Patent Application
20250155163
The present application relates to the technical field of heat exchange, and in particular to a heat exchange system, a water heater, and a method for controlling the water heater.
Most conventional water heaters have a bypass tube connected between the cold water inlet tube and the hot water outlet tube of the heat exchanger. The cold water in the cold water inlet tube is transported to the hot water outlet tube through the bypass tube to mix with the hot water in the hot water outlet tube to achieve the bypass water mixing function.
In order to more clearly illustrate the technical solutions in the embodiments of the present application or in the related art, drawings used in the embodiments or in the related art will be briefly described below. Obviously, the drawings in the following description are only some embodiments of the present application. It will be apparent to those skilled in the art that other figures can be obtained according to the structures shown in the drawings without creative work.
The realization of the purposes, functional features and advantages of the present application will be further explained with reference to the accompanying drawings in combination with the embodiments.
It should be noted that any directional instructions in the embodiments of the present application (such as up, down, left, right, front, rear, etc.) are used merely to explain the relative positional relationships and movements of the components under a specific posture (as shown in the drawings). If the specific posture changes, the directional instructions will correspondingly change as well.
Additionally, the descriptions of “first” “second” and similar terms in the present application are only for illustrative purposes and should not be understood as indicating or implying relative importance, nor do they imply a specific number of technical features. Therefore, a feature defined as “first” or “second” may explicitly or implicitly include at least one such feature. In some embodiments, the term “and/or” in the full text includes three options. Taking “A and/or B” as an example, it includes option A, or option B, or an option that both A and B satisfy. In addition, the technical solutions in the various embodiments can be combined with each other, provided that those skilled in the art can implement such combinations.
Conventional water heaters, especially those with coilless heat exchangers, often suffer from low thermal efficiency.
The present application provides a heat exchange system 10.
The heat exchange system can be applied to a water heater or other hot water system that needs to realize a bypass water mixing function. The following mainly uses the application of the heat exchange system in a water heater as an example for explanation. The water heater is specifically described by taking a gas water heater with a coilless heat exchanger 100 as an example.
The water heater includes a heat exchange system 10, a burner 21 and a fan 22. The heat exchange system 10 includes a heat exchange tube 140, a heat exchange plate 150 sleeved on the outer periphery of the heat exchange tube 140, the water inlet end of the heat exchange tube 140 is connected to the water inlet tube, and the water outlet end of the heat exchange tube 140 is connected to the water outlet tube. The burner 21 is provided below the heat exchange system 10. For a strong drum type gas water heater, the fan 22 is provided below the burner 21; for a strong extraction type gas water heater, the fan 22 is provided above the heat exchange system 10. When the water heater is working, the fan 22 starts, and the mixture of gas and air enters the burner 21 for combustion. The cold water in the external water supply system can enter the heat exchange tube 140 of the heat exchange system 10 through the water inlet tube. The high-temperature flue gas generated by the burner 21 flows upward to exchange heat with the heat exchange system 10 to heat the water in the heat exchange tube 140. The heated hot water can be output to the user end through the water outlet tube to provide hot water for the user.
Conventional water heaters usually connect a long bypass tube between the water inlet tube and the water outlet tube of the heat exchanger to achieve the bypass water mixing function. When the water heater is working, part of the cold water in the water inlet tube will enter the water outlet tube through the bypass tube to achieve the mixing of cold water and hot water. According to research, water heaters with such a bypass structure have at least the following defects.
Firstly, when the water heater is burning normally, the flow path in the bypass tube always remains in a communicated-state, so the highest temperature in the heat exchange tube is higher than the set temperature of the water heater. The set temperature is reached only after the cold water is mixed. In order to solve the temperature rise when the water is shut off, a large bypass ratio is usually required. If the set temperature of the water heater is 65° C., the actual temperature in the heat exchange tube will be as high as 75° C., which will produce serious vaporization noise, affect the user experience, and shorten the life of the heat exchanger.
Secondly, if the bypass ratio is too large, serious vaporization noise will be generated and the thermal efficiency of the heat exchanger will be reduced. Generally, the bypass ratio cannot be set too high. Since the coilless heat exchanger lacks coil water cooling, the water-off temperature rise is high, and a large bypass ratio may be required to reduce the water-off temperature rise, which further causes the adverse effects of high vaporization noise and low thermal efficiency.
Lastly, since the bypass tube is always open and the bypass ratio is fixed, if the bypass ratio is too large, it may be easy to cause large undershoot during start-stop in winter; and if the bypass ratio is too small, it may easily cause the outlet water temperature to be too high or the risk of condensation in summer.
The water-off temperature rise or the overshoot during start-stop refers to the fact that when the water heater is working normally, the fin tube (that is, the heat exchange tube with heat exchange plates) is in a high temperature state. When the water heater stops working, the heat on the fin tube will be quickly transferred to the stopped water, causing the water temperature to rise. When the water heater is restarted, a section of high-temperature water will flow out, which may scald the user in severe cases.
The water-off temperature drop/undershoot during start-stop refers to the fact that after the water heater stops working, it needs to be pre-cleaned and ignited when it is restarted. At this time, a section of cold water will flow out of the heat exchanger before it can be heated to the set temperature.
The start-stop constant temperature process refers to the fact that there is a part of normal temperature hot water in the user's hot water pipeline. After the burner is restarted, it will first experience a normal water temperature, then experience an overshoot (water-off temperature rise) and an undershoot (water-off temperature drop), and finally reach the normal set temperature.
The bypass ratio refers to the ratio of the bypass flow to the main line flow. The bypass cold water flow plus the main line flow equals the total flow.
Based on this, the present application provides a heat exchange system 10, which has a good bypass water mixing function and can effectively improve the problem of low thermal efficiency of the water heater.
As shown in
It can be understood that the first tube 211 is provided with a first water inlet port and a first water outlet port at both ends, and the water inlet tube section 110 is connected to the first water outlet port. The second tube 212 is provided with a second water inlet port and a second water outlet port at both ends respectively, and the water outlet tube section 120 is connected to the second water inlet port. Cold water enters the first tube 211 through the first water inlet port, and then flows into the water inlet tube section 110 from the first water outlet port. The cold water in the water inlet tube section 110 flows into the heat exchange tube 140 of the heat exchanger 100 for heat exchange. After the heat exchange, the hot water enters the second tube 212 from the second water inlet port through the water outlet tube section 120, and then is output from the second water outlet port.
In some embodiments, the water inlet tube section 110 is detachably plugged into the first tube 211, the water outlet tube section 120 is detachably plugged into the second tube 212, and the assembly is performed by plugging and matching, which facilitates the installation and removal of the flow valve 200 and the heat exchanger 100. The controller 220 can be provided at the peripheral wall of the bypass tube 213 and located between the first tube 211 and the second tube 212. In this way, the cavity area constructed by the valve body 210 can be fully utilized to accommodate the controller 220, thereby improving the space utilization rate and facilitating the reduction of the overall volume of the flow valve 200.
In some embodiments, the water inlet tube section 110 and the water outlet tube section 120 of the heat exchanger 100 can be provided at different sides of the heat exchanger 100. The water inlet tube section 110 and the water outlet tube section 120 of the heat exchanger 100 can also be provided at the same side of the heat exchanger 100. According to the direction of the heat exchange channel inside the heat exchanger 100, the water inlet tube section 110 and the water outlet tube section 120 can be provided at the same side of the length direction (such as the left-right direction) of the heat exchanger 100. The water inlet tube section 110 and the water outlet tube section 120 can also be provided at the same side of the width direction (such as the front-to-rear direction) of the heat exchanger 100. In addition, the water inlet tube section 110 and the water outlet tube section 120 can also be provided at the same side of the height direction (such as the up-down direction) of the heat exchanger 100, which is not limited here. When the water inlet tube section 110 and the water outlet tube section 120 are provided at the same side of the heat exchanger 100, the arrangement positions of the water inlet tube section 110 and the water outlet tube section 120 are more concentrated, so that the flow valve 200 is connected to the water inlet tube section 110 and the water outlet tube section 120 at the same time. The flow valve 200 can be provided at one side of the heat exchanger 100, specifically, the flow valve 200 can be provided at the side of the heat exchanger 100 where the water inlet tube section 110 and the water outlet tube section 120 are provided, that is, the flow valve 200, the water inlet tube section 110 and the water outlet tube section 120 are all provided at the same side of the heat exchanger 100. The flow valve 200 can also be provided at the side of the heat exchanger 100 adjacent to the water inlet tube section 110 and the water outlet tube section 120.
In some embodiments, the valve body 210 plays a structural supporting role for the installation of the controller 220, and the valve body 210 can be made of metal pieces or high temperature resistant plastic pieces. When the heat exchange system 10 is working, cold water is transported to the heat exchanger 100 through the first tube 211 and the water inlet tube section 110 for heat exchange, and the hot water in the heat exchanger 100 is output to the second tube 212 through the water outlet tube section 120. At the same time, the cold water in the first tube 211 can also be transported to the second tube 212 through the bypass tube 213, thereby realizing the bypass water mixing function. It should be noted that the controller 220 controls the water flow rate of the bypass tube 213, which should be understood as the water flow rate flowing through the bypass tube 213 can be changed to a certain extent under the control of the controller 220. The change in water flow here can refer to a transition between no flow and flow, or to a variation between high flow and low flow when flow is present. The controller 220 includes but is not limited to the use of solenoid valves, proportional valves, etc. The controller 220 of the flow valve 200 can be electrically connected to the control system of the water heater in a wired or wireless manner. The control system sends corresponding control instructions to the controller 220 according to the working state of the water heater, and then the water flow rate of the bypass tube 213 can be controlled through the controller 220.
The cold water inlet tube and the hot water outlet tube of the conventional water heater are placed on both sides of the width direction of the water heater, and the distance between the two is large. Usually, a long bypass pipe needs to be connected. It is difficult to connect and install with the control valve in actual production, the cost is high, and the sealing performance is difficult to ensure. As shown in
As shown in
When the water heater is working normally, the controller 220 controls the closing of the bypass tube 213. At this time, the highest temperature in the heat exchange tube 140 of the heat exchange system 10 is the set temperature of the water heater. In this way, the risk of vaporization noise can be greatly reduced, and the thermal efficiency of the heat exchange system 10 will not be affected. The service life of the heat exchange system 10 can also be extended.
After the water supply to the water heater is stopped, the controller 220 controls the bypass tube 213 to be opened, and can close the bypass tube 213 within a few seconds of startup according to the actual working conditions. At this time, part of the cold water in the first tube 211 is transported to the second tube 212 via the bypass tube 213, and the cold water is mixed with the high-temperature water in the second tube 212, which can effectively reduce the temperature rise when the water supply is stopped; because part of the cold water is diverted from the bypass tube 213, the water flow rate transported by the first tube 211 toward the water inlet tube section 110 is reduced, thereby reducing the undershoot at startup.
In addition, it is also possible to determine whether to open the bypass during normal combustion based on actual working conditions. For example, in winter, when the temperature difference between the inlet and outlet water is large and needs to be quickly heated to the set temperature, the controller 220 controls the bypass tube 213 to close. This not only improves the heating speed but also ensures that it can be heated to the set temperature. When the water is stopped and restarted, the bypass time can be reduced, thereby reducing the undershoot. When a low-temperature bath is needed in summer, the controller 220 controls the bypass tube 213 to open. At this time, the minimum temperature rise of the water heater can be reduced to prevent the water temperature from being too hot during bathing, and the water temperature in the heat exchange tube 140 can be increased, thereby increasing the flue gas temperature and avoiding the risk of condensation water.
The bypass tube 213 is short, and the water flow can quickly pass through the bypass tube 213, which can ensure that the water heater has a faster bypass response speed and a more accurate bypass ratio, thereby effectively improving the low thermal efficiency of conventional water heaters. In this solution, the bypass flow is the water flow entering the bypass tube 213 through the first tube 211, and the main line flow is the water flow entering the water inlet tube section 110 through the first tube 211. In other words, the bypass ratio of the flow valve 200 is the ratio of the water flow entering the bypass tube 213 through the first tube 211 to the water flow entering the water inlet tube section 110 through the first tube 211.
The heat exchange system 10 of the present application includes a heat exchanger 100 and a flow valve 200. The heat exchanger 100 is provided with a water inlet tube section 110 and a water outlet tube section 120. The flow valve 200 is provided at the side of the heat exchanger 100. The flow valve 200 includes a valve body 210 and a controller 220. The valve body 210 includes a first tube 211 communicated with the water inlet tube section 110, a second tube 212 communicated with the water outlet tube section 120, and a bypass tube 213 communicating the first tube 211 and the second tube 212. The controller 220 is used to control the water flow rate of the bypass tube 213. With such a configuration, when the heat exchange system 10 is applied to a water heater, the first tube 211 can be used as a water inlet tube communicated with the cold water input tube 23 of the water heater, the second tube 212 can be used as a water outlet tube communicated with the hot water output tube 24 of the water heater, and the cold water in the first tube 211 can be transported to the second tube 212 through the bypass tube 213 to mix with the hot water in the second tube 212, thereby realizing the bypass water mixing function. The controller 220 is used to be electrically connected to the control system of the water heater, and the control system sends corresponding control instructions to the controller 220 according to the working state of the water heater, and then the water flow rate of the bypass tube 213 can be controlled by the controller 220, so that the bypass water mixing amount of the water heater can be adjusted according to the actual working conditions, thereby effectively improving the problem of low thermal efficiency of conventional water heaters.
In some embodiments, the bypass ratio of the flow valve 200 ranges from 40% to 70%, and the bypass ratio is the ratio of the water flow entering the bypass tube 213 through the first tube 211 to the water flow entering the water inlet tube section 110 through the first tube 211.
It is understandable that when the bypass ratio is too large, during the process of starting the water heater to heat, too much water flows from the bypass tube 213 into the second tube 212, which will produce serious vaporization noise, reduce the thermal efficiency of the heat exchanger 100, affect the user experience, and affect the life of the heat exchanger 100. When the bypass ratio is too small, the amount of water flowing from the bypass tube 213 into the second tube 212 is too small to neutralize the high-temperature water in the second tube 212. This solution can effectively improve the problems of start-stop constant temperature difference, high vaporization noise, low thermal efficiency, etc. of conventional water heaters by limiting the range of the bypass ratio of the flow valve 200.
In some embodiments, the first tube 211 is connected to the cold water input tube 23 of the water heater, and the second tube 212 is connected to the hot water output tube 24 of the water heater. The inner diameter of the first tube 211 is larger than the inner diameter of the bypass tube 213, so that most of the cold water in the first tube 211 can be transported to the water inlet tube section 110, and a small part of the cold water is diverted to the bypass tube 213, which can avoid the water transported to the heat exchanger 100 being too little and directly vaporized, affecting the efficiency of preparing hot water, and also avoid the water transported from the bypass tube 213 to the second tube 212 being too much, causing the hot water in the second tube 212 to cool too much. In addition, by designing the inner diameter of the first tube 211 and the inner diameter of the bypass tube 213, it is ensured that the bypass ratio is in the range of 40% to 70%, ensuring that a good bypass water mixing effect can be achieved. The value of the bypass ratio can be 40%, 50%, 60%, 70%, etc., which is not specifically limited here. By limiting the bypass ratio to 40%˜70%, compared with a bypass ratio value less than 40% or greater than 70%, this solution can reduce the start-stop temperature fluctuation range (the fluctuation range of temperature overshoot and temperature undershoot when the water heater is restarted), and reduce the constant temperature waiting time (the duration of temperature overshoot and temperature undershoot when the water heater is restarted), thereby achieving better start-stop constant temperature control of the water outlet temperature of the water heater.
In addition, in order to prevent the bypass water volume from being too large and causing a large impact and temperature drop on the hot water in the second tube 212, the inner diameter of the second tube 212 is larger than the inner diameter of the bypass tube 213.
In some embodiments, the controller 220 is provided at the bypass tube 213, and the controller 220 is used to control the water flow rate of the bypass tube 213 according to a preset bypass time and the bypass ratio, and the bypass time ranges from 2 seconds to 4 seconds.
It is understandable that when the bypass time is too long, the water temperature in the heat exchange tube 140 has exceeded the set temperature of the water heater. When the controller 220 controls to close the bypass tube 213, the high-temperature water flowing into the second tube 212 from the heat exchange tube 140 cannot be mixed with the bypassed cold water, which easily causes water outage and overshoot, affecting the user to use the water heater. When the bypass time is too short, the high-temperature water flowing into the second tube 212 from the heat exchange tube 140 stops bypassing before it is completely mixed with the bypassed cold water. When the water heater is restarted, a section of high-temperature water will flow out, which may scald the user in severe cases. This solution can effectively control the water flow of the bypass tube 213 by controlling the bypass time and the bypass ratio, thereby accurately controlling the outlet water temperature of the water heater, achieving better start-stop constant temperature control of the outlet water temperature of the water heater, and effectively improving the problems of start-stop constant temperature difference, high vaporization noise, and low thermal efficiency of conventional water heaters. The bypass time can be 2 seconds, or 3 seconds, or 4 seconds, etc., which are not specifically limited here.
As shown in
It is understandable that there can be multiple heat exchange tubes 140, and there can be multiple heat exchange plates 150. Multiple heat exchange plates 150 are provided side by side, and multiple heat exchange tubes 140 are provided in sequence on each heat exchange plate 150. Multiple heat exchange tubes 140 are communicated in sequence to form a heat exchange flow channel. The heat exchange plates 150 are sleeved outside the heat exchange tubes 140. The heat exchange plates 150 can be clamped with or welded to the heat exchange tubes 140, which is not limited here. In addition, the material of the heat exchange tubes 140 and the heat exchange plates 150 can be copper, of course, it can also be other materials, which will be described in detail in the following.
In some embodiments, the axial projection surface of the heat exchange tube 140 can be understood as: along the radial section of the heat exchange tube 140. On the radial section of the heat exchange tube 140, the minimum distance between any point of the heat exchange plate 150 on the section and the outer tube wall of the heat exchange tube 140 is less than or equal to 3 mm, so that the distance between any point on the heat exchange plate 150 and the heat exchange tube 140 is relatively close. When the water heater is working, the heat exchange plate 150 that absorbs the heat of the high-temperature flue gas will transfer the heat to the heat exchange tube 140. The distance between the heat exchange plate 150 and the heat exchange tube 140 is relatively close, which is beneficial to improve the heat exchange capacity of the heat exchange plate 150, and is also beneficial to reduce the volume of the heat exchange plate 150, improve the material utilization rate of the heat exchange plate 150, so that the temperature on the heat exchange plate 150 can be evenly distributed. The minimum distance between any point on the heat exchange plate 150 and the outer tube wall of the heat exchange tube 140 can be 3 mm, or 2.5 mm, or 2 mm, etc., which is not specifically limited here.
In some embodiments of the present application, the minimum distance between any point on the heat exchange plate 150 and the outer tube wall of the heat exchange tube 140 is limited to less than or equal to 3 mm. In this way, the distance between any point on the heat exchange plate 150 and the heat exchange tube 140 is relatively close, and the temperature on the heat exchange plate 150 can be quickly transferred to the heat exchange tube 140, thereby improving the heat exchange performance of the heat exchange plate 150. In addition, the material utilization rate of the heat exchange plate 150 is also improved, the temperature difference between the inner side of the heat exchange plate 150 closer to the heat exchange tube 140 and the outer side farther from the heat exchange tube 140 is reduced, the high temperature area and the low temperature area on the heat exchange plate 150 are reduced, so that the temperature distribution on the heat exchange plate 150 is more uniform. The reduction of high-temperature areas on the heat exchange plate 150 is beneficial to reducing the heat storage capacity of the heat exchange plate 150, thereby reducing the temperature rise of the water in the heat exchanger 100 when the water supply is cut off, which is beneficial to reducing the risk of scalding the user by the high-temperature water when the user starts the water heater again. In other words, this solution makes the temperature distribution on the heat exchange plate 150 more uniform, reduces the high-temperature areas on the heat exchange plate 150, and reduces the temperature rise of the heat exchanger 100 when the water supply is cut off.
In addition, when the water heater is working at a small load, the low-temperature area on the heat exchange plate 150 is reduced, which is conducive to increasing the temperature of the heat exchange plate 150 after heat exchange with the high-temperature flue gas, so as to ensure that the temperature of the entire heat exchange plate 150 is high, and the situation of local low temperature on the heat exchange plate 150 causing condensed water is reduced, thereby reducing the risk of condensed water corroding the water heater. In other words, this solution makes the temperature distribution on the heat exchange plate 150 more uniform, reduces the low-temperature area on the heat exchange plate 150, and reduces the risk of condensed water in the heat exchanger 100 corroding the water heater. It can be seen that the technical solution of the present application improves the heat exchange performance of the heat exchanger 100, lowers the risk of the scalding the user due to the water in the heat exchanger 100 having an excessively high temperature rise when the water is stopped, and also reduces the risk of condensed water in the heat exchanger 100 corroding the water heater.
In some embodiments, the heat exchanger 100 includes a plurality of heat exchange tubes 140 and a plurality of heat exchange plates 150 provided side by side, and the plurality of heat exchange tubes 140 are sequentially spaced apart along the length direction of each heat exchange plate 150, so as to be provided in a single row on the heat exchange plate 150. It can be understood that the heat exchanger 100 in the embodiment includes a plurality of heat exchange tubes 140, and the plurality of heat exchange tubes 140 are provided in a single row on the heat exchange plate 150, that is, the plurality of heat exchange tubes 140 in the embodiment are single-layer tubes, and the single-layer fin tubes (that is, the single-layer heat exchange tubes 140 with the heat exchange plates 150) are directly in contact with the high-temperature flue gas. Compared with the double-layer fin tubes (that is, heat exchange tubes 140 with upper and lower layers), the single-layer fin tubes have fewer low-temperature areas, and the single-layer fin tubes do not have the problem of temperature difference between the upper and lower layers. When the burner 21 of the water heater is working at a small load, the single-layer fin tubes with fewer low-temperature areas are not easy to produce condensed water, thereby reducing the risk of condensed water corroding the water heater. In addition, the single-layer fin tube is combined with the heat exchange plate 150 with higher heat exchange performance, so as to further improve the heat exchange performance of the heat exchanger 100.
In some embodiments, the plurality of heat exchange tubes 140 are all oval tubes; and/or, the plurality of heat exchange tubes 140 are at the same height on the heat exchange plates 150.
It can be understood that the heat exchange tube 140 is an oval tube. Compared with the conventional circular heat exchange tube 140, the oval heat exchange tube 140 is more conducive to the high-temperature flue gas flowing to the back side of the heat exchange tube 140 for heat exchange, and the heat exchange area per unit volume of the oval tube is larger than that of the circular tube, thereby effectively improving the heat exchange efficiency of the heat exchanger 100.
In addition, the multiple heat exchange tubes 140 have the same height on the heat exchange plate 150, and the distances between the multiple heat exchange tubes 140 and the burner 21 are kept consistent, which helps to ensure that the temperatures of the multiple heat exchange tubes 140 when in contact with the high-temperature flue gas are basically the same, avoiding the situation where a large temperature difference on the multiple heat exchange tubes 140 provided in a single row easily generates condensed water, thereby helping to increase the service life of the heat exchanger 100.
As shown in
In some embodiments, the plurality of installation holes 151 are all oval holes; and/or, the plurality of installation holes 151 on the heat exchange plate 150 are all the same in size and height.
It can be understood that the multiple installation holes 151 are all oval holes, so that the corresponding heat exchange tubes 140 passing through the multiple installation holes 151 are also oval tubes. The oval heat exchange tubes 140 are more conducive to the high-temperature flue gas flowing to the back side of the heat exchange tubes 140 for heat exchange, and the heat exchange area per unit volume of the oval tubes is larger, which is beneficial to improving the heat exchange efficiency of the heat exchanger 100.
In addition, the size and height of the multiple installation holes 151 on the heat exchange plate 150 are the same, which ensures the consistency of the multiple installation holes 151 and is also beneficial to maintaining the size and height of the multiple heat exchange tubes 140 consistent. Therefore, it is beneficial to ensuring that the temperatures of the multiple heat exchange tubes 140 when in contact with the high-temperature flue gas are basically the same, avoiding the situation where there is a large temperature difference on the multiple heat exchange tubes 140 provided in a single row, which easily generates condensed water, thereby helping to increase the service life of the heat exchanger 100.
In some embodiments, a second flange 155 extending outward is provided at the outer periphery of the installation hole 151. The second flange 155 can have a variety of shapes, such as but not limited to a ring shape. By providing the second flange 155, the sleeve area of the heat exchange tube 140 and the heat exchange plate 150 is increased, and it is also beneficial to improve the stability of the connection between the heat exchange tube 140 and the heat exchange plate 150. In addition, by providing the second flange 155, it is also ensured that there can be a certain distance between two adjacent heat exchange plates 150, which is beneficial for high-temperature flue gas to pass between two adjacent heat exchange plates 150, thereby improving the heat exchange efficiency of the heat exchanger 100.
As shown in
It can be understood that the baffle bar 152 is located between any two adjacent installation holes 151, the middle part of the baffle bar 152 is concave downward, and a guide channel is formed between the baffle bar 152 and the heat exchange tube 140 in the adjacent installation hole 151. The guide channel can gather the high-temperature flue gas to flow in the upper half of the heat exchange tube 140, that is, to gather the high-temperature flue gas to flow on the back of the heat exchange tube 140. In addition, the guide channel can also block the high-temperature flue gas from flowing directly upward, delay the separation of the high-temperature flue gas and the heat exchange tube 140, increase the heat exchange intensity and reduce heat loss, thereby helping to improve the heat exchange efficiency. In some embodiments, the curvature of the guide strip is consistent with the curvature of the heat exchange tube 140 in the adjacent installation hole 151, which is conducive to guiding the high-temperature flue gas to the back of the heat exchange tube 140 for heat exchange.
In some embodiments, a guide hole 153 is provided between any two adjacent installation holes 151, and a guide edge 154 is provided in a ring shape on the outer periphery of the guide hole 153. The guide edge 154 is located directly below the baffle bar 152.
It can be understood that the heat is more concentrated below the baffle bar 152. By providing the guide hole 153 directly below the baffle bar 152, local overheating of the position directly below the baffle bar 152 is avoided, which is beneficial to improving the uniformity of temperature distribution on the heat exchange plate 150. In addition, the outer periphery of the guide hole 153 is provided with a guide edge 154 provided in a ring shape, and the guide edge 154 guides the gathered high-temperature flue gas to the periphery of the heat exchange tube 140. The guide edge 154 is provided to help increasing the heat exchange area and improving the heat exchange efficiency.
In some embodiments, the heat exchanger 100 is provided with a water inlet 11 and a water outlet 12, and the water inlet 11 and the water outlet 12 are provided at the same side of the heat exchanger 100.
In some embodiments, the quantity of the heat exchange tubes 140 is six, and the six heat exchange tubes 140 are provided in sequence and spaced apart along the length direction of the heat exchange plates 150.
It is understandable that the heat exchanger 100 further includes a water inlet tube section 110 and a water outlet tube section 120, the water inlet tube section 110 is communicated with the water inlet 11, and the water outlet tube section 120 is communicated with the water outlet 12. The water inlet 11 and the water outlet 12 are provided at the same side of the heat exchanger 100, which is conducive to fully utilizing the space on the same side of the heat exchanger 100, and is conducive to improving the compactness of the water circuit arrangement of the water heater, reducing the space occupied by the water circuit arrangement device of the water heater, and thus helping to reduce the volume of the water heater.
In addition, the six heat exchange tubes 140 are provided in sequence along the length direction of the heat exchange plate 150, so that the six heat exchange tubes 140 are provided in a single row. The six heat exchange tubes 140 provided in a single row can ensure that the temperature of the heat exchange tubes 140 when in contact with the high-temperature flue gas remains basically consistent, reducing the risk of condensation water generated by the heat exchange tubes 140 and corroding the water heater, thereby improving the reliability of the heat exchanger 100.
In some embodiments, the heat exchanger 100 further includes two end plates 160 that are opposite and spaced apart from each other. The plurality of heat exchange plates 150 are provided between the two end plates 160, and the end plates 160 are made of stainless steel.
In some embodiments, the heat exchange tube 140 is made of stainless steel.
In some embodiments, the heat exchange plates 150 are made of stainless steel.
It can be understood that a communication part 161 is provided at the end plate 160, every two heat exchange tubes 140 are communicated through one of the communication parts 161, and a plurality of heat exchange tubes 140 are communicated through a plurality of communication parts 161 to form a heat exchange channel.
The end plate 160 in the embodiment is made of stainless steel, which has good thermal conductivity, high temperature resistance and corrosion resistance. Therefore, the end plate 160 is not easily corroded by condensed water, which is beneficial to extending the service life.
Similarly, the heat exchange tube 140 and/or the heat exchange plate 150 are made of stainless steel, so that the heat exchange tube 140 and/or the heat exchange plate 150 are not easily corroded by condensed water, so that the heat exchanger 100 has better corrosion resistance, which is beneficial to improving the service life of the heat exchanger 100.
In addition, the heat exchange plates 150 and the heat exchange tubes 140 in the heat exchanger 100 are both made of stainless steel, and the minimum distance between any point on the heat exchange plate 150 and the outer tube wall of the heat exchange tube 140 is less than or equal to 3 mm. That is, the distance between the heat exchange plate 150 and the heat exchange tube 140 is relatively close, and the temperature on the heat exchange plate 150 can be quickly transferred to the heat exchange tube 140, thereby further improving the heat exchange efficiency of the heat exchanger 100.
It is understandable that when the size of the heat exchanger 100 is constant, a large tube spacing between adjacent heat exchange tubes 140 will result in a reduction in the quantity of installed heat exchange tubes 140, thereby affecting the heat exchange efficiency of the heat exchanger 100 and the performance of the water heater.
As shown in
It can be understood that the two end plates 160 are provided opposite to each other and spaced apart along the second direction, and the second direction intersects with the first direction. In some embodiments, the first direction can be specifically the width direction of the heat exchanger 100 (for example, the front-to-rear direction), and the second direction can be specifically the length direction of the heat exchanger 100 (for example, the left-to-right direction). The two end plates 160 cooperate to support the heat exchanger 100, and the communication parts 161 on the two end plates 160 also play the role of a water box to connect multiple independent heat exchange tubes 140 in series to form a tortuous heat exchange channel. With this arrangement, there is no need to set a bend structure on the outside of the two end plates 160 to connect two adjacent heat exchange tubes 140, which can simplify the assembly process and improve production efficiency.
In some embodiments, a plurality of through holes 164 are provided at the end plate 160, and an annular protrusion 165 is provided at the outer periphery of the through hole 164. The annular protrusion 165 is provided at the side of the end plate 160 facing the other end plate 160, that is, the annular protrusion 165 is provided at the side of the end plate 160 facing the heat exchange plate 150, which not only facilitates the insertion of the end of the heat exchange tube 140 into the annular protrusion 165, but also facilitates the sealed connection between the heat exchange tube 140 and the annular protrusion 165. The sealed connection manner includes but is not limited to: welding sealing, or filling sealing with a seal 222. In some embodiments, the heat exchange tube 140 is welded and sealed with the annular protrusion 165 sleeved on the outside of its end, which not only simplifies the assembly process but also ensures the stability of the seal.
As shown in
It can be understood that the annular protrusion 165 in some embodiments is provided at the side of the end plate 160 facing the heat exchange tube 140, and the side of the end plate 160 facing distant from the heat exchange tube 140 does not need to be provided with a connection part adapted to the communication part 161. That is, the side of the end plate 160 facing distant from the heat exchange tube 140 does not need to be provided with an annular protrusion 165 adapted to the communication part 161. Every two heat exchange tubes 140 are communicated through a communication port 1611 of a communication part 161, and W1 is less than or equal to W2, which means that the annular protrusion 165 in some embodiments does not occupy the internal space of the communication port 1611 of the first communication part 1612, which is beneficial to reducing the width dimension of the communication port 1611 of the first communication part 1612 along the first direction. The reduction in the width of the first communication part 1612 is beneficial for reducing the tube spacing between the two heat exchange tubes 140 communicated with the first communication part 1612, so that the heat exchanger 100 can increase the quantity of heat exchange tubes 140 within a certain width range, thereby improving the heat exchange efficiency of the heat exchanger 100, that is, improving the heat exchange efficiency of the heat exchange system 10.
It can be seen that W1≤W2, that is, the annular protrusion 165 is connected to the end of the heat exchange tube 140, and the annular protrusion 165 does not occupy the internal space of the communication port 1611 of the first communication part 1612, so that the opening width of the communication port 1611 of the first communication part 1612 along the first direction can be reduced, that is, the width dimension of the first communication part 1612 along the first direction can be reduced, so that the tube spacing between the two heat exchange tubes 140 communicated with the first communication part 1612 can be reduced. The tube spacing between the two heat exchange tubes 140 is reduced. When the size of the heat exchanger 100 is constant, it is beneficial for the heat exchanger 100 to arrange more heat exchange tubes 140 in the first direction. The quantity of heat exchange tubes 140 increases, which can improve the heat exchange efficiency of the heat exchanger 100. It can be seen that the technical solution of the present application is conducive to reducing the tube spacing between the two heat exchange tubes 140, thereby improving the heat exchange efficiency of the heat exchanger 100, that is, improving the heat exchange efficiency of the heat exchange system 10.
As shown in
It is understandable that the communication part 161 on the second plate 163 can be formed by stamping into a groove shape, and the side of the second plate 163 facing distant from the communication port 1611 can be a plane, or can be convex, which is not limited here and will be described in detail as follows. The communication port 1611 of the communication part 161 is communicated with the through hole 164 on the first plate 162, and the heat exchange tube 140 is communicated with the through hole 164 on the first plate 162, so that the heat exchange tube 140 is communicated with the communication part 161. The second plate 163 is provided at the side of the first plate 162 facing distant from the heat exchange tube 140, so as to facilitate the sealed connection between the second plate 163 and the first plate 162. The second plate 163 and the heat exchange tube 140 do not interfere with each other. The sealing connection manner includes but is not limited to: the second plate 163 is welded and sealed with the first plate 162 as a whole, or the whole is filled and sealed by the seal 222. This is conducive to simplifying the assembly process. There is no need to configure a bend structure for every two heat exchange tubes 140. The sealing connection is carried out through the entire second plate 163, which is conducive to improving the assembly efficiency.
In some embodiments, the second plate 163 is provided with a first plate surface facing the first plate 162 and a second plate surface facing distant from the first plate 162, and the first plate surface is recessed in the direction of the second plate surface to form the communication part 161. In this arrangement, the communication part 161 is formed by the second plate 163 being recessed in the direction of the second plate surface into a groove shape, and the groove shape can be formed by stamping, that is, the second body can be formed into the communication part 161 by stamping, so that the communication part 161 is easy to form, which is conducive to simplifying the manufacturing process of the end plate 160.
As shown in
In some embodiments, the stamped part 166 and the second plate 163 are an integral structure, and the communication part 161 and the stamped part 166 are stamped. It can be understood that, compared with the stamped part 166 and the second plate 163 being fixed by welding, the stamped part 166 and the communication part 161 in the embodiment are both stamped by the second plate 163, which is not only conducive to enhancing the strength of the second plate 163, but also simplifies the manufacturing process of the communication part 161, avoids the problem of loose sealing when the stamped part 166 and the second plate 163 are sealed (such as welding sealing), and improves the reliability of the second body.
In some embodiments, one of the multiple communication parts 161 is provided with a water inlet 11, and another one of the communication parts 161 is provided with a water outlet 12. The heat exchanger 100 further includes a water inlet tube section 110 and a water outlet tube section 120. The water inlet tube section 110 is communicated with the water inlet 11, and the water outlet tube section 120 is communicated with the water outlet 12. The water inlet 11 and the water outlet 12 are provided at the same side of the heat exchanger 100. Such a configuration is conducive to making full use of the space on the same side of the heat exchanger 100, improving the compactness of the water path arrangement of the water heater, reducing the space occupied by the water path arrangement device of the water heater, and thus helping to reduce the volume of the water heater.
As shown in
It is understandable that an accommodation sink 167 is formed on one side of the first plate 162 facing the second plate 163, and the second plate 163 is provided in the accommodation sink 167 to facilitate the rapid positioning and installation of the second plate 163. The periphery of the second plate 163 can be welded and sealed with the first plate 162, and the periphery of the second plate 163 can also be welded and sealed with the first flange 1621. The periphery of the second plate 163 can also be welded and sealed at the connection between the first plate 162 and the first flange 1621, which is not limited here. By sealedly connecting the periphery of the second plate 163 with the first plate 162 and/or the first flange 1621, a plurality of communication parts 161 are formed on the second plate 163, and the communication parts 161 do not need to be welded with the heat exchange tube 140. Compared with the need to weld a bend structure for every two heat exchange tubes 140, this solution can simplify the assembly process of the heat exchanger 100 and improve production efficiency.
When the water heater is working, cold water enters the heat exchange tube 140, and the high-temperature flue gas flows upward. The lowermost end of the heat exchange tube 140 contacts the high-temperature flue gas first. The lowermost end of the heat exchange tube 140 is the fire-facing end. The fire-facing end of the heat exchange tube 140 is prone to local high-temperature vaporization and generate noise, thereby affecting the silent performance index of the water heater.
In order to reduce the vaporization noise of the heat exchange tube 140, as shown in
It is understandable that a baffle 170 may be provided in each heat exchange tube 140. The baffle 170 may also be provided in only one or part of the heat exchange tubes 140 as required, which is not limited here. In some embodiments, a baffle 170 may be provided in each heat exchange tube 140. The baffle 170 can extend the flow path of the water flow in the heat exchange tube 140, enhance the baffle effect, increase the contact time between the high-temperature flue gas and the water, and make the heat exchange between the high-temperature flue gas and the water more sufficient.
In some embodiments, the baffle 170 includes a baffle body 171 and two support parts 172. The baffle body 171 is connected to the top ends of the two support parts 172, so that the baffle 170 is provided in an inverted Y shape. The bottom ends of the two support parts 172 are provided at intervals and are respectively supported on the inner wall surface of the fire-facing end of the heat exchange tube 140. The two support parts 172 increase the contact area with the inner wall surface of the fire-facing end of the heat exchange tube 140, destroy the flow boundary layer of the inner wall surface of the fire-facing end of the heat exchange tube 140, thereby increasing the contact time between the high-temperature flue gas and water, which is beneficial to increasing the temperature of the water flow in the heat exchange tube 140. That is, strengthening the inner side heat transfer of the fire-facing end of the heat exchange tube 140, thereby reducing the noise generated by the local overheating vaporization of the fire-facing end of the heat exchange tube 140. It can be seen that the present solution increases the turbulence effect on water by providing the baffle 170, destroys the flow boundary layer on the inner wall surface of the fire-facing end of the heat exchange tube 140, and makes the heat exchange between the water flow and the high-temperature flue gas more complete, thereby reducing the vaporization noise of the heat exchange tube 140.
In some embodiments, one of the two support parts 172 includes a plurality of first support leg 176, and the other support part 172 includes a plurality of second support leg 177, and the plurality of first support leg 176 and the plurality of second support leg 177 are alternately provided in sequence along the length direction of the baffle 170. The plurality of first support leg 176 are tilted toward one side of the baffle body 171, and the plurality of second support leg 177 are tilted toward the other side of the baffle body 171. In this way, the plurality of first support leg 176 and the plurality of second support leg 177 can be stably supported on the inner wall of the heat exchange tube 140, and the baffle effect can also be enhanced.
On the axial projection surface of the heat exchange tube 140, the first support leg 176 and the second support leg 177 form an angle, which is an acute angle. In this arrangement, the distance between the bottom end of the first support leg 176 and the bottom end of the second support leg 177 is relatively close, and they are respectively relatively adjacent to the bottom end of the fire-facing end of the heat exchange tube 140, which is conducive to destroying the flow boundary layer of the inner wall surface of the fire-facing end of the heat exchange tube 140, and can strengthen the heat transfer inside the fire-facing end of the heat exchange tube 140, so as to achieve the effect of reducing the noise generated by the local overheating vaporization of the fire-facing end of the heat exchange tube 140.
In other embodiments, on the axial projection surface of the heat exchange tube 140, the first support leg 176 and the second support leg 177 form an angle, and the angle is a right angle or an obtuse angle, which is not specifically limited here.
As shown in
In some embodiments, a baffle spur 175 extending toward the water-facing end is provided at a hole wall of at least one of the baffle holes 173.
It is understandable that each baffle hole 173 is provided with a baffle sheet 174 inclined outwardly, and each baffle sheet 174 is provided at the edge of the baffle hole 173 distant from the water-facing end, which can enhance the baffle effect and prevent water from scaling in the heat exchange tube 140. Two adjacent baffle sheets 174 are provided at both sides of the baffle body 171, which can further enhance the baffle effect.
In addition, a baffle spur 175 is provided in the baffle hole 173, and the baffle spur 175 extends toward the water-facing end of the baffle 170. When the water flows through the baffle hole 173, the baffle spur 175 blocks the water flow to extend the flow path of the water flow in the heat exchange tube 140, further enhancing the baffle effect, thereby further reducing the vaporization noise of the heat exchange tube 140.
In some embodiments, a baffle spur 175 is provided at the top wall and/or the bottom wall of the baffle hole 173. In this way, when water passes through the baffle hole 173, the baffle spur 175 provided at the top wall of the baffle hole 173 and/or the baffle spur 175 provided at the bottom wall of the baffle hole 173 increase the baffle effect of the baffle 170, so that the heat exchange between the water flow and the high-temperature flue gas is more complete, and the vaporization noise of the heat exchange tube 140 is further reduced.
In some embodiments, the annular protrusion 165 is provided in an oval ring shape, and the end of the heat exchange tube 140 passes through the annular protrusion 165 and extends into the through hole 164.
In some embodiments, the through hole 164 is provided in an oval shape.
It can be understood that the annular protrusion 165 is provided in the shape of an oval ring to be compatible with the oval heat exchange tube 140. When the end of the oval heat exchange tube 140 is inserted into the annular protrusion 165, the outer wall of the heat exchange tube 140 can fit tightly with the inner wall surface of the annular protrusion 165, facilitating the sealed connection between the heat exchange tube 140 and the annular protrusion 165. In addition, the end of the heat exchange tube 140 passes through the annular protrusion 165 and extends into the through hole 164, which increases the contact area between the heat exchange tube 140 and the end plate 160, and is conducive to improving the connection stability between the heat exchange tube 140 and the end plate 160.
In addition, the through hole 164 is in an oval shape to facilitate matching with the oval heat exchange tube 140, that is, the end of the oval heat exchange tube 140 extends into the through hole 164 and fits tightly with the end plate 160, so that multiple through holes 164 are compactly provided at the end plate 160, which is beneficial to reducing the tube spacing between the two heat exchange tubes 140.
In some embodiments, the length of the bypass tube 213 is less than or equal to 100 mm. With such an arrangement, the length of the bypass tube 213 is relatively short, and the cold water in the first tube 211 can be quickly transported to the second tube 212 through the relatively short bypass tube 213 to mix with the hot water in the second tube 212. The controller 220 of the flow valve 200 is easy to accurately control the water flow through the bypass tube 213, thereby ensuring that the heat exchange system 10 has a faster bypass response speed and a more accurate bypass ratio. In addition, the short length of the bypass tube 213 is conducive to improving the structural stability of the entire flow valve 200, avoiding the bypass tube 213 from deforming due to its length after long-term use, thereby affecting the bypass ratio and bypass response speed, thereby improving the stability of the heat exchange system 10. It can be seen that when the heat exchange system 10 of the present application is applied to a water heater, the bypass response speed of the heat exchange system 10 is relatively fast, and the controller 220 of the flow valve 200 is easy to accurately control the water flow rate of the bypass tube 213, which is beneficial to ensure the stability of the water outlet temperature of the water heater.
As shown in
It can be understood that the parallel extension of the first tube 211 and the second tube 212 means that the axis of the first tube 211 is parallel or substantially parallel to the axis of the second tube 212. The bypass tube 213 is a straight tube structure and is connected between the first tube 211 and the second tube 212. The straight tube structure is conducive to shortening the water flow path and improving the smoothness of water flow, and is also convenient for processing the flow valve 200. The axis of the bypass tube 213 can be perpendicular to or obliquely intersecting with the axis of the first tube 211 (or the second tube 212), so that the valve body 210 generally presents an “H”-shaped valve or an “N”-shaped valve structure. In this way, the overall structure of the valve body 210 is regular and suitable for connecting with the water inlet tube section 110 and the water outlet tube section 120 of the heat exchanger 100, which is conducive to shortening the length of the bypass tube 213 and reducing the overall volume of the water heater. The controller 220 is provided at the peripheral wall of the bypass tube 213 to control the bypass flow channel.
In some embodiments, the axis of the bypass tube 213 is perpendicular to the axis of the first tube 211 and the axis of the second tube 212. With this arrangement, the valve body 210 generally presents an “H”-shaped valve structure, which is conducive to ensuring that the length of the bypass tube 213 is less than or equal to 100 mm when manufacturing the valve body 210, and the overall structure of the valve body 210 is regular and reasonably provided, which is conducive to reducing the difficulty of manufacturing the valve body 210.
In some embodiments, the controller 220 is only a solenoid valve or a proportional valve. Specifically, the controller 220 is only a solenoid valve, and the on-off of the bypass tube 213 is controlled by the solenoid valve, which is conducive to the miniaturization of the flow valve 200. In some embodiments, the controller 220 is only a proportional valve, and the water flow rate of the bypass tube 213 is adjusted by the proportional valve, thereby realizing the bypass ratio adjustment, which is conducive to the miniaturization of the flow valve 200. In some embodiments, the controller 220 is only a solenoid valve, which can be a normally-off solenoid valve.
As shown in
In some embodiments, the controller 220 is located in the area formed by the heat exchanger 100, the first tube 211, the bypass tube 213 and the second tube 212. Specifically, the two ends of the bypass tube 213 are respectively connected to the middle of the first tube 211 and the middle of the second tube 212, and the valve of the flow valve 200 presents an “H”-shaped valve structure. The controller 220 is provided at the peripheral wall of the bypass tube 213, and the controller 220 is located between the first tube 211 and the second tube 212. In this way, the cavity area constructed by the flow valve 200 itself can be fully utilized to accommodate the controller 220, so as to further improve the compactness of the overall structure and reduce the occupied space. In some embodiments, the controller 220 is provided at the side of the bypass tube 213 facing the heat exchanger 100.
In some embodiments, the center line of the controller 220 is parallel to the axis of the first tube 211 and the axis of the second tube 212, and is perpendicular to the windward surface of the heat exchanger 100. It can be understood that the windward surface of the heat exchanger 100 specifically refers to the side of the heat exchanger 100 opposite to the burner 21. The center line of the controller 220 is parallel to the axis of the first tube 211 and the axis of the second tube 212, and the extension directions of the first tube 211, the second tube 212 and the controller 220 are consistent, so that the structural layout of the entire flow valve 200 is more regular, and the extension direction of the controller 220 is perpendicular to the windward surface of the heat exchanger 100, so that the arrangement of the flow valve 200 and the heat exchanger 100 is more regular, which is conducive to reducing the occupied space.
As shown in
In some embodiments, the heat exchanger 100 includes a heat exchanger body 130 provided with a water inlet 11 and a water outlet 12, the water inlet tube section 110 is communicated with the water inlet 11, the water outlet tube section 120 is communicated with the water outlet 12, and the distance between the flow valve 200 and the heat exchanger body 130 is greater than or equal to 60 mm. Such a configuration can ensure that a sufficient distance is reserved between the flow valve 200 and the heat exchanger body 130, so as to avoid the valve body 210 and the controller 220 of the flow valve 200 being damaged by the heat radiation of the heat exchanger body 130 for a long time, and the service life of the flow valve 200 can be extended. For example, the distance between the flow valve 200 and the heat exchanger body 130 can be 60 mm, 70 mm, 80 mm, 90 mm, 100 mm, etc.
In some embodiments, the heat exchanger body 130 includes two end plates 160 spaced apart and a plurality of heat exchange tubes 140 provided between the two end plates 160 and spaced apart along a first direction. The two end plates 160 are respectively provided with communication parts 161 corresponding to each of the heat exchange tubes 140. The plurality of heat exchange tubes 140 are communicated through the plurality of communication parts 161 to form a tortuous heat exchange channel. The water inlet 11 and the water outlet 12 are both provided at one of the end plates 160, and the heat exchange channel communicates the water inlet 11 with the water outlet 12.
It can be understood that the two end plates 160 are provided opposite to each other and spaced apart along the second direction, and the first direction intersects the second direction. The first direction can specifically be the width direction of the heat exchanger body 130 (for example, the front-to-rear direction), and the second direction can specifically be the length direction of the heat exchanger body 130 (for example, the left-to-right direction). The two end plates 160 cooperate to support the heat exchanger body 130, and the communication parts 161 on the two end plates 160 also act as a water box to connect multiple independent heat exchange tubes 140 in series to form a tortuous heat exchange channel. In this way, there is no need to set a bend structure on the outside of the two end plates 160 to connect two adjacent heat exchange tubes 140, which can simplify the assembly process and improve production efficiency.
In some embodiments, each end plate 160 includes a first plate 162 and a second plate 163 that cooperate with each other, where the first plate 162 is provided at the side of the second plate 163 facing the heat exchange tube 140. The second plate 163 is recessed in the direction distant from the first plate 162 to form the communication part 161. The second plate 163 has a first plate surface facing the first plate 162 and a second plate surface facing distant from the first plate 162, and the second plate surface is raised in the direction distant from the first plate surface, so that the communication part 161 is formed with a stamped part 166 on the second plate surface, so that the inside of the communication part 161 is hollow. The first plate 162 is provided with a through hole 164, and the end of the heat exchange tube 140 is inserted into the through hole 164 and communicated with the communication part 161. Every two heat exchange tubes 140 are communicated through a communication port 1611 of the communication part 161. The first plate 162 and the second plate 163 are fixed in a manner including but not limited to welding, screw connection, etc. In some embodiments, the periphery of the first plate 162 is provided with a flange, and the periphery of the second plate 163 is provided with a folded edge opposite to the flange of the first plate 162, and the folded edge and the flange are abutted and matched to improve the assembly reliability of the first plate 162 and the second plate 163.
The plurality of heat exchange tubes 140 are provided in a single row of heat exchange tubes 140 along the width direction (e.g., front-to-rear direction) of the heat exchanger body 130, and the single row of heat exchange tubes 140 is perpendicular to the flue gas flow direction, so that the high-temperature flue gas generated by the burner 21 flows from bottom to top and can fully contact with the single row of heat exchange tubes 140 for heat exchange, thereby improving the heat exchange efficiency. In some embodiments, the heat exchanger body 130 further includes a plurality of heat exchange plates 150 provided between the two end plates 160, and the plurality of heat exchange plates 150 are provided side by side in sequence, and each heat exchange tube 140 is inserted into the heat exchange plates 150. By providing a plurality of heat exchange plates 150, the heat exchange area can be further increased, thereby improving the heat exchange efficiency.
In some embodiments, the water inlet 11 and the water outlet 12 are provided at the same side of the heat exchanger body 130 in the length direction, and the water inlet 11 and the water outlet 12 are spaced apart in the width direction of the heat exchanger body 130.
It can be understood that the length direction of the heat exchanger body 130 can be specifically the left-right direction, and the width direction of the heat exchanger body 130 can be specifically the front-rear direction. The water inlet 11 and the water outlet 12 are provided at the same side of the length direction of the heat exchanger body 130, and the water inlet tube section 110 and the water outlet tube section 120 can be provided at the same side of the length direction of the heat exchanger body 130, which is conducive to fully utilizing the same side space in the length direction of the heat exchanger body 130, and can also facilitate the installation of the flow valve 200. In addition, the water inlet 11 and the water outlet 12 are spaced apart along the width direction of the heat exchanger body 130, and the water inlet tube section 110 and the water outlet tube section 120 can be provided side by side along the width direction of the heat exchanger body 130, so that the space in the width direction of the heat exchanger body 130 can be fully utilized. In addition, the water inlet 11 and the water outlet 12 are spaced apart along the width direction of the heat exchanger body 130, and the distance between the water inlet 11 and the water outlet 12 is provided as large as possible, so that the length of the heat exchange channel connected between the water inlet 11 and the water outlet 12 can be extended as much as possible, so that the water in the heat exchange channel can fully exchange heat with the high-temperature flue gas generated by the burner 21, thereby improving the heat exchange efficiency.
In some embodiments, the first tube 211 and the second tube 212 are both extended along a third direction, the bypass tube 213 is extended along a fourth direction, two ends of the bypass tube 213 are respectively connected to the middle of the first tube 211 and the middle of the second tube 212, and the bypass tube 213 is provided with an installation base 218 on one side of the third direction for installing the controller 220, where the third direction intersects with the fourth direction.
In some embodiments, when the heat exchange system 10 is applied to a water heater, since the cold water input tube 23 and the hot water output tube 24 of the water heater are extended along the height direction of the water heater. Accordingly, the third direction is the height direction of the water heater, so that the first tube 211 and the second tube 212 are both vertical pipes extending along the height direction of the water heater, so as to facilitate the first tube 211 and the second tube 212 to be connected in series with the cold water input tube 23 and the hot water output tube 24 respectively, and improve the smoothness of the installation of the flow valve 200. The fourth direction can be the thickness direction of the water heater (for example, the front-to-rear direction) or the width direction of the water heater (for example, the left-to-right direction), and the third direction and the fourth direction can be perpendicular to each other or have a certain inclination angle. Since the length of the bypass tube 213 is short, in some embodiments, the fourth direction is the thickness direction of the water heater, which is conducive to making full use of the space in the thickness direction of the water heater to reduce the width size of the water heater.
As shown in
In some embodiments, a partition is provided inside the bypass tube 213, and the partition divides the bypass tube 213 into a first bypass section 214 and a second bypass section 215. The peripheral wall of the bypass tube 213 is provided with a first water outlet 216 and a second water outlet 217 on opposite sides of the partition. When the bypass tube 213 needs to be closed, the drive end of the driver 221 abuts against the seal 222. At this time, the driver 221 cooperates with the seal 222 to block the first water outlet 216 and the second water outlet 217, thereby ensuring the sealing performance. After the water in the first tube 211 enters the first bypass section 214, it cannot be further transported forward to the second bypass section 215. When the bypass tube 213 needs to be opened, the driver 221 can drive the seal 222 away from the peripheral wall of the bypass tube 213 to communicate the first water outlet 216 with the second water outlet 217, or the drive end of the driver 221 can be moved away from the seal 222 to cause the seal 222 to produce a certain displacement or deformation under the water flow pressure to communicate the first water outlet 216 with the second water outlet 217. At this time, the first bypass section 214 is communicated with the second bypass section 215, thereby realizing the bypass water mixing function.
In some embodiments, the peripheral wall of the bypass tube 213 is provided with an installation base 218 for installing the driver 221, the installation base 218 is provided with a sink for accommodating the seal 222, and the bottom wall of the sink is provided with the first water outlet 216 and the second water outlet 217. The driver 221 includes an actuator and a push rod 223 drivingly connected to the actuator, the actuator blocks the top opening of the sink, the push rod 223 is extended toward the seal 222, and the actuator is used to drive the push rod 223 to perform telescopic movement. When the push rod 223 is in an extended state, the push rod 223 abuts against the seal 222 to block the first water outlet 216 and the second water outlet 217. When the push rod 223 is in a retracted state, a water flow channel is formed between the seal 222 and the bypass tube 213 to communicate the first water outlet 216 with the second water outlet 217.
In some embodiments, the actuator is fixed to the installation base 218 and blocks the top opening of the sink. The seal 222 is located in the sealed cavity formed by the actuator and the bypass tube 213, which can prevent water in the bypass tube 213 from leaking out and causing damage to the actuator. When the bypass tube 213 needs to be closed, the push rod 223 abuts against the seal 222 to block the first water outlet 216 and the second water outlet 217. At this time, the push rod 223 generates a certain pressure on the seal 222, which can prevent the seal 222 from being displaced under the action of water pressure and losing its sealing function. The seal 222 may be a flexible diaphragm, when the bypass tube 213 needs to be opened, the push rod 223 retracts and separates from the seal 222. The seal 222 moves toward a side distant from the bypass tube 213 or partially deforms under the water flow pressure in the bypass tube 213. A water flow channel is formed between the seal 222 and the bypass tube 213 to communicate the first water outlet 216 with the second water outlet 217. There are many ways for the actuator to drive the push rod 223 to achieve telescopic movement. For example, in some embodiments, the controller 220 is only a solenoid valve, which is conducive to miniaturization. Accordingly, the actuator may be a solenoid coil of the solenoid valve, and the push rod 223 is an iron core provided in the solenoid coil. When the solenoid coil is energized, the iron core is driven to move. In other embodiments, the actuator may also use other mechanical structures to drive the push rod 223 to perform telescopic movement.
In some embodiments, an extension part 219 is provided at a side of the first tube 211 distant from the bypass tube 213, and the extension part 219 is provided with an external port opposite to and communicated with the bypass tube 213. The valve body 210 further includes a seal plug detachably connected to the extension part 219, and the seal plug is used to open or block the external port.
It is understandable that the extension part 219 is a hollow cylindrical structure extending from the peripheral wall of the first tube 211 toward the side distant from the bypass tube 213, and the inner cavity of the extension part 219 forms an external port. When manufacturing the valve body 210, a drilling tool can be inserted into the valve body 210 through the external port to facilitate processing of a bypass flow channel of the bypass tube 213 inside the valve body 210. When the flow valve 200 is in normal use, the external port is blocked by a seal plug, which can prevent water in the valve body 210 from leaking from the external port. In addition, the external port can also be used as another communication port of the valve body 210. When it is necessary to communicate with other pipelines, the seal plug can be taken out from the external port to expand the quantity of communication ports of the valve body 210.
In order to ensure the sealing reliability between the seal plug and the extension part 219, in some embodiments, a seal ring is provided at the outer peripheral wall of the seal plug. When the seal plug seals the external port, the seal ring is squeezed and deformed to seal with the inner peripheral surface of the extension part 219.
In some embodiments, the flow valve 200 further includes a flow sensor provided at the first tube 211, and the flow sensor is used to detect the water inlet flow of the first tube 211. In some embodiments, the flow valve 200 further includes a temperature sensor provided at the first tube 211, and the temperature sensor is used to detect the water inlet temperature of the first tube 211.
It is understandable that the first tube 211 of the flow valve 200 can be used as an installation carrier for the flow sensor and/or the temperature sensor, so that the flow valve 200 has a higher degree of integration and more diversified functions. It is no longer necessary to install a flow sensor and/or a temperature sensor on the cold water input tube 23 of the water heater, which is conducive to reducing the quantity of parts to be assembled, improving assembly efficiency, and reducing costs. At the same time, it can also reduce the risk of water leakage caused by the assembly of parts. When the heat exchange system 10 is applied to a water heater, the installation position of the flow valve 200 can be set closer to the water inlet end of the cold water input tube 23 of the water heater (that is, replacing the original installation position of the flow sensor and/or temperature sensor), and the flow valve 200 is distant from the heat radiation area formed by the burner 21, so as to avoid the electronic elements integrated in the flow valve 200 from being damaged by heat radiation, and the service life of the flow valve 200 can be extended.
In some embodiments, the heat exchanger 100 and the flow valve 200 enclose an accommodation space for receiving the burner 21. It can be understood that the heat exchanger 100 includes a heat exchanger body 130 extending laterally, and a water inlet tube section 110 and a water outlet tube section 120 extending downward from the same side of the heat exchanger body 130, and the flow valve 200 is connected to the bottom ends of the water inlet tube section 110 and the water outlet tube section 120. The heat exchange system 10 entirely presents a similar inverted “L”-shaped structure, and the heat exchanger 100 and the flow valve 200 enclose a semi-open accommodation space, which can be used to receive the burner 21 of the water heater. When the heat exchange system 10 is applied to a water heater, the burner 21 is accommodated in the accommodation space, so that the burner 21 and the heat exchange system 10 are more compactly matched, which is conducive to full utilization of space and reduction of the overall volume of the water heater. At the same time, the high-temperature flue gas generated by the burner 21 flows upward and can fully contact with the heat exchanger body 130 located above for heat exchange, thereby improving the heating efficiency.
In some embodiments, the valve body 210 is provided with a connection part, and the connection part is used to connect and fix with the back plate of the water heater. It is understandable that when the heat exchange system 10 is applied to the water heater, the heat exchange system 10 is installed in the shell of the water heater, and the shell of the water heater includes a first side plate, a second side plate and a back plate connected between the first side plate and the second side plate, and the back plate is provided at the side of the water heater adjacent to the wall, and the back plate is used to connect and fix the water heater to the wall. The valve body 210 is connected and fixed to the back plate through the connection part, so that the flow valve 200 can be stably installed on the back plate, avoiding the flow valve 200 from shaking during the operation of the water heater, thereby ensuring the working reliability of the flow valve 200. The connection part can be provided at the first tube 211 or the bypass tube 213, and can also be provided at the first tube 211 and the bypass tube 213. In some embodiments, the connection part can also be provided at the second tube 212, the specific position of the communication part on the valve body 210 is not limited, and the communication part and the back plate are fixed in a manner including but not limited to the use of snap or fastener.
In some embodiments, the valve body 210 and the communication part are integrally formed, and the connection part is connected and fixed to the back plate by fasteners; and/or the valve body 210 and the communication part are plastic pieces. In this way, the valve body 210 and the communication part are integrally injection molded, so that the flow valve 200 is easy to manufacture and has a stable structure. In some embodiments, the connection part is integrally injection molded on one side of the valve body 210 adjacent to the back plate (for example, the peripheral side of the first tube 211), and the connection part and the back plate are correspondingly provided with assembly holes for fasteners (such as screws, or pins, etc.) to pass through. The connection part is connected and fixed to the back plate by fasteners, and the assembly is simple, convenient, stable and reliable.
The present application further provides a water heater, which includes the aforementioned heat exchange system 10. The specific structure of the heat exchange system 10 refers to the above-mentioned embodiment. Since the water heater adopts all the technical solutions of all the above-mentioned embodiments, it at least has all the effects brought by the technical solutions of the above-mentioned embodiments, which will not be described one by one here.
As shown in
For example, when the water heater is working normally, the controller 220 controls the closing of the bypass tube 213. At this time, the highest temperature in the heat exchange tube 140 of the heat exchanger 100 is the set temperature of the water heater. In this way, the risk of vaporization noise can be greatly reduced, the thermal efficiency of the heat exchanger 100 will not be affected, and the service life of the heat exchanger 100 can also be extended.
After the water supply to the water heater is stopped, the controller 220 controls the bypass tube 213 to be opened, and can close the bypass tube 213 within a few seconds of startup according to the actual working conditions. At this time, part of the cold water in the first tube 211 is transported to the water outlet tube section 120 through the bypass tube 213, and the cold water is mixed with the high-temperature water in the water outlet tube section 120, which can effectively reduce the temperature rise when the water supply is stopped. Since part of the cold water is diverted from the bypass tube 213, the water flow rate transported by the first tube 211 to the heat exchanger 100 is reduced, thereby reducing the undershoot at startup.
In addition, it is also possible to determine whether to open the bypass during normal combustion based on actual working conditions. For example, in winter, when the temperature difference between the inlet and outlet water is large and needs to be quickly heated to the set temperature, the controller 220 controls the bypass tube 213 to close, which not only improves the heating speed but also ensures that it can be heated to the set temperature. When the water is stopped and restarted, the bypass time can be reduced, thereby reducing undershoot. When a low-temperature bath is needed in summer, the controller 220 controls the bypass tube 213 to open. At this time, the minimum temperature rise of the water heater can be reduced to prevent the water temperature from being too hot during bathing, and the water temperature in the heat exchange tube 140 can be increased, thereby increasing the flue gas temperature and avoiding the risk of condensation water.
In addition, based on the structure of the above water heater, the present application further provides a method for controlling the water heater, including the following steps:
It is understandable that the water heater is a gas water heater. The water usage state of the water heater includes but is not limited to an initial water usage state, a subsequent water usage state, a water-off state, etc. The subsequent water usage state here means that the hot water of the previous water heater has reached the user's water use end, that is, the user has used hot water, or the water heater has undergone a preheating cycle. The subsequent water usage state within the first preset time means that, starting from the end of the previous water usage state of the water heater, within the first preset time period, the water in the heat exchanger 100 still has a certain temperature due to the previous use. When the water heater is started again and water is used, the hot water retained in the heat exchanger 100 will flow to the user's water use end. The previous water usage state of the water heater can be determined according to the shutdown signal sent by the sensor at the user's water outlet, or it can be determined according to the preheating completion signal of the water heater.
The subsequent water usage state can be determined according to the signal sent by the sensor at the water outlet of the user, or according to the water inlet detection signal of the water heater, or the water inlet signal sent by the water flow sensor. In this way, when it is determined that the water heater is in the subsequent water usage state, the bypass tube 213 will be opened, and the bypass ratio of the flow valve 200 will be in the range of 40% to 70%. The bypass time of the bypass tube 213 will be 2 seconds to 4 seconds, and then the bypass tube 213 will be closed. Such operation can reduce the start-stop temperature fluctuation range (the fluctuation range of the temperature overshoot and the temperature undershoot when the water heater is restarted), and reduce the constant temperature waiting time (the duration of the temperature overshoot and the temperature undershoot when the water heater is restarted), thereby achieving better start-stop constant temperature control of the water outlet temperature of the water heater. The value of the bypass ratio can be 40%, 50%, 60%, 70%, etc., which is not specifically limited here.
When the bypass ratio is too large, during the process of starting the water heater to heat, too much water will flow from the bypass tube 213 into the second tube 212, which will produce serious vaporization noise, reduce the thermal efficiency of the heat exchanger 100, affect the user experience, and affect the life of the heat exchanger 100. When the bypass ratio is too small, the amount of water flowing from the bypass tube 213 into the second tube 212 is too small to neutralize the high-temperature water in the second tube 212, which will cause the outlet water temperature of the water heater to be too high, that is, the water temperature rises when the water is stopped. When the water heater is restarted, a section of high-temperature water will flow out, and the high-temperature water may scald the user. The method for controlling the water heater of the present application can effectively improve the problems of start-stop constant temperature difference, high vaporization noise, low thermal efficiency, etc. of conventional water heaters by controlling the bypass ratio and bypass time.
In some embodiments, the method for controlling the water heater further includes:
It can be understood that, the water inlet flow rate being less than or equal to the first preset flow means that within the first preset flow, the water heater is determined to be in a water-off state, and the water-off state can be determined based on a water inlet detection signal or a water inlet signal sent by a water flow sensor. When the water heater is in a water-off state, the bypass tube 213 is opened so that when the water heater uses water again, the bypass tube 213 can immediately transport the cold water in the first tube 211 to the second tube 212 to mix with the hot water in the second tube 212. That is, before the water heater uses water again, the bypass tube 213 is opened in advance, and the bypass tube 213 does not have a valve opening delay problem, the static valve opening voltage of the bypass tube 213 is low, and the start-stop constant temperature effect of the water heater is good.
The water-off time of the water heater exceeds the second preset time, which means that the water-off time of the water heater is long, the water heater is determined to be in the water usage end state, and the user will not use the water heater again within a certain period of time. The second preset time can be 5 minutes, or 6 minutes, or 8 minutes, or 10 minutes, etc. In this way, the bypass tube 213 is closed to prevent the bypass tube 213 from being in the open state for a long time, causing the controller to heat up, thereby affecting the performance of the controller, that is, affecting the reliability of the flow valve. It can be seen that the embodiment of the present application is conducive to improving the service life of the flow valve.
The above descriptions are only some embodiments of the present application, and do not limit the scope of the present application. Under the inventive concept of the present application, equivalent structural transformations made using the contents of the description and drawings of the present application, or direct/indirect application in other related technical fields, are included in the scope of the present application.
| Number | Date | Country | Kind |
|---|---|---|---|
| 202311182031.9 | Sep 2023 | CN | national |
This application is a continuation application of International Application No. PCT/CN2024/104747, filed on Jul. 10, 2024, which claims priority to Chinese Patent Application No. 202311182031.9, filed on Sep. 13, 2023. The disclosures of the above-mentioned applications are incorporated herein by reference in their entireties.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/CN2024/104747 | Jul 2024 | WO |
| Child | 19025769 | US |
