JP2017198365A - Heat recovery system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To effectively suppress corrosion of a heat exchanger caused of a dissolved gas, in a heat recovery system incorporating the heat exchanger.SOLUTION: A heat recovery system 1 includes a heat exchanger 40 for manufacturing hot water W2 from cooling water W1 by implementing heat exchange between the cooling water W1 and high-temperature fluid (compressed air A1, lubricant H1), a cooling water line L5 in which the cooling water W1 to the heat exchanger 40 flows, a hot water line L6 in which the hot water W2 from the heat exchanger 40 flows, and a proportion control valve 23 disposed in the hot water line L6, and functioned as a pressure application portion for increasing a pressure inside of the heat exchanger 40 (second air cooler 21 and second oil cooler 22) by throttling a flow channel of the hot water line L6.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a heat recovery system for producing hot water from cooling water using a heat exchanger.

  2. Description of the Related Art Conventionally, a heat recovery system that performs heat exchange between a cooling water to be heated and a high-temperature fluid to produce hot water from the cooling water is known. For example, Patent Document 1 and Patent Document 2 disclose such a heat recovery system. The heat recovery systems disclosed in Patent Documents 1 and 2 are both for the purpose of recovering the compression heat generated in the oil supply type air compressor, exchanging heat between the lubricating oil and the cooling water, Hot water is produced from the cooling water by exchanging heat of the cooling water. In particular, Patent Document 1 discloses using a plate heat exchanger as a heat exchanger for heat recovery.

JP 2012-067673 A JP 2012-087664 A

  By the way, in the above-described plate heat exchanger, there is a multi-pass design that folds the flow of fluid along the heat transfer plate in order to make a large temperature difference between the fluids. In such a heat exchanger, bubbles tend to accumulate at locations where the flow of the cooling water turns (especially, locations where the flow from the upward flow to the downward flow), and the retention of the bubbles causes corrosion of the heat transfer plate, resulting in heat It may lead to puncture of the exchanger. Bubbles generated in the heat exchanger are those in which dissolved gas in the water is separated by heating the cooling water, and it has been considered inevitable as long as the solubility of the gas depends on the temperature. However, since the occurrence of repair / replacement costs due to heat exchanger punctures offsets the benefits of heat recovery, it has been desired to effectively suppress corrosion of the heat exchanger caused by dissolved gas.

  An object of this invention is to suppress effectively the corrosion of the heat exchanger resulting from dissolved gas in the heat recovery system incorporating the heat exchanger.

  The present invention includes a heat exchanger that produces heat from cooling water by performing heat exchange between cooling water and a high-temperature fluid, a cooling water line through which cooling water flows to the heat exchanger, and the heat exchanger. The present invention relates to a heat recovery system comprising: a hot water line through which hot water from circulates; and a pressure applying unit that is arranged in the hot water line and raises the internal pressure of the heat exchanger by restricting the flow path of the hot water line.

  The heat exchanger includes a plurality of heat exchangers connected in series, and the pressure applying unit is disposed in the hot water line through which hot water from the heat exchanger located on the most downstream side flows. preferable.

  The heat recovery system is disposed in the hot water line as the pressure application unit, a proportional control valve capable of adjusting the valve opening, a hot water temperature detection unit for detecting the temperature of hot water, and a hot water pressure for detecting the pressure of hot water A detection unit; and a control unit that controls the proportional control valve. The control unit is acquired by a dissolved gas concentration acquisition unit that acquires a dissolved gas concentration of cooling water, and the dissolved gas concentration acquisition unit. Based on the dissolved gas concentration and the detected temperature of the hot water temperature detecting unit, the target pressure calculating unit that calculates the target pressure of hot water that allows the dissolved gas concentration of hot water to exceed the dissolved gas concentration of cooling water, and the hot water pressure It is preferable to include a valve opening degree adjusting unit that adjusts the valve opening degree of the proportional control valve so that the detection pressure of the detection unit becomes the target pressure.

  The heat recovery system further includes a cooling water temperature detection unit that detects a temperature of the cooling water, and the dissolved gas concentration acquisition unit acquires the dissolved gas concentration based on a detection temperature of the cooling water temperature detection unit. It is preferable.

  It is preferable that the valve opening adjustment unit adjusts the valve opening of the proportional control valve so that the temperature detected by the hot water temperature detection unit is equal to or higher than a preset target temperature.

  The pressure applying unit includes an orifice arranged in the hot water line, and the orifice has a dissolved gas concentration of the hot water based on a preset dissolved water concentration of the cooling water and a target temperature of the hot water. It is preferable that the pressure loss is set so that the target pressure of hot water can exceed the gas concentration.

  According to the present invention, in a heat recovery system incorporating a heat exchanger, corrosion of the heat exchanger caused by dissolved gas can be effectively suppressed.

It is a figure showing typically composition of a heat recovery system concerning a 1st embodiment of the present invention. It is a block diagram which shows the electrical connection relation of the control part of 1st Embodiment, and the structure in connection with pressure provision. It is a flowchart which shows the flow of the pressure provision by the proportional control valve of 1st Embodiment. It is a figure which shows typically the structure of the heat recovery system which concerns on 2nd Embodiment of this invention.

<First Embodiment>
FIG. 1 is a diagram schematically showing a configuration of a heat recovery system 1 according to the first embodiment of the present invention. FIG. 2 is a block diagram illustrating an electrical connection relationship between the control unit 90 of the first embodiment and a configuration related to pressure application. The heat recovery system 1 according to this embodiment includes a compressor unit 10, a heat recovery unit 20, and a pump unit 30. The heat recovery system 1 manufactures hot water W2 from the cooling water W1 by recovering the compression heat generated in the compressor unit 10 by the heat recovery unit 20, and supplies the hot water W2 to the steam boiler 5 as boiler feed water. .

[Compressor unit 10]
As shown in FIG. 1, the compressor unit 10 includes a compressor 11, an oil separator 12, a first air cooler 13, a first oil cooler 14, and a control unit 90 as main components. These components are housed in a single housing and packaged.

  The compressor 11 has an air compression mechanism (not shown) such as a screw mechanism, a scroll mechanism, and a rotary mechanism. The compressor 11 drives the motor 15 connected to the drive shaft of the air compression mechanism, thereby sucking and adiabatically compressing outside air to generate compressed air A1. The compressor 11 of the present embodiment is an oil supply type, and cools the air compression mechanism, that is, removes the compression heat, by introducing the lubricating oil H1 into the air compression mechanism in the process of generating the compressed air A1. The motor 15 can employ various drive systems such as an electric drive motor and a steam drive motor.

  An air supply line L <b> 1 for sending compressed air A <b> 1 is connected to the discharge port of the compressor 11. In the air supply line L1, an oil separator 12, a first air cooler 13, and a dryer 16 are provided in order from the upstream side. The oil separator 12 is a separator for the lubricating oil H1 contained in the compressed air A1 discharged from the compressor 11. The oil separator 12 is connected to an oil feed line L2 for reintroducing the separated and recovered lubricating oil H1 into the air compression mechanism. In the oil feed line L2, a three-way valve 17 and a first oil cooler 14 are provided in order from the upstream side. The remaining port of the three-way valve 17 is connected to a bypass line L3 that bypasses the first oil cooler 14 and distributes the lubricating oil H1.

  The 1st air cooler 13 is a heat exchanger for cooling compressed air A1 (compressed air A1 after heat recovery with the 2nd air cooler 21 mentioned below) which distribute | circulates the air supply line L1. Moreover, the 1st oil cooler 14 is a heat exchanger for cooling the lubricating oil H1 (Lubricating oil H1 after heat-recovered with the 2nd oil cooler 22 mentioned later) which distribute | circulates the oil feeding line L2. As the 1st air cooler 13 and the 1st oil cooler 14, a shell and tube type heat exchanger is employable, for example. The first air cooler 13 and the first oil cooler 14 are connected to a water circulation line L4 for circulating and circulating the cooling water W3 supplied from the cooler 2 installed outside the compressor unit 10. The cooler 2 is a cooling tower, for example. On the water circulation line L4, it is preferable to arrange the first air cooler 13 in series upstream of the first oil cooler 14 from the viewpoint of increasing the cooling efficiency of the compressed air A1.

  The dryer 16 removes moisture from the compressed air A1 that flows through the air supply line L1 (compressed air A1 that has been heat-recovered by the second air cooler 21 described later and cooled by the first air cooler 13). The compressed air A1 dried by the dryer 16 is sent to a compressed air utilization device (not shown).

[Heat recovery unit 20]
As shown in FIG. 1, the heat recovery unit 20 includes a second air cooler 21, a second oil cooler 22, and a proportional control valve 23 as main components. These components are housed in a single housing and packaged. Since the heat recovery unit 20 is configured separately from the compressor unit 10, it can be retrofitted to the existing compressor unit 10.

  The heat recovery unit 20 incorporates a part of the air supply line L1 and the oil supply line L2 in the heat recovery unit 20 in order to recover heat of the compressed air A1 (high temperature fluid) and the lubricating oil H1 (high temperature fluid). . Specifically, the air supply line L1 extending from the oil separator 12 is drawn to the outside of the compressor unit 10 on the way to the first air cooler 13, and is disposed at an appropriate position inside the heat recovery unit 20. In addition, it is returned to the inside of the compressor unit 10 again. On the other hand, the oil feed line L2 extending from the oil separator 12 is drawn to the outside of the compressor unit 10 on the way to the first oil cooler 14, and after being disposed at an appropriate position inside the heat recovery unit 20, It is returned to the inside of the compressor unit 10 again. In the heat recovery unit 20, the air supply line L1 is provided with a second air cooler 21, and the oil supply line L2 is provided with a second oil cooler 22.

  The second air cooler 21 is a heat exchanger for recovering the compression heat of the compressed air A1 that flows through the air supply line L1 on the upstream side of the first air cooler 13. The second oil cooler 22 is a heat exchanger for recovering the compression heat of the lubricating oil H1 flowing through the oil feed line L2 on the upstream side of the first oil cooler 14. As the 2nd air cooler 21 and the 2nd oil cooler 22, a plate type heat exchanger is employable, for example. A cooling water line L5 for supplying the cooling water W1 is connected to the second air cooler 21 and the second oil cooler 22. The second oil cooler 22 is connected to a hot water line L6 for taking out the hot water W2. On the cooling water line L5, the second air cooler 21 is preferably arranged in series upstream of the second oil cooler 22 from the viewpoint of increasing the cooling efficiency of the compressed air A1.

  Here, each of the second air cooler 21 and the second oil cooler 22 performs heat exchange between the cooling water W1 and the high-temperature fluid (compressed air A1 or lubricating oil H1) to produce the hot water W2 from the cooling water W1. A heat exchanger 40 is provided. The cooling water line L5 is a conduit through which the cooling water W1 to the heat exchanger 40 flows, and the hot water line L6 is a conduit through which the hot water W2 from the heat exchanger 40 flows.

The warm water line L6 is provided with a warm water pressure sensor 24 (warm water pressure detector), a proportional control valve 23, and a warm water temperature sensor 25 (warm water temperature detector) in order from the second oil cooler 22 side. The hot water pressure sensor 24 detects the pressure of the hot water W2. Detected pressure _{P 2} of the hot water pressure sensor 24 is transmitted to the control unit 90. The hot water temperature sensor 25 detects the temperature of the hot water W2. The detected temperature _{T 2} of the hot water temperature sensor 25 is transmitted to the control unit 90. The proportional control valve 23 is disposed in the hot water line L6 through which the hot water W2 from the second oil cooler 22 located on the most downstream side of the heat exchanger 40 flows. The proportional control valve 23 functions as a flow rate adjusting unit for the hot water W2 by adjusting the valve opening. The proportional control valve 23 is electrically connected to the control unit 90 and is driven by a command signal from the control unit 90.

[Pump unit 30]
As shown in FIG. 1, the pump unit 30 includes a feed water pump 31 as a main component. These components are housed in a single housing and packaged. Since the pump unit 30 is configured separately from the compressor unit 10, it can be retrofitted to the existing compressor unit 10.

The upstream end of the cooling water line L5 is connected to the water supply line L7. The pump unit 30 is provided in this water supply line L7. Inside the pump unit 30, a cooling water temperature sensor 32 (cooling water temperature detection unit), a cooling water pressure sensor 33, and a water supply pump 31 are provided in the water supply line L7 in order from the upstream side. The cooling water temperature sensor 32 detects the temperature of the cooling water W <b> 1 before being pressurized by the feed water pump 31. The detected temperature T ₁ of the cooling water temperature sensor 32 is transmitted to the control unit 90. The cooling water pressure sensor 33 detects the pressure of the cooling water W <b> 1 before being pressurized by the feed water pump 31. The detected pressure P ₁ of the cooling water pressure sensor 33 is transmitted to the control unit 90. The feed water pump 31 pumps the cooling water W <b> 1 toward the second air cooler 21 located on the most upstream side in the heat exchanger 40. The water supply pump 31 is electrically connected to the control unit 90 and is driven by a command signal from the control unit 90.

  In the present embodiment, the feed water pump 31 that pumps the cooling water W <b> 1 is operated at a constant pressure by the control unit 90. Therefore, as will be described later, the proportional control valve 23 is also used as a pressure applying unit that increases the pressure inside the heat exchanger 40 (the second air cooler 21 and the second oil cooler 22) by narrowing the path of the hot water line L6. Function.

[Steam boiler 5 and incidental equipment]
The water supply line L7 on the downstream side of the pump unit 30 is provided with a hard water softening device 3 for softening the cooling water W1. The cooling water W <b> 1 is softened by the water softening device 3 and then sent to the heat recovery unit 20.

  The downstream end of the hot water line L6 is connected to the water supply tank 4. A water level sensor 41 is provided in the water supply tank 4. The detected water level of the water level sensor 41 is transmitted to the control unit 90. The steam boiler 5 and the feed water tank 4 are connected by a boiler feed water line L8. The boiler feed water line L8 is provided with a feed water pump 42 and a check valve 43. The hot water W2 stored in the water supply tank 4 is sent to the steam boiler 5 by driving the water supply pump 42. In the steam boiler 5, the hot water W2 sent through the boiler feed water line L8 is heated to generate steam. The generated steam is supplied to a steam use facility (not shown).

[Valve opening control of proportional control valve 23]
Next, the valve opening degree control of the proportional control valve 23 by the control unit 90 will be described. As shown in FIG. 2, the control unit 90 of the present embodiment includes a target temperature setting unit 91, a dissolved gas concentration acquisition unit 92, a target pressure calculation unit 93, and a valve opening degree adjustment unit 94.

The target temperature setting unit 91 sets a target temperature T ₀ (for example, 65 ° C.) of the hot water W2. The target temperature T ₀ may be set in advance, or set according to the load of the steam boiler 5 (the amount of water used), the water level in the feed water tank 4, and the operating state of the compressor unit 10. It may be.

The dissolved gas concentration acquisition unit 92 calculates the dissolved gas concentration of the cooling water W <b> 1 from the conditions on the upstream side of the heat exchanger 40. The dissolved gas concentration C in water and the gas solubility S with respect to water can be expressed as a function f of the temperature T and the pressure P of the cooling water W1 as shown in Expression (1). The dissolved gas concentration acquisition unit 92 assigns the detected temperature T ₁ of the cooling water temperature sensor 32 and the detected pressure P ₁ of the cooling water pressure sensor 33 to the equation (1), respectively, and the dissolved gas concentration C ₁ (mgO of the cooling water W1). ₂ / L).
C = S = f (T, P) (1)
In addition to the air, the gas for which the dissolved gas concentration is to be calculated can be exemplified by oxygen, which is a major component of air and has a high temperature dependency of solubility.

The target pressure calculation unit 93 uses the target pressure P ₀ of the hot water W2 that is a condition that the dissolved gas is not released from the hot water W2 flowing out of the heat exchanger 40 (that is, no bubbles are generated inside the heat exchanger 40) as cooling water. Calculation is based on the dissolved gas concentration C ₁ (mgO ₂ / L) of W ₁ and the detected temperature T ₂ of the hot water temperature sensor 28. Specifically, the condition that the dissolved gas is not released from the hot water W2 is that the gas solubility S ₂ (= dissolved gas concentration C ₂ ) of the hot water W2 is larger than the dissolved gas concentration C ₁ of the cooling water W1, that is, S _{the 2> C 1} is satisfied a condition. Here, by setting the safety factor α (for example, in the range of 1.05 to 1.20), the relationship of Expression (2) that satisfies the condition of S ₂ > C ₁ is established. Then, when the gas solubility S ₂ of the hot water W2 obtained by the equation (2) and the detected temperature T ₂ of the hot water temperature sensor 28 are respectively substituted into the equation (1), the dissolved gas concentration C ₂ of the hot water W2 is equal to that of the cooling water W1. A target pressure P _{0 of the} hot water W2 that can exceed the dissolved gas concentration C ₁ is calculated.
S ₂ = C ₁ × α (2)

The valve opening degree adjusting unit 94 adjusts the valve opening degree of the proportional control valve 23 according to the detected pressure P ₂ of the hot water pressure sensor 24. Specifically, the valve opening degree adjusting unit 94 adjusts the valve opening degree of the proportional control valve 23 so that the detected pressure P ₂ becomes the target pressure P _{0 using} the detected pressure P ₂ of the hot water pressure sensor 24 as a feedback value. PID control is performed.

The valve opening degree adjustment unit 94 adjusts the valve opening degree of the hot water temperature sensor 25 for detecting temperature T ₂ is the target temperature setting unit 91 the target temperature is set to T ₀ or more so as to proportional control valve 23. Specifically, the valve opening degree adjustment unit 94, after detecting the pressure P ₂ of the hot water pressure sensor 24 to adjust the valve opening of the proportional control valve 23 so that the target pressure P _0, the detection of the hot water temperature sensor 25 temperature T ₂ is in the case of more than the target temperature T ₀ holds conditioned degree of valve opening. On the other hand, the valve opening adjustment unit 94 adjusts the valve opening of the proportional control valve 23 so that the detected pressure P ₂ of the hot water pressure sensor 24 becomes the target pressure P _0, and then the detected temperature T ₂ of the hot water temperature sensor 25. PID but if less than the target temperature T ₀ is, for adjusting the detected temperature T ₂ of the hot water temperature sensor 28 as a feedback value, the valve opening of the proportional control valve 23 so that the detected temperature T ₂ becomes the target temperature T ₀ Take control. When increasing toward the temperature of the hot water W2 to the target temperature T _0, since thereby squeezing the valve opening of the proportional control valve 23 to reduce the flow rate of the hot water W2, it is also increased internal pressure of the heat exchanger 40 at the same time It will be. As a result, it is possible to produce hot water W2 having a desired temperature while suppressing the generation of bubbles inside the heat exchanger 40.

[Example of control flow by control unit 90]
Next, an example of the flow of control for maintaining the pressure inside the heat exchanger 40 above the target pressure P _0. FIG. 3 is a flowchart showing a flow of pressure application by the proportional control valve 23 of the first embodiment.

As shown in FIG. 3, the valve opening degree adjustment unit 94 acquires the target temperature T ₀ set by the target temperature setting unit 91 (step S101). Next, the valve opening degree adjustment unit 94 obtains the target pressure _{P 0} of the hot water W2 calculated by the target pressure calculating section 93 (step S102). As described above, the dissolved gas concentration acquisition unit 92 performs cooling water based on the temperature / pressure conditions on the cooling water W1 side (the detected temperature T ₁ of the cooling water temperature sensor 32 and the detected pressure P ₁ of the cooling water pressure sensor 33). calculating the dissolved gas concentration _{C 1} of W1. Further, the target pressure calculation unit 93 calculates the target pressure P ₀ of the hot water W2 based on the dissolved gas concentration C ₁ of the cooling water W1 and the temperature condition on the hot water W2 side (the detected temperature T ₂ of the hot water temperature sensor 25). To do.

Valve opening adjusting unit 94 obtains the detected pressure P ₂ of the hot water pressure sensor 24, so that the value reaches the target pressure P _0, performs a pressure feedback control for operating the valve opening of the proportional control valve 23 ( Step S103). In the pressure feedback control, the valve opening (operation amount) is sequentially calculated by the PID algorithm, and the internal pressure of the heat exchanger 40 is increased or decreased. At this time, in the heat exchanger 40, the amount of heat transfer from the high-temperature fluid is changed by increasing or decreasing the flow rate of the cooling water W1, and the temperature of the hot water W2 is changed.

  The valve opening degree adjusting unit 94 determines whether or not a predetermined time has elapsed since the execution of the pressure feedback control was started (step S104). If the predetermined time has not elapsed in step S104, the process returns to step S103 to continue the pressure feedback control. On the other hand, when a predetermined time has elapsed in the process of step S104, the process proceeds to the process of step S105.

Valve opening adjusting unit 94 obtains the detected temperature T ₂ of the hot water temperature sensor 25, determines whether this value is less than the target temperature T ₀ (step S105). Detection temperature _{T 2} in the process of step S105 is equal to or larger than the target temperature _{T 0,} and continues the pressure feedback control returns to step S103. That is, by narrowing the flow path of the hot water line L6, the internal pressure of the second air cooler 21 and the second oil cooler 22 constituting the heat exchanger 40 is increased, and the state where the dissolved gas is not released from the hot water W2 is maintained. On the other hand, the detected temperature _{T 2} in the processing of step S105 in the case of less than the target temperature _{T 0,} the process proceeds to step S106.

Valve opening adjusting unit 94 obtains the detected temperature T ₂ of the hot water temperature sensor 25, so that the value reaches the target temperature T _0, the temperature feedback control for operating the valve opening of the proportional control valve 23 ( Step S106). In the temperature feedback control, the valve opening (operation amount) is sequentially calculated by the PID algorithm, and the flow rate of the hot water W2 is reduced. That is, in the heat exchanger 40, while the internal pressure is increased, the temperature of the hot water W2 will be increased toward the target temperature T ₀ by being reduced the flow rate of the cooling water W1.

  The valve opening degree adjusting unit 94 determines whether or not a predetermined time has elapsed since the execution of the temperature feedback control was started (step S107). If the predetermined time has not elapsed in the process of step S107, the process returns to step S106 and the temperature feedback control is continued. On the other hand, if a predetermined time has elapsed in the process of step S107, the process proceeds to step S108.

Valve opening adjusting unit 94 obtains the detected pressure P ₂ of the hot water pressure sensor 24, determines whether this value is less than the target pressure P ₀ (step S108). Detected pressure _{P 2} in the process of step S108 is equal to or larger than the target pressure _{P 0,} and continues the temperature feedback control returns to step S106. That is, the state where the dissolved gas is not released from the hot water W2 inside the heat exchanger 40 is maintained. On the other hand, if the detected pressure P ₂ in the process of the step S108 is less than the target pressure P _0, since the dissolved gas from the hot water W2 in the heat exchanger 40 is ready to be released, the process returns to step S101, again step Pressure feedback control is executed in the process of S103.

When receiving a water supply stop signal during the processing from step S101 to step S108, the control unit 90 performs water supply stop control by, for example, an interrupt process. As the water supply stop signal, for example, a water level detection signal indicating that the water level sensor 41 has reached the upper limit set water level can be used. In the water supply stop control, the water supply pump 31 is stopped and the proportional control valve 23 is fully closed. On the other hand, the control part 90 will perform water supply start control, if a water supply start signal is received during a water supply stop. As the water supply start signal, for example, a water level detection signal indicating that the water level sensor 41 has reached the lower limit set water level can be used. In the water supply after the start step S102, the value of the target pressure P ₀ calculated for the most recent (e.g., water value of immediately before the stop) is preferably used. By using the most recently calculated value of the target pressure P ₀ , the internal pressure of the heat exchanger 40 can be quickly increased.

The heat recovery system 1 according to the first embodiment described above has the following effects.
That is, the heat recovery system 1 includes a heat exchanger 40 that produces heat water W2 from the cooling water W1 by exchanging heat between the cooling water W1 and the high-temperature fluid (compressed air A1, lubricating oil H1), and a heat exchanger. The cooling water line L5 through which the cooling water W1 flows to 40, the hot water line L6 through which the hot water W2 from the heat exchanger 40 flows, and the hot water line L6 are arranged, and the heat exchange is performed by narrowing the flow path of the hot water line L6. And a proportional control valve 23 as a pressure applying unit for increasing the pressure inside the container 40 (second air cooler 21 and second oil cooler 22).

  Thus, the internal pressure of the heat exchanger 40 (second air cooler 21 and second oil cooler 22) is increased by narrowing the flow path downstream of the heat exchanger 40 and increasing the pressure loss by the proportional control valve 23. Thus, the gas solubility S of the water flowing through the heat exchanger 40 can be lowered. Therefore, the situation where the dissolved gas in the water is separated by the heating of the cooling water W1 and bubbles are effectively suppressed, and the corrosion of the heat exchanger 40 due to the dissolved gas can be prevented. It is not necessary to change the internal structure of the heat exchanger 40, and application to existing facilities is easy.

  Further, the heat exchanger 40 of the present embodiment includes a second air cooler 21 and a second oil cooler 22 connected in series, and the proportional control valve 23 is hot water from the second oil cooler 22 located on the most downstream side. It arrange | positions at the hot water line L6 through which W2 distribute | circulates.

  As a result, the proportional control valve 23 as a pressure applying portion is arranged downstream of the second oil cooler 22 located on the most downstream side, so that not only the internal pressure of the second oil cooler 22 is raised. The internal pressure of the second air cooler 21 on the upstream side of the second oil cooler 22 can be increased. That is, by disposing one proportional control valve 23 as a pressure applying unit, it is possible to prevent corrosion of the internal piping caused by the dissolved gas in the second air cooler 21 and the second oil cooler 22 (a plurality of heat exchangers).

Further, the heat recovery system 1 of the present embodiment includes a proportional control valve 23 that can adjust the valve opening, a hot water temperature sensor 25 that detects the temperature of the hot water W2, and a hot water pressure sensor 24 that detects the pressure of the hot water W2. And a control unit 90 for controlling the proportional control valve 23 as a pressure applying unit. Control unit 90, the dissolved gas concentration C _{1 (gas} solubility S ₁₎ dissolved gas concentration acquisition unit 92 that acquires the cooling water W1, and the dissolved gas concentration C ₁ obtained at dissolved gas concentration acquisition unit _92, and the hot water temperature based on the detected temperature _{T 2} of the sensor 25, calculates a target pressure _{P 0} of the hot water W2 dissolved gas concentration _{C 2} (the gas solubility _{S 2)} it is capable of exceeding the dissolved gas concentration _{C 1} of the cooling water W1 heated W2 with a target pressure calculating section 93, a valve opening degree adjustment unit 94 which detects the pressure P ₂ of the hot water pressure sensor 24 to adjust the valve opening of the proportional control valve 23 so that the target pressure P _0, the.

Thereby, since the pressure inside the heat exchanger 40 is maintained so as to be equal to or higher than the target pressure P ₀ set as a condition that the dissolved gas is not released from the hot water W2, bubbles are generated inside the heat exchanger 40. It can suppress more reliably. In this embodiment, since the proportional control valve 23 used for the feedback control of the tapping temperature is used, it can be easily applied to a conventional heat recovery system including a device that performs the temperature feedback control.

The heat recovery system 1 further includes a cooling water temperature sensor 32 that detects the temperature of the cooling water W1, and the dissolved gas concentration acquisition unit 92 acquires the dissolved gas concentration C ₁ based on the detected temperature of the cooling water temperature sensor 32. To do.

Thus, the detected temperature T dissolved gas concentration C ₁ on the basis of the _first cooling water temperature sensor 32 is calculated, it is possible to reflect the actual temperature of the cooling water W1 in the calculation of the target pressure P _0, the target pressure it is possible to perform a heat exchanger 40 inside the pressure increase control based on P ₀ more accurately.

Valve opening adjusting unit 94 adjusts the valve opening of the proportional control valve 23 so that the above target temperature T ₀ which is detected temperature T ₂ is set in advance of the hot water temperature sensor 25.

  Thereby, warm water W2 of desired temperature can be manufactured, maintaining the state from which dissolved gas is not liberated from warm water W2.

  The configuration of the heat recovery system 1 of the first embodiment described above can be changed as appropriate according to circumstances. For example, in the first embodiment, the dissolved gas concentration is indirectly calculated using a temperature sensor or a pressure sensor, but the cooling water W1 or hot water W2 or directly using a dissolved oxygen concentration sensor (DO meter). It is good also as a structure which measures and acquires both these dissolved oxygen concentrations.

In the first embodiment, the detection is pressure based on P ₁ calculates the dissolved gas concentration, dissolved gas concentration regards the pressure of the cooling water W1 and atmospheric pressure (1 atm) of the cooling water pressure sensor 33 It is good also as a structure to calculate. For example, the cooling water W1 is received in a tank by a water source (not shown) to which the water supply line L7 is connected, and the pipe connected to the tank is a sealed pipe that can be regarded as a saturated concentration under atmospheric pressure. The fixed value according to the season and time the temperature of the cooling water W1 (e.g., room temperature 20 ° C.) may be configured to calculate the dissolved gas concentration C ₁ as. Alternatively, the target pressure P ₀ may be calculated with the dissolved gas concentration C ₁ as a constant value (for example, a dissolved oxygen concentration of 8.84 mg / L under the conditions of 1 atm and 20 ° C.). Moreover, since the pressure loss in the heat exchanger 40 (the second air cooler 21 and the second oil cooler 22) is small, the secondary pressure of the heat exchanger 40 can be regarded as the primary pressure. By utilizing this, a pressure sensor is disposed between the feed water pump 31 and the heat exchanger 40 in the cooling water line L5, and the detected pressure of this pressure sensor is regarded as the pressure of the hot water W2, and the target pressure P ₀ and the detected pressure P _2. It is good also as a structure which compares. Further, the control flow described with reference to FIG. 3 is an example, and the control method can be appropriately changed according to circumstances, such as changing the processing order or performing parallel processing.

Second Embodiment
In the first embodiment, the present invention has been described by taking as an example the configuration using the proportional control valve 23 as the pressure applying unit. However, it is possible to use a pressure control unit other than the proportional control valve 23. Next, 2nd Embodiment is described as an example of the heat recovery system using things other than the proportional control valve 23 for a pressure provision part. FIG. 4 is a diagram schematically showing the configuration of the heat recovery system 201 according to the second embodiment of the present invention. Note that in the second embodiment, the same components as those in the first embodiment may be denoted by the same reference numerals, and the description thereof may be omitted.

  The heat recovery system 201 shown in FIG. 4 is different from the first embodiment in that an orifice 223 is used instead of the proportional control valve 23 in which the pressure inside the heat exchanger 40 is increased in the first embodiment. Further, the cooling water temperature sensor 32 and the cooling water pressure sensor 33 are omitted from the configuration of the first embodiment.

The orifice 223 is a pressure applying unit and is disposed in the hot water line L6. The orifice 223 of the present embodiment is disposed on the downstream side of the second oil cooler 22 located on the most downstream side of the heat exchanger 40. The orifice 223 of the second embodiment is configured to increase the internal pressure of the heat exchanger 40 (second air cooler 21 and second oil cooler 22) by narrowing the flow path of the hot water line L6. Pressure loss is set to the orifice 223, device configuration of the heat recovery system 201, is configured to impart a target pressure P ₀ with respect to hot water W2 based on the use conditions such as pipeline construction and use environment.

That is, the heat recovery system 201 of the second embodiment includes an orifice 223 disposed in the hot water line L6 as a pressure applying unit, and the orifice 223 has a preset dissolved gas concentration C ₁ (gas solubility S) of the cooling water W1. _1), and on the basis of the target temperature _{T 0} of hot water W2, the target pressure P of the hot water W2 dissolved gas concentration _{C 2} of the hot water W2 which (gas solubility _{S 2)} is capable of exceeding the dissolved gas concentration _{C 1} of the cooling water W1 _The pressure loss is set to be _zero .

Thereby, the pressure inside the heat exchanger 40 is maintained by the orifice 223 in which the pressure loss is set based on the use conditions or the like so that the dissolved gas is not released from the hot water W2 so as to be equal to or higher than the target pressure P _0. Therefore, corrosion of the heat exchanger due to dissolved gas can be reliably prevented. Since corrosion prevention can be realized without changing the configuration of the heat exchanger 40, it can be easily applied to conventional equipment, and the heat recovery system is stable by suppressing the occurrence of repair and replacement costs due to puncture of the heat exchanger. Operation can be realized.

  As mentioned above, although preferable embodiment of this invention was described, this invention is not restrict | limited to the above-mentioned embodiment, It can change suitably.

  In the second embodiment, the orifice 223 is used as the pressure applying unit. However, instead of the orifice 223, the hot water line L6 is increased in piping distance or the diameter of the flow path is reduced to cause pressure loss. The pressure inside the heat exchanger 40 may be increased.

  Moreover, in the said 1st Embodiment and 2nd Embodiment, although demonstrated using as an example what uses compressed air and lubricating oil as a high-temperature fluid of the object which collect | recovers heat, it is not necessarily limited to this structure and is independent. It can be changed to a configuration in which heat is recovered by a heat exchanger or a configuration in which a gas medium other than compressed air or lubricating oil is used as a high-temperature fluid. Thus, the present invention can be applied to various heat recovery systems that use heat exchangers that produce heat from cooling water by exchanging heat between the cooling water and a high-temperature fluid.

1 Heat recovery system 21 Second air cooler (heat exchanger)
22 Second oil cooler (heat exchanger)
23 Proportional control valve (pressure applying part)
24 Hot water pressure sensor (hot water pressure detector)
25 Hot water temperature sensor (hot water temperature detector)
32 Cooling water temperature sensor (cooling water temperature detector)
33 Cooling water pressure sensor (cooling water temperature detector)
DESCRIPTION OF SYMBOLS 40 Heat exchanger 90 Control part 91 Target temperature setting part 92 Dissolved gas concentration acquisition part 93 Target pressure calculation part 94 Valve opening degree adjustment part 201 Heat recovery system 223 Orifice (pressure provision part)
L5 Cooling water line L6 Hot water line

Claims (6)

A heat exchanger that exchanges heat between the cooling water and the high-temperature fluid to produce hot water from the cooling water;
A cooling water line through which cooling water to the heat exchanger flows;
A hot water line through which hot water from the heat exchanger flows;
A pressure applying unit that is disposed in the hot water line and raises the pressure inside the heat exchanger by narrowing a flow path of the hot water line;
A heat recovery system comprising. The heat exchanger comprises a plurality of heat exchangers connected in series,
The heat recovery system according to claim 1, wherein the pressure applying unit is disposed in the hot water line through which hot water from the heat exchanger located on the most downstream side flows. A proportional control valve that is arranged in the hot water line as the pressure applying unit and is capable of adjusting a valve opening;
A hot water temperature detector for detecting the temperature of the hot water;
A hot water pressure detector for detecting the pressure of hot water;
A control unit for controlling the proportional control valve,
The controller is
A dissolved gas concentration acquisition unit for acquiring a dissolved gas concentration of cooling water;
Based on the dissolved gas concentration acquired by the dissolved gas concentration acquisition unit and the detected temperature of the hot water temperature detection unit, the target pressure of hot water that allows the dissolved gas concentration of hot water to exceed the dissolved gas concentration of cooling water is calculated. A target pressure calculation unit for
The heat recovery system according to claim 1, further comprising: a valve opening degree adjusting unit that adjusts a valve opening degree of the proportional control valve so that a detected pressure of the hot water pressure detecting unit becomes the target pressure. A cooling water temperature detector for detecting the temperature of the cooling water;
The dissolved gas concentration acquisition unit
The heat recovery system according to claim 3, wherein the dissolved gas concentration is acquired based on a temperature detected by the cooling water temperature detection unit. The valve opening adjuster is
The heat recovery system according to claim 3 or 4, wherein the opening degree of the proportional control valve is adjusted so that a temperature detected by the hot water temperature detection unit is equal to or higher than a preset target temperature. Comprising an orifice arranged in the hot water line as the pressure applying part,
The orifice is
Based on the preset dissolved water concentration of cooling water and the target temperature of hot water, the pressure loss is set so that the dissolved gas concentration of hot water becomes the target pressure of hot water that can exceed the dissolved gas concentration of cooling water. The heat recovery system according to claim 1 or 2.

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