supply source VA. The heated fluid passage 13 that leads to the heat exchanger 11, the hot water outlet passage 14 that leads out the hot water M generated in the heat exchanger 11, and the heated fluid S that has passed through the heat exchanger 11 is condensed ( And a condensate discharge passage 15 for discharging as drain).

  The cold water passage 12 is provided with a partition wall 51 that extends the cold water passage 12 in a direction orthogonal to the flow direction of the cold water C, and partitions the cold water passage 12 into an upstream side and a downstream side. A pressure valve 20 that opens when the pressure on the upstream side exceeds the pressure on the downstream side by a predetermined value, a bypass path 21A for cold water C that bypasses the pressure valve 20, and an orifice that forms the bypass path 21A 16A. As shown in FIG. 2, the specific configuration is such that a partition wall 51 extending in a direction perpendicular to the flow direction of the cold water C is provided in the cold water pipe 50 constituting the cold water passage 12, and an orifice is provided in the partition wall 51. 16A and the valve port 22 of the pressure valve 20 are formed side by side. The orifice 16A is a small hole formed so as to restrict the passage flow rate of the cold water C flowing from the upstream side to the downstream side in the cold water pipe 50. In the pressure valve 20, a valve body 20 a that opens and closes the valve port 22 is pressed against the valve port 22 by the spring force of the compression coil spring 40. The compression coil spring 40 is interposed between the valve body 20 a and the spring receiving member 36, and the adjustment screw 41 abutting on the spring receiving member 36 is advanced and retracted toward the partition wall 51, whereby the compression coil spring 40 is springed. By changing the force, the valve opening pressure, that is, the pressure difference between the upstream side and the downstream side of the partition wall 51 when the valve body 20a opens the valve port 22 can be adjusted to a predetermined value.

  In the cold water pipe 50, an upstream introduction pipe 52 that forms the upstream introduction passage 18 is branched from a location on the upstream side across the partition wall 51, and downstream from a location on the downstream side of the partition wall 51. A downstream introduction pipe 53 that forms the side introduction passage 19 is branched. The leading ends of the upstream introduction pipe 52 and the downstream introduction pipe 53 are connected to the control valve 17 of FIG. The regulating valve 17 is disposed in the heating fluid passage 13 and the opening degree is adjusted according to the differential pressure between the upstream side and the downstream side of the pressure valve 20, whereby the heating fluid S is supplied to the heat exchanger 11. The amount is adjusted. Next, a specific structure of the control valve 17 will be described with reference to FIG.

  FIG. 3 shows a closed state of the control valve 17. In the control valve 17, a valve rod 26 arranged in a vertical direction is slidable in a casing 25 having a heated fluid passage 13 formed in the upper part. A drive portion 27 of the control valve 17 is provided at one end (lower end) of the valve rod 26, and the heating fluid passage 13 is opened and closed at the other end (upper end) of the valve rod 26. A valve body 28 made of a ball valve is disposed.

  The drive unit 27 receives the differential pressure between the upstream pressure and the downstream pressure of the orifice 16A and the pressure valve 20 to drive the valve rod 26 in the axial direction to move the valve body 28 in the axial direction. Accordingly, the opening of the valve is adjusted, and a disc-shaped receiving member 26a provided at the lower end of the valve stem 26, a diaphragm 30 fixed to the receiving member 26a in an overlapped state, and the diaphragm 30 And a downstream side introduction chamber 39 and an upstream side introduction chamber 38 which are partitioned vertically. Cold water C upstream of the orifice 16A in FIG. 2 is introduced into the upstream introduction chamber 38 through the upstream introduction path 18, and cold water C downstream of the orifice 16A is downstream in the downstream introduction chamber 39. It is introduced through the introduction path 19. The valve body portion 28 is pressed against the upper end of the valve stem 26 or the valve seat 25 a by receiving the spring force of the compression coil spring 29 interposed between the valve body portion 28 and the casing 25.

  An O-ring 42 is attached to a sliding surface portion between the valve stem 26 and the casing 25 to ensure airtightness and liquid tightness. Thus, the downstream side introduction passage 19 introduces the downstream side introduction chamber 39. It is considered that the chilled water C does not enter the heating fluid passage 13. As clearly shown in FIG. 1, in this embodiment, the case where the valve stem 26 and the valve body portion 28 are separated is illustrated, but the valve stem 26 and the valve body portion 28 are integrally formed. It may be formed.

  Further, as shown in FIG. 1, hot water M from the heat exchanger 11 is provided in a hot water outlet passage 14 that guides the hot water M led out from the heat exchanger 11 to a hot water outlet valve (caran) 24 serving as a hot water outlet. A hot water mixing valve 23 is provided for mixing the cold water C from the water supply source WA and adjusting the hot water M1 to be taken out to a desired temperature.

  Further, check valves 31 and 32 are provided at locations upstream of the connection point of the upstream side introduction passage 18 in the cold water passage 12 and the cold water bypass passage 37 that branches from the cold water passage 12 and reaches the hot water mixing valve 23, respectively. It is arranged. The condensate discharge passage 15 is provided with a steam trap 33 that traps the steam that is the heating fluid S and discharges only the condensate. In the cold water discharge passage 34 branched from the location between the pressure valve 20 and the heat exchanger 11 in the cold water passage 12, the heat in the heat exchanger 11 is removed when the extraction of the hot water M1 from the hot water supply valve 24 is stopped. A relief valve 35 is provided to prevent the pressure of the water M from rising too much.

  Next, the operation of the heating system 10A will be described. When the hot water M1 with the hot water supply valve 24 shown in FIG. 1 closed is not used, the cold water C does not flow through the cold water passage 12, so that the differential pressure between the upstream side and the downstream side across the orifice 16A in the cold water passage 12 becomes zero. In addition, the differential pressure between the upstream side introduction chamber 38 and the downstream side introduction chamber 39 is also zero. Therefore, as shown in FIG. 3, in the adjusting valve 17, the valve body portion 28 is pressed against the valve seat 25 a by the spring force of the compression coil spring 29 and held in the closed state, and the heating fluid passage 13 is closed and heated. Supply of the fluid S to the heat exchanger 11 shown in FIG. 1 is stopped. That is, in this heating system 10A, the stop of the flow of the cold water C in the cold water passage 12 due to the closing of the hot water supply valve 24 is mechanically detected based on the fact that the differential pressure between the upstream side and the downstream side of the orifice 16A becomes zero. Then, the control valve 17 is held in the closed state. Therefore, unlike the case where the control valve is always feedback controlled based on the temperature information of the hot water sensed by the temperature sensor as in the conventional heating system, unless the hot water supply valve 24 is opened, that is, unless the hot water M1 is used, Since the heating fluid S is not supplied to the heat exchanger 60, wasteful consumption of the heating fluid S can be prevented.

  When the hot water supply valve 24 is opened, the cold water C from the water supply source WA passes through the orifice 16A provided in the bypass passage 21A of the cold water passage 12 and flows into the heat exchanger 11. When the cold water C passes through the orifice 16A, the pressure near the downstream side of the orifice 16A in the cold water passage 12 is lower than the pressure near the upstream side due to the venturi effect. This differential pressure acts on the upstream side introduction chamber 38 and the downstream side introduction chamber 39 of the drive unit 27 of FIG. 3 via the upstream side introduction passage 18 and the downstream side introduction passage 19. The pressure in the downstream introduction chamber 39 also increases. Due to the differential pressure generated between the two introduction chambers 38 and 39, as shown in FIG. 4, the diaphragm 30 is deformed upward and pushes up the receiving member 26a. Accordingly, the valve stem 26 is driven upward in the axial direction. The As a result, the valve body 28 is moved upward against the spring force of the compression coil spring 29, the adjustment valve 17 is opened, and the heating fluid S is supplied to the heat exchanger 11 through the heating fluid passage 13. Is done.

  Therefore, it is generated by heat exchange between the heating fluid S guided to the heat exchanger 11 through the heating fluid passage 13 and the cold water C guided to the heat exchanger 11 through the orifice 16A, and the hot water mixing valve The hot water M 1 whose temperature has been adjusted at 23 is taken out from the hot water supply valve 24. Here, when the hot water supply valve 24 is opened to a small opening and a relatively small amount of hot water M1 is used, the pressure valve 20 is kept in the closed state by the spring force of the compression coil spring 40, The heat exchanger 11 is supplied with a small amount of cold water C that has passed through the orifice 16A. On the other hand, the control valve 17 has an opening degree corresponding to the differential pressure between the introduction chambers 38 and 39, and the supply amount of the heating fluid S to the heat exchanger 11 in FIG. Adjust to a small amount.

  On the other hand, when the hot water supply valve 24 is opened to a large opening for the purpose of using a relatively large amount of hot water M1, the flow rate of the cold water C passing through the orifice 16A increases, and the upstream side and the downstream side with respect to the partition wall 51. When the pressure difference between the pressure valve 20 and the pressure valve 20 becomes equal to or greater than a predetermined value that balances with the spring force of the compression coil spring 40 of the pressure valve 20, the pressure valve 20 opens and the valve port 22 having a diameter larger than that of the orifice 16A A large amount of cold water C that has passed through is supplied to the heat exchanger 11. At this time, a large differential pressure between the upstream side and the downstream side of the pressure valve 20 acts on the upstream side introduction chamber 38 and the downstream side introduction chamber 39, the regulating valve 17 is adjusted to a large opening, and the heating fluid S is supplied. The amount increases.

  As described above, in the heating system 10A, when the amount of the hot water M1 used is small, the cold water C passes only through the small-diameter orifice 16A and is caused by the differential pressure generated between the upstream side and the downstream side of the orifice 16A. The control valve 17 is operated with good responsiveness, and when the amount of hot water M1 used is large, the pressure valve 20 is opened, and a large amount of cold water C is supplied to the heat exchanger 11 through both the valve port 22 and the orifice 16A. Therefore, it is possible to achieve both the improvement of the responsiveness of the temperature adjustment of the hot water M by the control valve 17 and the securing of a large amount of hot water at the same time. In other words, when the orifice 16A is formed to have a small diameter in order to obtain a large differential pressure, a large usage amount of the hot water M1 cannot be ensured, while on the other hand, the orifice 16A has a large diameter to ensure a large usage amount of the hot water M1. In this case, since the differential pressure between the upstream side and the downstream side becomes small, it becomes difficult to control the temperature by the control valve 17, but this heating system 10A has the orifice 16A and the pressure valve 20 in parallel. By providing in the above, the above two conflicting problems are solved simultaneously.

  The heating system 10A of this embodiment replaces a complicated mechanism that feedback-controls the regulating valve based on the sensed hot water temperature as in a conventional heating device, and instead of the upstream side and the downstream side of each of the orifice 16A and the pressure valve 20. The amount of heating fluid S supplied to the heat exchanger 11 is adjusted by adjusting the opening of the control valve 17 according to the differential pressure generated between the heat exchanger 11 and the cost. . In addition, since there is no unexpected temperature change of hot water due to a delay in sensing the temperature of the hot water by the temperature sensor in the conventional heating system or a delay in the temperature change of the hot water relative to the change in the supply amount of the heated fluid, the hot and cold mixing valve 23 Through the process, the hot water M1 having a predetermined temperature can always be stably generated.

  FIG. 5 is a system diagram showing a heating system 10B according to the second embodiment of the present invention, in which the same or corresponding parts as those in FIG. The heating system 10B differs from that in FIG. 1 in that only the pressure valve 20 similar to that in FIG. 2 is provided in the cold water passage 12, while the orifice 16B is provided through the diaphragm 30 in the control valve 17. Only the configuration in which the upstream side introduction chamber 38 and the downstream side introduction chamber 39 are communicated with each other via the orifice 16B. Therefore, in this heating system 10B, the bypass path 21B that bypasses the pressure valve 20 includes the upstream introduction pipe 52 that forms the upstream introduction path 18, the downstream introduction pipe 53 that forms the downstream introduction path 19, and the upstream introduction. The chamber 38 and the downstream introduction chamber 39 are formed, and the orifice 16B is provided in the bypass path 21B.

  Specific configurations of the pressure valve 20 and the orifice 16B in FIG. 5 will be described. As shown in FIG. 6, only the pressure valve 20 is provided on the partition wall 51 provided in the cold water passage 12. On the other hand, as shown in FIG. 7, the screw member 43 passes through the insertion hole of the diaphragm 30 and is screwed and fixed to the screw hole of the receiving member 26 a, and is formed in the central portion of the screw member 43 in the axial direction. The orifice 16B is formed by a small-diameter through hole. A bush 44 is disposed on the outer periphery of the screw member 43 to prevent the diaphragm 30 from being crushed by fastening the screw member 43. In this embodiment, the orifice 16B is a small hole that penetrates the screw member 43 in the axial direction. However, as shown by a two-dot chain line, the upstream introduction chamber 38 and the downstream introduction chamber 39 are connected to the casing 25. You may make it provide the small hole formed so that it might connect.

  Since this heating system 10B basically operates in the same manner as in the first embodiment, only the operation different from that in the first embodiment will be described. First, the operation when the hot water M in FIG. 5 is not used is the same as that of the first embodiment. When the hot water supply valve 24 is opened, the cold water C from the water supply source WA is bypassed by the bypass passage 21 </ b> B including the upstream introduction passage 18, the upstream introduction chamber 38, the orifice 16 </ b> B, the downstream introduction chamber 39, and the downstream introduction passage 19. Flowing through. At this time, the pressure in the upstream introduction chamber 38 with respect to the orifice 16B becomes larger than the pressure in the downstream introduction chamber 38. Due to the differential pressure generated between the introduction chambers 38 and 39, the diaphragm 30 is shown in FIG. In the same manner as in the case of the first embodiment, it is deformed upward and pushes up the receiving member 26a of FIG. 7, so that the valve stem 26 is driven upward in the axial direction. As a result, the valve body portion 28 moves upward, the control valve 17 is opened, and the heating fluid S is supplied to the heat exchanger 11. When the differential pressure between the upstream side introduction chamber 38 and the downstream side introduction chamber 39 increases, the pressure valve 20 opens and a large amount of hot water M1 is secured.

  In the heating system 10B, in addition to obtaining the same effect as described in the first embodiment, the diaphragm 30 generally made of a material having low heat resistance such as rubber passes through the bypass path 21B. Since it is cooled by the flowing cold water C, thermal deterioration of the diaphragm 30 due to heat transfer from the heating fluid S is prevented, the valve operation of the control valve 17 is stabilized, and the life of the diaphragm 30 is extended.

It is a distribution diagram showing the heating system concerning a 1st embodiment of the present invention. It is a longitudinal cross-sectional view which shows the vicinity of the orifice and pressure valve in a heating system same as the above. It is a longitudinal cross-sectional view which shows the valve closing state of the control valve in a heating system same as the above. It is a longitudinal cross-sectional view which shows the valve opening state of a control valve same as the above. It is a systematic diagram which shows the heating system which concerns on 2nd Embodiment of this invention. It is a longitudinal cross-sectional view which shows the vicinity of the pressure valve in a heating system same as the above. It is a longitudinal cross-sectional view which shows the valve closing state of the control valve in a heating system same as the above. It is a systematic diagram of the conventional heating system.

Explanation of symbols

10A, 10B Heating system 11 Heat exchanger 12 Chilled water passage 13 Heating fluid passage 16A, 16B Orifice 17 Control valve 18 Upstream side introduction passage 19 Downstream side introduction passage 20 Pressure valve 21A, 21B Bypass passage 22 Valve port 27 Drive unit 28 Valve body Part 30 Diaphragm 38 Upstream side introduction chamber 39 Downstream side introduction chamber 51 Partition wall S Heating fluid C Cold water M Hot water (hot water)
M1 Hot water VA Heating fluid supply source WA Water supply source

Claims (2)

A heat exchanger that generates hot water by heat exchange between the heating fluid and cold water;
A heating fluid passage for directing the heating fluid from a heating fluid supply to the heat exchanger;
A cold water passage for guiding cold water from a water supply source to the heat exchanger;
A pressure valve provided in the cold water passage, and opened by the differential pressure when the upstream pressure becomes larger than the downstream pressure by a predetermined value; and
A regulating valve provided in the heating fluid passage for adjusting a supply amount of the heating fluid to the heat exchanger according to a differential pressure between the upstream side and the downstream side of the pressure valve;
An orifice provided in a bypass path of cold water that bypasses the pressure valve;
With
A valve port of the pressure valve and the orifice are formed in a partition wall provided in the cold water passage,
The pressure valve includes a valve body that opens and closes the valve port, a compression spring that presses the valve body against the valve port, and a heating screw that adjusts the valve opening pressure by changing the spring force of the compression spring. system. A heat exchanger that generates hot water by heat exchange between the heating fluid and cold water;
A heating fluid passage for directing the heating fluid from a heating fluid supply to the heat exchanger;
A cold water passage for guiding cold water from a water supply source to the heat exchanger;
A pressure valve that is provided in the cold water passage and opens when the pressure on the upstream side is larger than the pressure on the downstream side by a predetermined value or more;
A regulating valve provided in the heating fluid passage for adjusting a supply amount of the heating fluid to the heat exchanger according to a differential pressure between the upstream side and the downstream side of the pressure valve;
An orifice provided in a bypass path of cold water that bypasses the pressure valve;
With
In the control valve, a drive unit that drives a valve body unit that opens and closes the heating fluid passage includes an upstream introduction chamber into which cold water upstream of the pressure valve is introduced via an upstream introduction passage, and a downstream introduction A downstream side introduction chamber into which cold water on the downstream side of the pressure valve is introduced through a passage, and a diaphragm that partitions the both introduction chambers,
The bypass path is formed by the upstream introduction passage, the downstream introduction passage, the upstream introduction chamber, and the downstream introduction chamber,
A heating system in which the upstream introduction chamber and the downstream introduction chamber communicate with each other through the orifice.

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