JP2012088031A - Heat exchanger and sanitary washing device including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve heat transfer between a heating element and water, to decrease the surface temperature of the heating element and to reduce boiling noise, by increasing a flow velocity of water that flows in a flow passage formed between the heating element and a casing.SOLUTION: A heat exchanger 1, for heating water to produce hot water, includes: a heater 2 having a columnar outer shape and serving as a heating element to heat water; a case 3 covering the outer periphery of the heater 2 and forming a flow passage of the water heated by the heater 2, between an heater outer peripheral face 2c and the case; and a spring 11 and a spiral section 12, as a water flow regulating means which partitions the flow passage in a direction along the circumference direction of the heater 2 in an axial view of the heater 2, and regulates the flow in the axial direction of the heater 2 in the flow passage.

Description

  The present invention relates to a heat exchanger that heats water to make warm water, and a sanitary washing device that cleans a local part of a human body using hot water obtained thereby as washing water.

  Conventionally, as a heat exchanger that heats water to make warm water, a cylindrical heating element and a cylindrical case that accommodates the heating element are provided, and between the outer peripheral surface of the heating element and the inner peripheral surface of the case Some have a configuration for forming a flow path of water to be heated. Thus, the flow path formed between the heating element and the case is a flow path for sending water in the axial direction of the heating element. Such a heat exchanger is provided, for example, in a sanitary washing device for washing a local part of a human body, and is used to make washing water hot water.

  In the heat exchanger configured as described above, there is a problem that boiling noise is generated when water is excessively heated by the heating element. Such a boiling noise problem is caused by an excessive increase in the surface temperature of the heating element, and therefore tends to occur when the watt density of the heating element increases.

  Therefore, the problem of boiling noise becomes a more serious problem when the surface area of the heating element is reduced in order to reduce the size of the heat exchanger under the condition that the heating value of the heating element is constant. That is, when the heat generation amount of the heating element is constant, if the surface area of the heating element is reduced, the watt density is increased and a boiling sound is likely to be generated. In recent years, downsizing of heat exchangers has been remarkable, and for example, attempts have been made to reduce the length of the heating element to about half of the conventional length.

  In order to solve the problem of boiling noise, it is necessary to lower the surface temperature of the heating element. In order to lower the surface temperature of the heating element, it is important to improve heat transfer between the heating element and water. Therefore, conventionally, in the heat exchanger configured as described above, there is a technique of forming a spiral flow path between the heating element and the case in order to improve heat transfer between the heating element and water (for example, , Patent Document 1 and Patent Document 2).

  In Patent Document 1 and Patent Document 2, the spiral flow path is formed by fitting a metal member such as a spiral into the outer periphery of the heating element, or a portion on the inner peripheral surface side of the case. Thus, the space between the heating element and the case is formed by being spirally partitioned. When the space between the heating element and the case is not partitioned by the spiral flow path, that is, the flow path is formed as a substantially cylindrical space by the outer peripheral surface of the heating element and the inner peripheral surface of the case. In comparison with the flow channel flowing along the axial direction of the body, the flow channel area can be reduced and the flow rate of water can be increased. When the flow rate of water flowing around the heating element is increased, heat transfer between the heating element and water is improved.

JP 2005-171580 A JP-A-8-94175

  However, the conventional technique for forming a spiral flow path between the heating element and the case has the following problems. In the conventional technique, when an actual spiral channel is to be formed, the outer diameter of the heating element is between the member for forming the spiral channel, such as a spring, and the surface of the heating element. A gap is generated due to a dimensional tolerance or a dimensional tolerance of a spring. Such a gap generated between the member forming the spiral flow path and the surface of the heating element becomes conspicuous when the heating element is made of a material having a relatively large bend, dimensional tolerance or the like such as ceramic.

  Since there is a gap between the member that forms the spiral flow path and the surface of the heating element, the gap passes water, so the spiral flow along the member that forms the spiral flow path In addition, a phenomenon occurs in which a flow along the axial direction of the heating element is formed.

  Specifically, the flow path formed between the heating element and the case is a flow path for sending water heated by the heating element in the axial direction of the heating element. For this reason, the water flowing through the flow path formed between the heating element and the case inherently tends to flow along the axial direction of the heating element. The helical flow path as described above regulates the flow of water along the axial direction of the heating element and converts it into a helical flow along the circumferential direction of the heating element, thereby reducing the flow area and reducing the flow velocity. It is intended to increase. Therefore, as described above, a gap exists between the member forming the spiral flow path and the surface of the heating element, so that the flow of water along the axial direction of the heating element is sufficiently restricted in the spiral direction. Instead, a part of the water passes through the gap, so that a flow along the axial direction of the heating element is formed.

  As described above, in the conventional technique, in the flow path configuration aiming to form a spiral flow between the heating element and the case, the flow of water in the axial direction of the heating element along the surface of the heating element. The problem of “missing” occurs. Due to the occurrence of such a hollow-out problem, the effect of narrowing the channel area by forming a spiral channel cannot be obtained sufficiently, and it becomes difficult to increase the flow velocity. As a result, according to the prior art, the heat transfer between the heating element and water cannot be sufficiently increased to lower the surface temperature of the heating element, and the problem of boiling noise cannot be solved.

  The present invention has been made in view of the above circumstances, and the heat between the heating element and the water is increased by increasing the flow rate of the water flowing through the flow path formed between the heating element and the case. A heat exchanger capable of improving the transmission to lower the surface temperature of the heating element and reducing the boiling noise, and a sanitary washing device including the heat exchanger.

  The heat exchanger according to the present invention is a heat exchanger that warms water to make warm water, has a cylindrical outer shape, covers a heating element that heats water, and an outer periphery of the heating element. A case in which a flow path of water heated by the heating element is formed between an outer peripheral surface, the flow path is partitioned in a direction along a circumferential direction of the heating element in the axial direction of the heating element, and the flow path And a water flow restricting means for restricting the axial flow of the heating element. With such a configuration, the surface temperature of the heating element is lowered by improving the heat transfer between the heating element and the water by increasing the flow rate of the water flowing through the flow path formed between the heating element and the case. The boiling sound can be reduced.

  In the heat exchanger according to the present invention, preferably, the water flow restricting means is provided along a first restricting portion provided so as to protrude spirally along the outer peripheral surface of the heating element, and along the inner peripheral surface of the case. And a second restricting portion that is provided so as to protrude in a spiral shape and forms a spiral flow path together with the first restricting portion. With such a configuration, the surface temperature of the heating element can be lowered by improving the heat transfer by increasing the flow rate of the water flowing through the flow path formed between the heating element and the case. Since the axial flow can be effectively regulated, the boiling sound can be reduced.

  In the heat exchanger according to the present invention, preferably, the first restricting portion and the second restricting portion are at least partially overlapped in the axial direction of the heating element. With such a configuration, the axial flow of the heating element can be more reliably regulated, so that the surface temperature of the heating element can be effectively lowered and the effect of reducing boiling noise can be enhanced.

  In the heat exchanger according to the present invention, preferably, overlapping portions of the first restricting portion and the second restricting portion are in contact with each other. With such a configuration, the spiral flow path formed by the first restricting portion and the second restricting portion can be reliably held, and the boiling sound can be more effectively reduced.

  In the heat exchanger according to the present invention, preferably, the first restricting portion is in contact with the second restricting portion on the downstream side of the water flow path. With such a configuration, water in the spiral channel easily comes into contact with the first restricting portion, and turbulent flow is likely to occur in the spiral channel. It becomes easy to take the heat of the surface of the water, and the efficiency of heat transfer between the heating element and water can be effectively improved. Thereby, the surface temperature of a heat generating body can be lowered | hung more effectively and the reduction effect of a boiling sound can be heightened.

  In the heat exchanger according to the present invention, preferably, the first restricting portion is a winding spring having an inner diameter smaller than an outer diameter of the heating element, and is elastic in a state of being wound around an outer peripheral side of the heating element. Is fixed to the heating element. With such a configuration, the first restricting portion configured separately from the heating element can be attached to the heating element without a gap, and the axial flow of the heating element can be more reliably regulated.

  In the heat exchanger according to the present invention, it is preferable that the first restricting portion is formed integrally with the heating element. With such a configuration, parts for constituting the water flow regulating means can be omitted, so that the structure can be simplified and the heat exchanger can be easily assembled in a short time.

  In the heat exchanger according to the present invention, preferably, the heating element is assembled to the case by being inserted into the case in an axial direction of the heating element, and the first restricting portion includes: It is constituted by a winding spring that is separate from the heating element and has a spiral pitch wider than that of the second restricting portion, and the heating spring is assembled to the case so that the winding spring is The portion that is compressed in the axial direction of the heating element by the restricting portion and overlaps with the second restricting portion is held in a state of being pressed against the second restricting portion by the elasticity of the winding spring. is there. With such a configuration, it is possible to prevent the winding spring constituting the first restricting portion from shifting on the outer peripheral surface of the heating element due to the water pressure in the flow path, and to ensure a spiral flow velocity.

  In the heat exchanger according to the present invention, preferably, the water flow restricting means includes a plurality of annular plate members provided at intervals in the axial direction of the heating element so as to protrude in a radial direction of the heating element. The annular plate member is configured to be elastically deformed so as to be in close contact with the outer peripheral surface of the heating element and to have a notch for ensuring water flow in the flow path. With such a configuration, since the bending and dimensional tolerance of the heating element can be absorbed, the flow path can be reliably formed regardless of the bending and dimensional tolerance of the heating element.

  In the heat exchanger according to the present invention, preferably, the water flow restricting means is formed of an elastic body and has a cylindrical sheet member that is in close contact with the outer peripheral ends of the plurality of annular plate members. With such a configuration, the flow path can be reliably formed even when the heating element is inclined with respect to the case.

  In the heat exchanger according to the present invention, preferably, the water flow restriction means is formed in a spiral shape along the outer peripheral surface of the heating element, and is configured by a spiral member provided in a state of being wound around the heating element, The spiral member is provided in a plate-like radial direction portion formed along the radial direction of the heating element and an outer peripheral side end portion of the radial direction portion, and is formed along the circumferential direction of the heating element. A circumferential portion, and an inner circumferential end surface of the radial portion is brought into contact with an outer circumferential surface of the heating element, and an end portion of the circumferential portion is adjacent to the axial direction of the heating element. The flow path is partitioned into a spiral shape along the outer peripheral surface of the heating element. With such a configuration, the bending and dimensional tolerances of the heating element can be absorbed with a small number of parts, so the flow path can be reliably formed with a simple structure regardless of the bending or dimensional tolerance of the heating element. Can do.

  In the heat exchanger according to the present invention, preferably, the heating element is a sheathed heater, and the flow path includes a linear portion formed in a straight line and a curved portion formed in a curved shape. The water flow restricting means is provided at least in the curved portion. With such a configuration, the flow rate of the water flowing through the flow path can be increased even in the curved portion of the flow path where the length of the water contacting the heating element is different between the inner peripheral side and the outer peripheral side. The efficiency of heat transfer between water can be improved. Thereby, the surface temperature of a sheathed heater can be lowered | hung, generation | occurrence | production of bumping boiling can be suppressed and a boiling sound can be reduced. Further, when the heat exchanger is miniaturized by providing a curved portion in the sheathed heater, it is possible to effectively suppress bumping and generation of boiling noise in the curved portion of the outer peripheral flow path. Furthermore, by adopting a sheathed heater as a heating element, the characteristics of the sheathed heater can be obtained as an advantage.

  The sanitary washing device of the present invention includes the heat exchanger, and uses hot water generated by the heat exchanger as washing water, and discharges the washing water from a nozzle to wash a local part of the human body. With such a configuration, it is possible to reduce boiling noise in a heat exchanger that is uncomfortable for a user who receives local cleaning.

  According to the present invention, the surface temperature of the heating element is lowered by improving the heat transfer between the heating element and the water by increasing the flow rate of the water flowing through the flow path formed between the heating element and the case. The boiling sound can be reduced.

Sectional drawing which shows the structure of the heat exchanger which concerns on 1st embodiment of this invention. 1 is a partially cutaway cross-sectional perspective view showing a configuration of a heat exchanger according to a first embodiment of the present invention. The elements on larger scale of the water flow control means which concern on 1st embodiment of this invention. The figure which shows the structure of the comparative example which concerns on 1st embodiment of this invention. The figure which shows an example of the relationship between the spring position and heater surface temperature which concern on 1st embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 2nd embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 3rd embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 4th embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 5th embodiment of this invention. The partial cross section figure which shows the structure of the heat exchanger which concerns on 5th embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 6th embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 7th embodiment of this invention. The figure which shows the structure of the spring which concerns on 7th embodiment of this invention. Explanatory drawing about the manufacturing method of the heat exchanger which concerns on 7th embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 8th embodiment of this invention. The elements on larger scale of the water flow control means which concern on 8th embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 9th embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 10th embodiment of this invention. The figure which shows the structure of the metal ring which concerns on 10th embodiment of this invention. (A) is a front view, (b) is XX sectional drawing in (a). Sectional drawing which shows the structure of the heat exchanger which concerns on 11th embodiment of this invention. The figure which shows the structure of the metal ring which concerns on 11th embodiment of this invention. The figure which shows the modification of a structure of the metal ring which concerns on 11th embodiment of this invention. (A) is a front view, (b) is the Y arrow partial enlarged view in (a). Sectional drawing which shows the structure of the heat exchanger which concerns on 12th embodiment of this invention. Sectional drawing which shows the structure of the heat exchanger which concerns on 13th embodiment of this invention. The figure which shows the structure of the bush which concerns on 13th embodiment of this invention. (A) is a front view, (b) is a ZZ sectional view in (a). Sectional drawing which shows the structure of the heat exchanger which concerns on 14th embodiment of this invention. Sectional drawing which shows the other structure of the heat exchanger which concerns on 14th embodiment of this invention. The perspective view which shows the example of application of the sanitary washing apparatus which concerns on one Embodiment of this invention. The block diagram which shows the structure of the sanitary washing apparatus which concerns on one Embodiment of this invention.

  The present invention provides a flow along the axial direction of a heating element in a flow path in a configuration in which a flow path is formed between an outer peripheral side of a heating element having a cylindrical outer shape and an inner peripheral side of a case housing the heating element. Is intended to increase the flow velocity, improve the heat transfer between the heating element and water, lower the surface temperature of the heating element, and reduce the boiling noise. Embodiments of the present invention will be described below.

  A first embodiment of the present invention will be described with reference to FIGS. 1 and 2. The heat exchanger 1 according to the present embodiment warms water to make warm water. For example, it is installed in a sanitary washing device that is installed in a toilet bowl or the like to wash a local part of a human body, and the washing water is used as warm water. Used.

  As shown in FIGS. 1 and 2, the heat exchanger 1 includes a heater 2 as a heating element and a case 3 that accommodates the heater 2. The heat exchanger 1 has a water inlet 4 formed by the heater 2 and a water outlet 5 formed by the case 3. In other words, in the heat exchanger 1, the water flowing in from the water inlet 4 is warmed by the heater 2 and becomes warm water and flows out from the water outlet 5.

  The heater 2 has a cylindrical outer shape and heats water. The heater 2 has a cylindrical outer shape by being configured in a pipe shape. The heater 2 is assembled to the case 3 by being inserted into the case 3 from the axial direction (left-right direction in FIG. 1, hereinafter referred to as “heater axial direction”). The heater 2 has a flange portion 2a that partially expands the diameter of the pipe-shaped heater 2 in the middle of the heater axial direction. The heater 2 is accommodated in a state where a portion on the one side (right side in FIG. 1) of the flange portion 2 a in the heater axial direction is inserted into the case 3.

  The heater 2 is a so-called ceramic pipe heater, and generates heat from the inner peripheral surface (hereinafter referred to as “heater inner peripheral surface”) 2b and the outer peripheral surface (hereinafter referred to as “heater outer peripheral surface”) 2c. The water passing through the side and the outer peripheral side is heated. In the heater 2, a belt-like heater pattern made of tungsten or the like is formed along the heater axial direction by printing or the like inside an exterior portion formed of ceramic. The water inlet 4 of the heat exchanger 1 is formed by the opening at the end opposite to the side inserted into the case 3 of the heater 2 configured in a pipe shape.

  The case 3 is made of resin, metal, or the like, has a substantially rectangular parallelepiped outer shape as a whole, and has an inner peripheral surface portion formed as a substantially circumferential surface. The case 3 includes a case main body 3a that forms a space for accommodating the heater 2, and a lid 3b that covers an opening formed on one end side of the case main body 3a.

  The case body 3a is a substantially cylindrical member that has a substantially rectangular parallelepiped outer shape and is open at both ends in the longitudinal direction. One opening of the case body 3a is closed by the lid 3b. The lid 3b is a plate-like member having a shape along the outer shape of the case main body 3a, and is fixed to the opening end surface of the case main body 3a with a bolt or the like, thereby constituting the case 3 integrally with the case main body 3a. . The lid 3b is watertightly fixed to the internal space of the case body 3a by an O-ring 6 interposed between the opening end surface of the case body 3a and the lid 3b.

  The heater 2 is inserted into the case 3 and assembled from the opening on the side opposite to the side closed by the lid 3b of the case body 3a. The heater 2 is assembled to the case 3 by fixing the flange portion 2 a to the opening end surface of the case main body 3 a constituting the case 3 with a fastener such as a bolt. The flange portion 2 a is formed in a substantially rectangular plate shape corresponding to the outer shape of the case 3. At the four corners of the flange portion 2a, hole portions 2d through which fasteners for fixing to the case body 3a are passed are formed. The heater 2 is watertightly fixed to the internal space of the case 3 by an O-ring 7 interposed between the flange portion 2a and the opening end surface of the case main body 3a.

  In a state where the heater 2 is assembled to the case 3 by the flange portion 2a, there is a gap between the tip of the heater 2 and the inner surface of the lid 3b. That is, the opening of the heater 2 on the side accommodated in the case 3 opens in the case 3 without being blocked by the lid 3b.

  Thus, the case 3 covers the outer periphery of the heater 2 in a state where the portion on the insertion side with respect to the case 3 is inserted with respect to the flange portion 2 a of the heater 2. The water discharge port 5 included in the heat exchanger 1 is formed on the peripheral wall portion of the case body 3 a constituting the case 3. The water discharge port 5 is provided in the vicinity of the opening end on the opposite side to the side on which the lid 3b of the case body 3a is attached. In the present embodiment, the water discharge port 5 opens the internal space of the case main body 3a upward.

  The case 3 forms a flow path of water heated by the heater 2 between the outer peripheral surface 2c of the heater. Hereinafter, the flow path formed between the heater outer peripheral surface 2c and the case 3 is referred to as an “outer peripheral flow path”. The heater outer peripheral surface 2 c is an outer peripheral surface in the cylindrical outer shape of the heater 2. The case 3 into which the heater 2 is inserted has an inner peripheral surface portion formed as a substantially circumferential surface. Therefore, an outer peripheral flow path is formed between the heater outer peripheral surface 2c and the inner peripheral surface portion of the case 3 facing each other.

  In the heat exchanger 1 having the above-described configuration, the water flowing in from the water inlet 4 flows while being heated in the internal flow path of the heater 2 formed by the heater inner peripheral surface 2b (FIG. 1, arrow A1). See), and discharged from the open end of the internal flow path of the heater 2 into the internal space of the case 3. Then, water discharged from the internal flow path of the heater 2 into the internal space of the case 3 is transported to the opposite side in the heater axial direction by the outer peripheral flow path while being heated by the heater outer peripheral surface 2 c and discharged from the water outlet 5. Is done.

  The heat exchanger 1 according to the present embodiment partitions the outer peripheral side flow path in a direction along the circumferential direction of the heater 2 (hereinafter referred to as “heater circumferential direction”) as viewed in the heater axial direction, and the heater in the outer peripheral side flow path. Water flow restricting means for restricting the axial flow is provided.

  In the heat exchanger 1, the outer peripheral flow path is formed as a flow path for flowing water in a direction along the heater circumferential direction by being partitioned in a spiral shape or in a direction perpendicular to the heater axial direction. That is, with respect to the water flow regulating means, in order to partition the outer peripheral side flow path in the direction along the heater circumferential direction, the outer peripheral side flow path is partitioned in a spiral manner, and the outer peripheral side flow path is perpendicular to the heater axial direction. Includes partitioning. However, the outer peripheral flow path may be partitioned in a direction along the heater circumferential direction as viewed in the heater axial direction, and the partitioning method is not particularly limited.

  As described above, the water flow restricting means forms a flow in the direction along the heater circumferential direction, such as a spiral flow, in the outer side flow path by partitioning the outer circumferential flow path in the direction along the heater circumferential direction. Therefore, in the configuration in which the flow in the direction along the heater circumferential direction is formed by partitioning the outer peripheral flow path by the water flow regulating means, the flow along the heater axial direction is maintained as long as the flow in the direction along the heater circumferential direction is maintained. Directional flow is regulated.

  Therefore, the water flow restricting means restricts the flow in the heater axial direction in the outer peripheral flow path by holding the flow in the direction along the heater circumferential direction. Specifically, the water flow restricting means includes a gap between the inner peripheral side and the heater outer peripheral surface 2c on the inner peripheral side, and an inner peripheral surface portion of the case 3 on the outer peripheral side. The flow in the direction along the circumferential direction of the heater is maintained by being provided without a gap therebetween. That is, the water flow restricting means forms a flow in the direction along the heater circumferential direction so that the outer side passage is not visible through the outer circumference side channel when viewed from the heater axial direction.

  As described above, the heat exchanger 1 includes the water flow restricting means for partitioning the outer peripheral flow path in the direction along the heater circumferential direction as viewed in the heater axial direction and for restricting the flow in the heater axial direction in the outer peripheral flow path. By increasing the flow rate of the water flowing through the outer peripheral flow path, the heat transfer between the heating element and the water can be improved, the surface temperature of the heater 2 can be lowered, and the boiling noise can be reduced. Hereinafter, the specific form of a water flow control means is demonstrated.

  As shown in FIG. 1 and FIG. 2, the heat exchanger 1 of the present embodiment includes a spring 11 that is externally fitted to the heater 2 and a spiral portion 12 that is provided on the inner periphery of the case 3 as water flow restricting means. Have.

  The spring 11 is a wire formed in a spiral shape as a winding spring. As the spring 11, a spring having a relatively thin wire diameter (for example, a wire diameter of about 0.8 mm) is used. The spring 11 is provided in a state where it is mounted over substantially the entire portion of the heater 2 inserted into the case 3.

  The spring 11 is fitted on the heater 2 in a state of being in close contact with the heater outer peripheral surface 2c. Specifically, as the spring 11, one having an inner diameter smaller than the outer diameter of the heater 2 is used. When the spring 11 is attached to the heater 2, the spring 11 is twisted in the direction opposite to the spiral direction to enlarge the inner diameter of the spring 11, and the spring 11 is put on the heater 2 in that state. By releasing the torsion, the spring 11 returns due to elasticity and comes into close contact with the heater outer peripheral surface 2c. Here, the one where the wire diameter of the spring 11 is smaller adheres more securely to the heater outer peripheral surface 2c.

  As described above, in the heat exchanger 1 of the present embodiment, the spring 11 is attached to the heater 2 in close contact with the heater outer peripheral surface 2c so as to protrude spirally along the heater outer peripheral surface 2c. A first restricting portion is provided. That is, in the present embodiment, the spring 11 attached to the heater 2 constitutes a first restricting portion included in the water flow restricting means. The spring 11 is fixed to the heater 2 by an elastic force while being wound around the outer peripheral side of the heater 2.

  The spiral portion 12 forms a spiral groove portion 12 a in the inner peripheral surface portion of the case 3 with the heater axis direction as the central axis direction of the turning direction. In other words, the spiral portion 12 forms, on the inner peripheral surface portion of the case 3, a spiral protrusion 12 b whose heater axis direction is the central axis direction of the turning direction. Accordingly, the spiral portion 12 appears as a plurality of tooth-like portions in a cross-sectional view in a direction passing through the central axis of the heater 2 as shown in FIG.

  The spiral portion 12 is formed such that the spiral winding number and pitch are substantially the same as the spring 11 winding number. And the spiral part 12 is formed so that the spiral groove part 12a may be along with the spring 11 of the state wound around the heater 2. FIG. The spiral portion 12 is formed so that the width of the spiral groove portion 12 a is wider than the wire diameter of the spring 11. The spiral portion 12 and the spring 11 wound around the heater 2 divide the outer peripheral flow path into a spiral shape, thereby forming a spiral flow path.

  Thus, in the heat exchanger 1 of the present embodiment, the spiral portion 12 formed on the inner peripheral surface portion of the case 3 is provided so as to protrude spirally along the inner peripheral surface of the case 3, and the spring 11 and the 2nd control part which forms a helical flow path are comprised. That is, in the present embodiment, the spiral portion 12 formed on the inner peripheral side of the case 3 constitutes a second restricting portion included in the water flow restricting means.

  Desirably, at least a part of the spring 11 and the spiral portion 12 constituting the water flow regulating means overlap when viewed in the heater axial direction. Specifically, as shown in FIG. 3, the spiral protrusion 12b forming the spiral portion 12 has a clearance (dimension B1) with respect to the heater outer peripheral surface 2c. On the other hand, the wire diameter B2 of the spring 11 provided in close contact with the heater outer peripheral surface 2c is larger than the clearance (B1) between the spiral protrusion 12b and the heater outer peripheral surface 2c.

  For this reason, the spring 11 and the spiral portion 12 are arranged so that the outer peripheral end of the spring 11 is located on the outer side (upper side in FIG. 3) of the inner end face of the spiral projection 12b. It has a part that overlaps in the direction. That is, the spring 11 and the spiral portion 12 are equivalent to the length (B3 = B2-B1) in the radial direction of the heater 2 from the position of the end face of the spiral projection 12b to the position of the outer peripheral end of the spring 11. It has a part that overlaps in the direction.

  According to the heat exchanger 1 of the present embodiment having the above-described configuration, the spiral flow in the direction along the circumferential direction of the heater is held by the water flow restricting means configured by the spring 11 and the spiral portion 12. The flow in the heater axial direction in the outer peripheral channel is reliably regulated.

  Specifically, in the water flow regulating means provided in the outer peripheral side flow path, there is no gap on the inner peripheral side because the spring 11 is in close contact with the heater outer peripheral surface 2c. Moreover, about the outer peripheral side, since the spiral part 12 is a part integrally formed in the case 3, there is no gap. And since the spring 11 and the spiral part 12 have a part which mutually overlaps as mentioned above, the clearance gap in the heater axial direction view does not exist between the spring 11 and the spiral part 12 either.

  In addition, as a desirable form, the gap between the spring 11 and the spiral portion 12 as viewed in the heater axial direction does not exist, that is, the spring 11 and the spiral portion 12 overlap when viewed in the heater axial direction. Although configured, there is no problem if the gap between the spring 11 and the spiral portion 12 is a minute gap (for example, B1≈B2) that can regulate the flow in the heater axial direction.

  As described above, according to the water flow restricting means constituted by the spring 11 and the spiral portion 12, the flow in the heater axial direction can be more reliably restricted, so that the spiral flow is maintained, and the spiral flow path By forming the film, it is possible to sufficiently obtain the effect of narrowing the channel area, and to increase the flow velocity. As a result, the efficiency of heat transfer can be sufficiently increased, the surface temperature of the heater 2 can be effectively lowered, and the effect of reducing boiling noise can be enhanced.

  Moreover, the heat exchanger 1 of this embodiment has the following advantages. By making the wire diameter of the spring 11 constituting the water flow restricting means thinner, even if the heater 2 has a bend, it is possible to easily follow the bend and adhere to the heater 2. Similarly, by reducing the wire diameter of the spring 11, the inner diameter can be easily widened by twisting the spring 11 in the direction opposite to the winding direction, and the spring 11 can be smoothly covered with the heater 2. By releasing the twist in the reverse direction, the spring 11 can be easily adhered to the heater 2. That is, by reducing the wire diameter of the spring 11, the spring 11 can be easily brought into close contact with the heater 2 by elastic deformation of the spring 11.

  Further, by reducing the wire diameter of the spring 11, the secondary moment of section of the spring 11 can be reduced. Therefore, even when the heater 2 is thermally deformed, the spring 11 can be easily deformed by heat. The heater 2 can be prevented from cracking or breaking. Furthermore, since the spring 11 can be easily produced by a wire material that is widely distributed in general, the water flow regulating means can be produced at low cost. The spring 11 preferably has a wire diameter sufficiently smaller than the outer diameter of the heater 2 (about 1/10 of the outer diameter of the heater 2 at most) in relation to the heater 2 having a cylindrical outer shape. Used.

  In addition, by forming the spiral portion 12 constituting the water flow regulating means as a part of the case 3, it is possible to reliably prevent a gap from being generated between the spiral portion 12 and the case 3. Similarly, by forming the spiral portion 12 as a part of the case 3, the pitch of the spiral between the spring 11 and the spiral portion 12 is made substantially the same, so that the heater 2 with the spring 11 attached can be spirally wound. The case 3 having the portion 12 can be assembled like a screw, and productivity can be improved.

  Moreover, in the heat exchanger 1 of this embodiment, since the heat of the heater 2 can be transmitted to water through the spring 11 that is in close contact with the heater 2, the temperature of the heater 2 can be effectively reduced. That is, the heat transfer area of the heater 2 can be widened by the spring 11 that is in close contact with the heater 2, and the heat transfer of the heat exchanger 1 can be improved. Accordingly, a material having a relatively high thermal conductivity such as copper, stainless steel, or aluminum is employed as the material constituting the spring 11.

  Moreover, in the heat exchanger 1 of this embodiment, it is preferable that the overlapping part of the spring 11 and the spiral part 12 is mutually contacting. In this embodiment, the part where the spring 11 and the spiral part 12 overlap is a part where the wire constituting the spring 11 enters the spiral groove part 12a.

  As shown in FIG. 3, the spring 11 has a substantially circular cross-sectional shape and is in close contact with the surface of the heater outer peripheral surface 2c. Therefore, when the wire diameter (B2) of the spring 11 is larger than the clearance dimension B1 between the spiral protrusion 12b and the heater outer peripheral surface 2c, the wire constituting the spring 11 is brought into contact with the spiral portion 12. be able to. In the present embodiment, the spring 11 is in contact with the spiral groove 12a on the side opposite to the lid 3b in the heater axial direction.

  In this manner, the overlapping portions of the spring 11 and the spiral portion 12 come into contact with each other, so that the spiral flow path formed by the spring 11 and the spiral portion 12 can be reliably held. Thereby, it is possible to reliably obtain the effect of narrowing the channel area by forming the spiral channel, and to increase the flow velocity. As a result, the boiling sound can be reduced more effectively.

  Further, as a mode of contact between the spring 11 and the spiral portion 12 that are in contact with each other, the spring 11 is located on the downstream side of the outer circumferential side channel with respect to the spiral portion 12 as in the heat exchanger 1 of the present embodiment. It is preferably in contact. In the present embodiment, as described above, the spring 11 that contacts the spiral groove portion 12a on the opposite side of the lid 3b in the heater axial direction contacts the spiral portion 12 on the downstream side in the outer circumferential channel. Yes.

  Specifically, in the heat exchanger 1 of the present embodiment, the direction of water flow in the outer peripheral flow path is a direction along the heater axial direction, and corresponds to the left-right direction in FIGS. 1 and 3. In this heater axial direction, the upstream side of the outer peripheral flow path is the side (right side in FIGS. 1 and 3) where the case body 3a having openings at both ends is closed by the lid 3b, and the outer peripheral flow path The downstream side is the side opposite to the upstream side, that is, the side where the case body 3a is closed by the flange portion 2a of the heater 2 (the left side in FIGS. 1 and 3). Therefore, the spring 11 is in contact with the spiral portion 12 at the downstream side in the outer circumferential side flow path. This means that the spring 11 is opposite to the spiral portion 12 from the lid 3b in the heater axial direction view. It is that it contacts on the flange portion 2a side.

  Specifically, as shown in FIG. 3, the groove portion 12 a formed in the spiral portion 12 is an upstream side wall surface 12 c that is an upstream surface in the outer peripheral flow path and a downstream surface in the outer peripheral flow path. And a downstream side wall surface 12d. That is, as shown in FIG. 3, the upstream side wall surface 12 c and the downstream side wall surface 12 d of the spiral groove 12 a have a center of the heater 2 in which the spiral protrusions 12 b appear as a plurality of tooth-like portions as described above. In cross-sectional view in the direction passing through the shaft, it appears as a wall surface facing the heater shaft direction between adjacent tooth-shaped portions.

  When attention is paid to the spiral protrusion 12b constituting the spiral portion 12, the upstream side wall surface 12c is a downstream surface in the outer peripheral flow path, and the downstream side wall surface 12d is an upstream surface in the outer peripheral flow path. Become. Further, when the upstream side wall surface 12c formed in the spiral protrusion 12b is a surface on one side in the heater axial direction, the downstream side wall surface 12d is the other side surface in the heater axial direction.

  In this manner, the spring 11 is preferably provided in contact with the downstream side wall surface 12d with respect to the spiral portion 12 having the upstream side wall surface 12c and the downstream side wall surface 12d. The spring 11 constituted by the wire has a wire diameter B2 smaller than the width dimension of the groove 12a in the spiral portion 12, that is, the interval B4 between the upstream side wall surface 12c and the downstream side wall surface 12d facing each other. Therefore, as described above, the spring 11 having a portion that enters the spiral groove 12a is in the heater axial direction from the position in contact with the upstream side wall surface 12c to the position in contact with the downstream side wall surface 12d in the heater axial direction. It can be located in the range.

  In this way, in the configuration in which the spring 11 can be positioned at a different position within a predetermined range in the heater axial direction with respect to the spiral portion 12, the spring 11 is downstream of the spiral portion 12 in the outer peripheral flow path. It is preferable to be provided at a position in contact with the downstream side wall surface 12d of the spiral portion 12 in the heater axial direction. In other words, the spring 11 is preferably provided in a state in which the spring 12 is in contact with the downstream side wall surface 12d which is the upstream surface of the protrusion 12b with respect to the protrusion 12b of the spiral portion 12.

  In this way, the spring 11 contacts the spiral portion 12 on the downstream side of the outer peripheral flow path, so that the water in the spiral flow path formed by the spring 11 and the spiral portion 12 contacts the spring 11. It becomes easy to remove water from the heater outer peripheral surface 2 c through the spring 11. Further, since the water in the spiral channel easily comes into contact with the spring 11, turbulent flow is likely to occur in the spiral channel, and the water in the channel takes the heat of the heater outer peripheral surface 2c. It becomes easy. From these things, the efficiency of the heat transfer between the heater 2 and water can be improved effectively. Thereby, the surface temperature of the heater 2 can be lowered more effectively, and the effect of reducing the boiling sound can be enhanced.

  Regarding the relative position of the spring 11 with respect to the spiral portion 12 in the heater axial direction, the position where the spring 11 contacts the spiral portion 12 on the downstream side in the outer peripheral flow path as in the heat exchanger 1 of the present embodiment is preferable. This will be described with reference to a comparative example for the example in the present embodiment (referred to as “this example”).

  Here, as a comparative example with respect to the present embodiment shown in FIG. 3, as shown in FIG. 4A, when the spring 11 is in a position in contact with the spiral portion 12 on the upstream side in the outer peripheral flow path (“ (Referred to as “first comparative example”), and when the spring 11 is at the center position in the heater axial direction with respect to the groove 12a of the spiral portion 12 as shown in FIG. ). That is, in the first comparative example, the spring 11 is provided in contact with the upstream side wall surface 12c of the spiral portion 12, and in the second comparative example, the spring 11 is provided with the upstream side wall surface 12c and the downstream side wall surface of the spiral portion 12. It is provided in a state in which it does not contact any of 12d and is in a central position between the upstream side wall surface 12c and the downstream side wall surface 12d.

  FIG. 5 shows an example of the measurement results of the temperature (heater surface temperature) [° C.] of the heater outer peripheral surface 2c under the same conditions for the present example, the first comparative example, and the second comparative example. That is, the graph G1 shown in FIG. 5 represents the relationship between the relative position (spring position) in the heater axial direction with respect to the spiral portion 12 of the spring 11 and the heater surface temperature.

  As shown in FIG. 5, the heater surface temperature decreases in the order of the first comparative example, the second comparative example, and the present embodiment. In the case of this measurement result, in the first comparative example, the heater surface temperature is about 140 ° C. (see measurement point P1), and in the second comparative example, the heater surface temperature is about 130 ° C. (see measurement point P2). In contrast to these comparative examples, the heater surface temperature is as low as about 126 ° C. in this example.

  As described above, since the heater surface temperature of the present embodiment is lower than that of the comparative example, as described above, the effect that the surface temperature of the heater 2 can be effectively lowered is obtained. In the example, it can be said that the water in the spiral channel is more likely to come into contact with the spring 11 and turbulence is more likely to occur than in the comparative example. And from the graph G1 of FIG. 5, the heater surface temperature is higher in the first comparative example where the spring position is the upstream position in the outer peripheral flow path than in the second comparative example. Therefore, it can be said that the effect that the water in the spiral channel easily comes into contact with the spring 11 and the turbulent flow is likely to be obtained as the spring position is located more downstream in the outer channel. .

  As described above, from the measurement result of the heater surface temperature using the comparative example, with respect to the spring position, as in the heat exchanger 1 of the present embodiment, the spring 11 is on the downstream side in the outer circumferential side flow path with respect to the spiral portion 12. It has been demonstrated that the location of contact is preferred.

  Furthermore, in the heat exchanger 1 of the present embodiment, the following configuration is preferably employed. The heater 2 is assembled to the case 3 by being inserted in the heater axial direction parallel to the direction of the turning center of the spiral flow path with respect to the case 3. In such an assembly configuration of the heater 2 and the case 3, the helical pitch of the spring 11, which is a winding spring configured separately from the heater 2, is configured to be wider than the helical pitch of the spiral portion 12. . In other words, the length of the spring 11 is such that the natural length of the spring 11 is longer than the length of the spiral portion 12 in the heater axial direction in the relationship between the spring 11 and the spiral portion 12 that have substantially the same number of turns of the spiral. Is set. That is, in this case, the spring 11 functions as a compression spring.

  As described above, in the configuration in which the spring 11 functions as a compression spring, when the heater 2 is assembled to the case 3, the spring 11 is pressed against the spiral portion 12 and the pitch is adjusted (aligned with the spiral pitch of the spiral portion 12). However, the heater 2 is inserted into the case 3. Therefore, when the heater 2 is assembled to the case 3, the spring 11 is compressed in the heater axial direction by the spiral portion 12 and is pressed against the spiral portion 12 by the elasticity of the spring 11 at a portion overlapping the spiral portion 12. It is held in the state.

  Here, since the spring 11 and the spiral portion 12 have a portion that overlaps in the heater axial direction, when the heater 2 is assembled to the case 3, the heater 2 with the spring 11 attached is attached to the case 3. On the other hand, it is inserted while being rotated like a screw.

  Thus, by providing the spring 11 as a compression spring and pressing the spring 11 against the spiral portion 12 by the elasticity of the spring 11, the spring 11 is displaced on the heater outer peripheral surface 2c by the water pressure in the outer peripheral flow path. Is prevented, and a spiral flow rate can be secured.

  A second embodiment of the present invention will be described with reference to FIG. In each embodiment described below, the same reference numerals are used for the same components as those in the first embodiment, and the description thereof is omitted as appropriate. The heat exchanger 20 of the present embodiment has the same function as the water flow regulating means provided in the outer flow path in the internal flow path of the pipe-like heater 2 in comparison with the heat exchanger 1 of the first embodiment. It differs in that a configuration that fulfills the above is provided.

  Specifically, as shown in FIG. 6, the heat exchanger 20 of the present embodiment is inserted into the heater 2 along the heater axial direction from the opening on the insertion side of the heater 2 with respect to the case 3. It has the column-shaped axial part 21 provided. The shaft portion 21 is supported in a state of being coaxially arranged with the heater 2 by fixing one end side to the inner surface of the lid 3b.

  A first spring 22 is attached to the outer peripheral surface of the shaft portion 21. A second spring 23 is attached to the heater inner peripheral surface 2b so as to face this. The first spring 22 and the second spring 23 are both winding springs, and the number of turns and the pitch are substantially the same.

  The first spring 22 and the second spring 23 are provided in close contact with the outer peripheral surface of the shaft portion 21 and the heater inner peripheral surface 2b, respectively. Specifically, the first spring 22 has an inner diameter smaller than the outer diameter of the shaft portion 21. And when attaching the 1st spring 22 to the axial part 21, the internal diameter of the 1st spring 22 is expanded by twisting the 1st spring 22 in the reverse direction to the spiral direction, and the 1st spring 22 is in that state. By covering the shaft portion 21 and releasing the torsion of the first spring 22, the first spring 22 returns due to elasticity and is in close contact with the outer peripheral surface of the shaft portion 21.

  Here, since both the shaft portion 21 and the first spring 22 are made of metal or resin, it is possible to manufacture with less dimensional tolerances and bends, so that a process such as twisting the first spring 22 is not performed. In addition, the shaft portion 21 and the first spring 22 can be assembled without causing a gap between the shaft portion 21 and the first spring 22.

  Further, as the second spring 23, one having an outer diameter larger than the inner diameter of the heater 2 is used. When the second spring 23 is attached to the heater 2, the outer diameter of the second spring 23 is reduced by twisting the second spring 23 in the direction opposite to the spiral direction, and the second spring 23 is in that state. Is inserted into the heater 2 and the torsion of the second spring 23 is released, so that the second spring 23 is elastically returned and closely contacts the heater inner peripheral surface 2b.

  Desirably, the first spring 22 and the second spring 23 are provided so that at least a part thereof is overlapped when viewed in the heater axial direction by selecting the wire diameter of each spring. In the present embodiment, the wire diameter of the second spring 23 provided on the heater 2 side is smaller than the wire diameter of the first spring 22 provided on the shaft portion 21 side. Here, from the viewpoint of preventing the flow rate of water along the surface of the heater inner peripheral surface 2b from decreasing, it is preferable that the second spring 23 provided on the heater 2 side is in close contact with the heater inner peripheral surface 2b. As the two springs 23, one having a relatively thin wire diameter that is easily brought into close contact with the heater inner peripheral surface 2b is used.

  As described above, in the heat exchanger 20 of the present embodiment, the flow path formed by the outer peripheral surface of the shaft portion 21 and the heater inner peripheral surface 2b is spirally formed by the first spring 22 and the second spring 23. A spiral flow path is formed. In other words, the configuration including the shaft portion 21, the first spring 22, and the second spring 23 in the heat exchanger 20 has a spiral flow path when viewed from the heater axial direction, in the same manner as the water flow restricting means provided in the outer peripheral flow path. And the flow in the heater axial direction in the flow path is restricted.

  Thus, by providing the water flow restricting means also in the heater 2, heat transfer between the heating element and water can be improved by increasing the flow velocity of the internal flow path of the heater 2. In the present embodiment, the first spring 22 and the second spring 23 are used as members separate from the shaft portion 21 or the heater 2 in order to form a spiral flow path inside the heater 2. However, it is not limited to this. That is, the spiral flow path configured in the heater 2 may be formed by a portion provided integrally with the shaft portion 21 or the heater 2.

  A third embodiment of the present invention will be described with reference to FIG. As compared with the heat exchanger 1 of the first embodiment, the heat exchanger 30 of the present embodiment is a spring 31 that forms a first restricting portion that forms a spiral flow path in the outer peripheral flow path. The difference is that a spring with a square cross section is used.

  As shown in FIG. 7, the heat exchanger 30 according to the present embodiment includes a spring 31 having a square cross section attached to the heater outer peripheral surface 2 c and a spiral portion 12 formed on the inner peripheral surface portion of the case 3. A spiral channel is formed in the channel. The spiral member constituting the spring 31 has a plate-like shape with the heater axial direction as the plate thickness direction.

  Therefore, as shown in FIG. 7, the shape of the spring 31 in a cross-sectional view in the direction passing through the central axis of the heater 2 is a rectangular shape whose longitudinal direction is the radial direction of the heater 2. The plate thickness of the spring 31 is smaller than the width of the spiral groove 12a forming the spiral portion 12.

  Thus, by using the spring 31 having a square cross section as a member constituting the first restricting portion, the radial length of the angular cross section of the spring 31 is increased, so that the spring 31 and the spiral portion 12 are overlapped. You can take a big bill. Thus, even when the heater 2 is tilted with respect to the case 3 when the heater 2 is assembled to the case 3 or when the heater 2 itself is bent, the overload between the spring 31 and the spiral portion 12 can be avoided. The wrap portion can be easily secured.

  Further, the spring 31 having a square cross section has a smaller secondary moment when compared with the spring having a circular cross section when the radial dimension is the same as that of the spring 11 of the first embodiment, for example. Therefore, it becomes easy to bend and attach to the heater 2 while being elastically deformed. Similarly, in comparison with the circular cross section, the spring 31 having a square cross section can easily have a large surface area, so that the heat transfer area of the heater 2 can be widened by the spring 31 closely contacting the heater 2, The heat transfer of the exchanger 30 can be improved.

  A fourth embodiment of the present invention will be described with reference to FIG. As compared with the heat exchanger 1 of the first embodiment, the heat exchanger 40 of the present embodiment is a spring 41 that constitutes a first restricting portion that forms a spiral flow path in the outer peripheral flow path. The difference is that a spring having an L-shaped cross section is used.

  As shown in FIG. 8, the heat exchanger 40 of the present embodiment includes an L-shaped spring 41 attached to the heater outer peripheral surface 2 c and a spiral portion 12 formed on the inner peripheral surface portion of the case 3. A spiral channel is formed in the side channel. The spiral member constituting the spring 41 protrudes radially outward from the peripheral wall portion 41a formed in a plate shape along the heater outer peripheral surface 2c and from one end side (right end side in FIG. 6) of the peripheral wall portion 41a. The flange portion 41b is formed, and the cross-sectional shape is L-shaped.

  Therefore, as shown in FIG. 8, the spring 41 having an L-shaped cross section brings the peripheral wall portion 41 a into contact with the heater outer peripheral surface 2 c and the flange portion 41 b in the radial direction of the heater 2 when attached to the heater 2. Project in a bowl shape toward the outside. Further, the plate thickness dimension of the flange portion 41 b of the spring 41 that partially protrudes into the groove portion 12 a of the spiral portion 12 is smaller than the width dimension of the groove portion 12 a of the spiral portion 12.

  Thus, by using the L-shaped spring 41 as a member constituting the first restricting portion, the heat transfer area from the heater 2 can be expanded, and the heat transfer of the heat exchanger 40 can be improved. it can. In particular, by increasing the width (dimension in the heater axial direction) of the peripheral wall 41a, which is a portion in contact with the heater outer peripheral surface 2c, the heat transfer area can be efficiently expanded.

  A fifth embodiment of the present invention will be described with reference to FIGS. 9 and 10. As compared with the heat exchanger 1 of the first embodiment, the heat exchanger 50 of the present embodiment is a spring 51 that constitutes a first restricting portion that forms a spiral flow path in the outer peripheral flow path. A difference is that a spring having a thin plate shape in an oblique direction in contact with the outer peripheral surface 2c of the heater is used.

  As shown in FIGS. 9 and 10, the heat exchanger 50 of the present embodiment includes an obliquely wound spring 51 mounted on the heater outer peripheral surface 2 c and a spiral portion 12 formed on the inner peripheral surface portion of the case 3. A spiral channel is formed in the outer peripheral channel. The helical member constituting the spring 51 is a thin plate-like member, and is formed so that each circular portion (one rotation in the helical shape) in the helical shape becomes a part of a substantially conical shape in which the diameter reduction direction is aligned. Is done.

  Therefore, as shown in FIG. 9 and FIG. 10, the obliquely wound spring 51 is attached to the heater 2 with the tip on the diameter-reduced side of a part of the substantially conical shape of each spiral portion in the spiral shape. It is made to contact the outer peripheral surface 2c. 9 differs from FIG. 10 in that the portion including the heater 2 and the spring 51 is shown in cross section.

  In this way, by using the obliquely wound spring 51 as a member constituting the first restricting portion, for example, compared with the spring 31 having a square cross section in the third embodiment, the spring 41 having an L-shaped cross section in the fourth embodiment, and the like Thus, the sectional moment of inertia can be reduced. Further, if the sectional moment of inertia is large, the allowable bending stress is easily exceeded when the inner diameter of the spring is expanded beyond the maximum outer diameter of the heater 2 for mounting on the heater 2. Therefore, according to the obliquely wound spring 51 according to the present embodiment, the secondary moment of section can be reduced, and the inner diameter can be easily changed when the heater 2 is mounted.

  In the above-described second to fourth embodiments and the present embodiment, the spiral pitch of the springs constituting the spiral flow path is set from the spiral pitch of the spiral portion 12 as in the first embodiment. It is also possible to apply a configuration in which the springs 31, 41, 51 are compression springs. Thus, when the heater 2 is assembled to the case 3, the spring is compressed in the heater axial direction by the spiral portion 12 and is pressed against the spiral portion 12 by the elasticity of the spring at a portion overlapping the spiral portion 12. Held in a state.

  A sixth embodiment of the present invention will be described with reference to FIG. The heat exchanger 60 of the present embodiment differs from the heat exchanger 1 of the first embodiment in that a portion constituting the first restricting portion is formed integrally with the heater 2. That is, in the above-described embodiment, the first restricting portion is configured by the spring 11 or the like which is a separate member from the heater 2, whereas in the present embodiment, the first restricting portion is formed by a part of the heater 2. It is configured.

  As shown in FIG. 11, in the heat exchanger 60 of this embodiment, the helical protrusion 61 which is a helical protrusion part is formed in the heater outer peripheral surface 2c. The spiral protrusion 61 protrudes in a plate shape in the radial direction of the heater 2. The spiral protrusion 61 is substantially the same in the number of turns and the pitch of the spiral in relation to the spiral portion 12. Further, the width dimension (the thickness dimension) of the spiral protrusion 61 is smaller than the width dimension of the spiral groove 12 a forming the spiral portion 12.

  The spiral protrusion 61 can be formed by, for example, winding a ceramic sheet-like member formed in a spiral shape around the main body of the heater 2 and sintering it. However, the method of forming the spiral protrusion 61 on the heater 2 is not particularly limited.

  As described above, the first restricting portion that forms the spiral flow path with the spiral portion 12 is provided as the spiral protrusion 61 integral with the heater 2, thereby omitting components for configuring the water flow restricting means. Therefore, the structure can be simplified, and the heat exchanger can be easily assembled in a short time. That is, when the first restricting portion is configured by a member different from the heater 2 such as the spring 11 or the like, a step of attaching the spring 11 to the heater 2 is required in the heat exchanger assembly process. According to the heat exchanger 60 of the present embodiment, since the first restricting portion is integral with the heater 2, the process can be omitted and the time for assembling the heat exchanger can be shortened.

  A seventh embodiment of the present invention will be described with reference to FIG. In the heat exchanger 70 of the present embodiment, in comparison with the heat exchanger 1 of the first embodiment, the portion constituting the second restricting portion is formed by a member separate from the case housing the heater 2. Is different. That is, in the above-described embodiment, the second restricting portion is provided as the spiral portion 12 that is a part of the case 3, whereas in the present embodiment, a member separate from the case that houses the heater 2, A second restricting portion is configured.

  As shown in FIG. 12, the heat exchanger 70 of this embodiment includes a case 73 that houses the heater 2. The case 73 includes a substantially cylindrical case main body 73a having an inner peripheral surface 73c, and a lid 73b that closes an opening on one end side of the case main body 73a. And the heat exchanger 70 of this embodiment is provided with the spiral cylinder 71 as a member which comprises a 2nd control part. In other words, in the heat exchanger 70 of the present embodiment, the spiral flow path is formed in the flow path on the outer peripheral side by the spring 11 attached to the heater outer peripheral surface 2 c and the spiral cylinder 71.

  The heat exchanger 70 of the present embodiment includes a case main body 73a constituting the case 73, and a portion of the spiral portion 12 provided on the inner peripheral surface portion of the case 3 in the heat exchanger 1 of the first embodiment (see FIG. 1). Is provided as a separate spiral cylinder 71. In other words, the heat exchanger 70 of the present embodiment has a configuration in which the portion of the spiral portion 12 in the heat exchanger 1 of the first embodiment is separated from the case body 73a as a spiral cylinder 71 that is a substantially cylindrical member. Have.

  Therefore, the spiral cylinder 71 has the spiral part 72 similar to the spiral part 12 in the above-described embodiment on the inner peripheral side. That is, the spiral portion 72 forms a spiral groove 72 a and a protrusion 72 b in the inner peripheral surface portion of the spiral cylinder 71 with the heater axis direction being the central axis direction of the turning direction. Accordingly, the spiral portion 72 appears as a plurality of tooth-like portions in a cross-sectional view in a direction passing through the central axis of the heater 2 as shown in FIG. The spiral portion 72 and the spring 11 wound around the heater 2 divide the outer peripheral flow path into a spiral shape, thereby forming a spiral flow path.

  The spiral cylinder 71 is moved by a relative approaching / separating direction (left-right direction in FIG. 12) in a state in which the cylinder axis directions coincide with each other in the relationship with the substantially cylindrical case main body 73a constituting the case 73. The case body 73a can be inserted and removed. The spiral cylinder 71 is housed in a state in which the spiral cylinder 71 is fitted to the case main body 73a so as to be relatively movable in the insertion / removal direction. That is, the outer peripheral surface 71a of the spiral cylinder 71 becomes a sliding surface with respect to the inner peripheral surface 73c of the case main body 73a.

  Therefore, the outer peripheral surface 71a of the spiral cylinder 71 and the inner peripheral surface 73c of the case main body 73a have a common shape when viewed in the cylinder axis direction. Thereby, the spiral cylinder 71 is positioned in the surface direction perpendicular to the cylinder axis direction in a state of being inserted into the case main body 73a.

  For example, when the shape of the outer peripheral surface 71a of the spiral cylinder 71 is a rectangular shape when viewed in the cylinder axis direction like the outer peripheral surface of a quadrangular prism, the shape of the inner peripheral surface 73c of the case body 73a is also the outer peripheral surface of the spiral cylinder 71. In order to match the shape and size of 71a, the shape is rectangular when viewed in the cylinder axis direction. Further, when the shape of the outer peripheral surface 71a of the spiral cylinder 71 is circular as viewed from the cylinder axis direction like the outer peripheral surface of the cylinder, the shape of the inner peripheral surface 73c of the case body 73a is also the outer peripheral surface 71a of the spiral cylinder 71. In order to match the shape and size of the cylinder, it is circular when viewed in the cylinder axis direction.

  Further, the spiral cylinder 71 has an outlet hole portion 75 for allowing a spiral flow path formed by the spiral portion 72 and the spring 11 to communicate with the water discharge port 5 of the case 73. The outlet hole 75 is provided so as to communicate with the water discharge port 5 in a state where the spiral cylinder 71 is accommodated in the case 73. The outlet hole 75 is a part that forms a hole having the same diameter as the water outlet 5, for example.

  The heat exchanger 70 of the present embodiment is the same as the heat exchanger 1 of the first embodiment except that the portion that forms a spiral flow path with the spring 11 wound around the heater 2 is separate from the case 73. It has the same configuration as. For this reason, description is abbreviate | omitted about the part which is common in the heat exchanger 1 of 1st embodiment.

  As in the heat exchanger 70 of this embodiment, the assembly of the heat exchanger 70 is provided by providing a spiral cylinder 71 having a spiral portion 72 that forms a spiral flow path together with the spring 11 separately from the case 73. Can be improved. Moreover, since the spiral cylinder 71 can be taken out from the case 73, the maintenance of the spiral portion 72 and the like forming the spiral flow path can be easily performed.

  In the above-described second to sixth embodiments and this embodiment, as in the case of the first embodiment, the overlapping portions of the portion constituting the first restricting portion and the spiral portion 12 are brought into contact with each other. By applying the configuration, the boiling sound can be effectively reduced as described above. Further, as in the case of the first embodiment, a configuration is adopted in which the members constituting the first restricting portion such as the spring 11 are in contact with the second restricting portion on the downstream side in the outer circumferential side flow path. Thus, the water in the flow path can easily take the heat of the heater outer peripheral surface 2c, and the efficiency of heat transfer between the heater 2 and water can be effectively improved, so that the surface temperature of the heater 2 is more effective. Therefore, the effect of reducing the boiling sound can be enhanced.

  An example of a method for manufacturing the heat exchanger 70 of the present embodiment will be described together with a preferable configuration of the spring 11. FIG. 13 shows an example of the configuration of the spring 11. FIG. 13B is a view taken along arrow E1 in FIG. 13A, and FIG. 13C is a view taken along arrow E2 in FIG.

  As described above, the spring 11 is a wire formed in a spiral shape as a winding spring. As shown in FIGS. 13A and 13B, the spring 11 has a fixed portion 11a at the end on one end side. The fixed portion 11a is a linear portion in which the end portion of the wire forming the spring 11 is bent inward so as to follow the radial direction in the cylindrical outer shape of the spring 11.

  Further, as shown in FIGS. 13A and 13C, the spring 11 has a hooking portion 11b at an end on the other end side, that is, an end opposite to the side where the fixing portion 11a is provided. The hook portion 11 b is a portion in which the end portion of the wire forming the spring 11 extends in the tangential direction in the cylindrical outer shape of the spring 11.

  An example of a manufacturing method of the heat exchanger 70 including the spring 11 having such a configuration will be described with reference to FIG. In the manufacturing method of the heat exchanger 70, first, the spring 11 is attached to the heater 2 as shown in FIG. When the spring 11 is attached to the heater 2, the diameter of the spring 11 is expanded by a predetermined jig.

  Specifically, the spring 11 is mounted on a predetermined jig and receives a force that increases the diameter. The spring 11 mounted on the jig is fixed by a fixing portion 11a (see FIG. 13). That is, in the jig, the one end side of the spring 11 is fixed by fixing and fixing the portion 11a. In a state where the spring 11 is fixed in the jig, the diameter of the spring 11 is expanded by rotating the spring 11 in the direction opposite to the winding direction (spiral direction) by the hook portion 11b (see FIG. 13). . In the example shown in FIG. 13, the diameter of the spring 11 is expanded by rotating the hook portion 11 b in the clockwise direction in FIG. The spring 11 is held in a state where the diameter is expanded in the jig.

  Thus, the heater 2 is inserted into the spring 11 whose diameter is expanded by the jig. That is, the portion of the heater 2 on the side inserted into the case 73 relative to the flange portion 2a is inserted into the spring 11 in an expanded state. After the heater 2 is inserted into the spring 11, the spring 11 is released from the state where it is spread by the jig. That is, the state in which the spring 11 is rotated in the direction opposite to the winding direction is returned. As a result, as shown in FIG. 14A, the spring 11 is elastically returned and wound around the heater 2 and is in close contact with the heater outer peripheral surface 2c. And the heater 2 with which the spring 11 was mounted | worn is removed from a jig | tool.

  Next, as shown in FIG. 14B, the spiral cylinder 71 is set in the heater 2 to which the spring 11 is attached. The spring 11 and the spiral portion 72 overlap with each other when viewed from the heater axial direction, or the outer peripheral end of the spring 11 and the inner peripheral end of the spiral portion 72 are substantially at the same position. For this reason, as for the relationship between the spring 11 and the spiral portion 72, the inner diameter of the protrusion 72 b of the spiral portion 72 is smaller than the outer diameter of the spring 11, or the protrusion between the outer peripheral end of the spring 11 and the spiral portion 72. The protruding end surface of the portion 72b comes into contact.

  For this reason, the spiral cylinder 71 is mounted while inserting the heater 2 into the heater 2 to which the spring 11 is mounted, and rotating with the central axis direction (straight line F1) as the rotation axis direction (arrows F2, F3). reference). As the spiral cylinder 71 rotates, the spiral cylinder 71 inserts the heater 2 in a state where the spring 11 enters the groove 72 a of the spiral portion 72. As described above, when the spiral cylinder 71 is rotated and attached to the heater 2, even when the pitch of the spring 11 is somewhat varied when the spring 11 is attached to the heater 2, the spring 11 is spiraled. By entering the groove 72 a of the portion 72, the pitch of the spring 11 is corrected to some extent along the spiral shape of the spiral portion 72.

  As shown in FIG. 14C, the spiral cylinder 71 is attached to the heater 2 with its end surface 71 b in contact with the flange portion 2 a of the heater 2. The spiral cylinder 71 is further rotated about a half turn from the state in contact with the flange portion 2 a of the heater 2. That is, the spiral cylinder 71 is idled by about a half turn with the end face 71b in contact with the flange portion 2a.

  Due to the idle rotation of the spiral cylinder 71, the protrusion 72 b of the spiral portion 72 faces the spring 11, and the spring position in the groove portion 72 a of the spiral portion 72 is on the flange portion 2 a side of the heater 2. That is, as shown in FIG. 14 (d), the spring 11 comes into contact with the protrusion 72 b of the spiral portion 72 on the downstream side in the outer peripheral flow path.

  Specifically, when the end surface 71b of the spiral cylinder 71 comes into contact with the flange portion 2a of the heater 2, the spring position in the groove portion 72a of the spiral portion 72 is the center position or the upstream side in the outer peripheral flow path (the tip of the heater 2). Even if it is in the position of the side), by projecting the spiral cylinder 71, the projection 72b of the spiral portion 72 will pick up the spring 11, and the spring position in the groove portion 72a of the spiral portion 72 is the outer peripheral flow path. It moves to the downstream side (flange portion 2a side). The correction of the pitch of the spring 11 in the process in which the spiral cylinder 71 is mounted on the heater 2 while rotating as described above is a pitch correction to such an extent that the spring 11 is accommodated in the groove portion 72a of the spiral portion 72. By performing the idle rotation of the spiral cylinder 71 as described above, most of the spring 11 is pressed against the spiral portion 72 on the downstream side (flange portion 2a side) of the outer circumferential side flow path in the groove portion 72a. The appearance of the spring 11 is further corrected.

  When performing the idle rotation of the spiral cylinder 71, the heater 2 and the spiral cylinder 71 are arranged so that the outlet hole 75 is in a position communicating with the water discharge port 5 in a state where the spiral cylinder 71 is accommodated in the case 73. The relative position with respect to the rotation direction is confirmed. That is, the relative position in the rotation direction of the heater 2 and the spiral cylinder 71 is adjusted so that the spout 5 is not blocked by the peripheral wall of the spiral cylinder 71 by inserting the spiral cylinder 71 into the case 73. .

  After the spiral rotation of the spiral cylinder 71 with respect to the heater 2 is performed as described above, the assembly of the heater 2 and the spiral cylinder 71 is inserted into the case 73 as shown in FIG. That is, as described above, the relationship between the heater 2 and the spiral cylinder 71 in the relationship between the spiral cylinder 71 and the case main body 73a that can be inserted and removed by movement in the relative approaching and separating directions with the cylinder axis directions aligned with each other. The assembly is inserted from the spiral cylinder 71 side into the opening on the side opposite to the side closed by the lid 83b of the case body 73a (see arrow F4).

  After the assembly of the heater 2 and the spiral cylinder 71 is inserted into the case 73, the flange portion 2a of the heater 2 is fixed to the opening end surface of the case main body 73a of the case 73 by a fastener such as a bolt, It is assembled to the case 73. Thereby, as shown in FIG.14 (f), the heat exchanger 70 is completed.

  The heater 2 and the case 3 are sealed by an O-ring 7 interposed between the flange portion 2a and the opening end surface of the case main body 73a. For this reason, the spiral cylinder 71 is configured such that its outer diameter is smaller than the outer diameter of the flange portion 2 a of the heater 2. That is, since the assembly of the heater 2 and the spiral cylinder 71 uses the flange portion 2a as a portion that sandwiches the O-ring 7 between the case body 73a while inserting the spiral cylinder 71 into the case 73, it has been described above. As described above, the outer diameter of the spiral cylinder 71 that forms the outer peripheral surface 71a serving as a sliding surface with respect to the inner peripheral surface 73c of the case body 73a is made smaller than the outer diameter of the flange portion 2a.

  According to the heat exchanger 70 of this embodiment capable of performing the manufacturing method as described above, assembly can be easily performed. In the heat exchanger 70, for example, other parts such as a thermal fuse are assembled to the case 73, and other parts such as a wire harness are attached to the heater 2. For this reason, when the heat exchanger 70 is assembled, it is difficult to rotate the case 73 and the heater 2, and workability is reduced. In this regard, as in the heat exchanger 70 of the present embodiment, a portion that forms a spiral flow path together with the spring 11 is provided as a spiral cylinder 71 separate from the case 73, so that the case 73 and the heater 2 can be provided. Parts can be assembled by a simple operation such as rotating the spiral cylinder 71 with respect to the heater 2 without rotating, and the heat exchanger 70 can be easily assembled.

  Moreover, in the manufacturing method of the heat exchanger 70 as described above, the fixing portion 11a of the spring 11 is fixed to a predetermined jig in a state where the spring 11 is assembled to the spiral cylinder 71, and the spring 11 is fixed by the hooking portion 11b. May be rotated in the direction opposite to the winding direction (spiral direction) to widen the diameter of the spring 11 and then the heater 2 may be inserted into the spring 11. As described above, the diameter of the spring 11 is increased by increasing the diameter of the spring 11 in a state where the spring 11 is assembled to the spiral cylinder 71 in advance (the state where the spring 11 is accommodated 1: 1 in the groove portion 72a of the spiral cylinder 71). The deformation (variation) of the pitch of the spring 11 can be prevented, and the heater 2 can be assembled while the pitch of the spring 11 is maintained. That is, by assembling the spring 11 into the spiral cylinder 71 in advance and then inserting the heater 2 into the spring 11, a change in the pitch of the spring 11 is regulated by the groove 72 a of the spiral cylinder 71. It is possible to avoid a situation in which a portion that does not fit or a portion in which two windings overlap is generated.

  An eighth embodiment of the present invention will be described with reference to FIGS. 15 and 16. In the heat exchanger 80 of the present embodiment, as in the seventh embodiment, the portion constituting the second restricting portion is formed of a member separate from the case that houses the heater 2.

  As shown in FIGS. 15 and 16, the heat exchanger 80 of the present embodiment includes a case 83 that houses the heater 2. The case 83 includes a substantially cylindrical case main body 83a having an inner peripheral surface 83c, and a lid 83b that closes an opening on one end side of the case main body 83a. And the heat exchanger 80 of this embodiment is provided with the winding spring 81 as a member which comprises a 2nd control part. That is, in the heat exchanger 80 of the present embodiment, the outer circumferential side flow path is spirally partitioned by the spring 11 attached to the heater outer peripheral surface 2c and the winding spring 81, and a spiral flow path is formed. .

  The winding spring 81 is a spiral member and is a very thin plate-like winding spring. The winding spring 81 is provided such that the central axis direction thereof coincides with the heater axial direction. That is, as shown in FIG. 15, the winding spring 81 is provided outside the heater outer peripheral surface 2 c on which the portion of the heater 2 located in the case 83 is inserted and the spring 11 is mounted.

  As shown in FIGS. 15 and 16, the winding spring 81 is plate-shaped so that the shape in a cross-sectional view in the direction passing through the central axis of the heater 2 is a rectangular shape whose longitudinal direction is the radial direction of the heater 2. It is comprised by the member of. The winding spring 81 is preferably as thin as possible as long as it has a strength necessary for a member that forms a spiral flow path. As shown in FIG. 16, the plate thickness dimension K1 of the winding spring 81 is smaller than, for example, the wire diameter B2 (see FIG. 3) of the spring 11 attached to the heater outer peripheral surface 2c.

  For example, the winding spring 81 is provided in a state of being attached to the inner peripheral surface portion of the case 83. In this case, specifically, a winding spring 81 having an outer diameter in a natural state larger than the inner diameter of the inner peripheral surface 83c of the case 83 is employed. Then, the outer diameter of the winding spring 81 is reduced by twisting the winding spring 81 in the direction opposite to the spiral direction, and the winding spring 81 is inserted into the case 83 in this state. Thereafter, by releasing the torsion of the winding spring 81, the winding spring 81 returns due to elasticity and comes into close contact with the inner peripheral surface 83c of the case 83 and is attached to the inner peripheral surface portion of the case 83.

  As shown in FIGS. 15 and 16, in the heat exchanger 80 of the present embodiment, a guide portion 82 is provided on the inner peripheral surface portion of the case 83. The guide portion 82 is a guide portion for keeping the pitch of the winding spring 81 separate from the case 83 constant.

  Specifically, the guide portion 82 is a portion formed on the inner peripheral surface 83c of the case 83, and is a spiral protrusion having the heater axis direction as the central axis direction of the turning direction. Therefore, the guide part 82 appears as a plurality of tooth-like portions in a cross-sectional view in a direction passing through the central axis of the heater 2 as shown in FIG.

  The guide portion 82 is formed so that the spiral winding number and pitch are substantially the same as the spring 11 winding number. And the guide part 82 guides the winding spring 81 by restrict | limiting the movement to the downstream (left side in FIG. 15 and FIG. 16) in the outer peripheral side flow path of the winding spring 81 which is a helical member.

  As shown in FIG. 16, in a state where the winding spring 81 is guided by the guide portion 82, a plate-like winding spring is placed on the guide surface 82 a that is the upstream surface in the outer peripheral flow path of the guide portion 82 in the heater axial direction. One plate surface 81a of 81 comes into contact. That is, the winding spring 81 is provided in a state in which the pitch of the spiral is kept substantially constant along the spiral shape of the guide portion 82 by bringing one plate surface 81 a into contact with the guide surface 82 a of the guide portion 82.

  As in the heat exchanger 80 of the present embodiment, the second restricting portion that forms a spiral flow path together with the spring 11 and the like is configured by a winding spring 81 that is a separate member from the case 83. It is possible to easily reduce the width dimension (dimension in the heater axial direction) of the second restricting portion which is a spiral projecting portion. It is preferable from the following viewpoint that the width dimension of a 2nd control part is small.

  The second restricting portion that forms the spiral flow path is configured to restrict the flow in the heater axial direction in the outer peripheral flow path together with the spring 11 and the like, and so on. It is provided so as to have a gap. For this reason, when the width dimension of the second restricting portion is large, the scale, underwater dust, and the like caused by heat generation are easily clogged between the second restricting portion and the heater outer peripheral surface 2c.

  For example, in the heat exchanger 1 of the first embodiment shown in FIG. 3, the heater outer peripheral surface 2c of the protrusion 12b increases as the width dimension B5 of the protrusion 12b constituting the spiral portion 12 serving as the second restriction portion increases. The gap between the end surface 12e and the heater outer peripheral surface 2c (see the broken line ellipse indicated by reference numeral H1) is likely to be clogged with scales and dust. In the gap between the end surface 12e of the protrusion 12b and the heater outer peripheral surface 2c, water does not pass through a portion clogged with scales or dust, so that heat accumulates in the vicinity of the heater outer peripheral surface 2c.

  As described above, when heat is partially accumulated in the vicinity of the heater outer peripheral surface 2c, a temperature difference of water occurs between the portion where the heat is accumulated and another portion such as the inside of the heater 2, for example. Such a temperature difference of water around the heater 2 causes a thermal shock that induces cracking of the heater 2.

  From such a viewpoint, it is preferable that the width of the protrusion 12b constituting the spiral portion 12 is small. That is, if the width of the protrusion 12b is small, scales and dust are less likely to be clogged in the gap between the end surface 12e of the protrusion 12b and the heater outer peripheral surface 2c, and a temperature difference around the heater 2 is less likely to occur.

  And in order to make the width dimension of a 2nd control part small, like the heat exchanger 80 of this embodiment, the structure which uses the 2nd control part as the coiled spring 81 different from the case 83 is suitable. Adopted. That is, according to the heat exchanger 80 of the present embodiment, the plate thickness of the winding spring 81 (see FIG. 16, dimension K1) is directly used as the width of the second restricting portion. By doing so, the width dimension of the second restricting portion can be easily reduced.

  Further, in the configuration including a winding spring 81 that is a separate member from the case 83 as a member constituting the second restricting portion as in the heat exchanger 80 of the present embodiment, a guide portion 82 for guiding the winding spring 81 is provided. As a result, the pitch of the winding springs 81 can be kept constant. Thereby, in the spiral flow path, the flow of water along the spiral can be stabilized, and the thermal efficiency can be improved. However, with respect to the guide portion 82, from the viewpoint of preventing the clogging of the scale and dust at the outer peripheral portion of the heater 2 as described above, the guide portion 82 has a sufficient gap between the heater outer peripheral surface 2c. In comparison with the size of the rectangular longitudinal direction (vertical direction in FIG. 16) which is the cross-sectional shape of the winding spring 81, the winding spring 81 is formed as a portion slightly protruding from the inner peripheral surface 83c of the case 83.

  In the present embodiment, as in the case of the first embodiment, by applying a configuration in which overlapping portions of the spring 11 and the winding spring 81 constituting the first restricting portion are in contact with each other, the above-described configuration is applied. As described above, the boiling sound can be effectively reduced. Moreover, the structure which the spring 11 which comprises a 1st control part contacts the downstream in an outer peripheral side flow path with respect to the winding spring 81 which comprises a 2nd control part similarly to the case of 1st embodiment. By applying, it becomes easy for the water in the flow path to take away the heat of the heater outer peripheral surface 2c, and the efficiency of heat transfer between the heater 2 and water can be effectively improved. Can be reduced more effectively, and the effect of reducing boiling noise can be enhanced.

  For example, in the heat exchanger 80 of the present embodiment, as shown in FIG. 16, the spring 11 is in contact with the winding spring 81 on the downstream side in the outer peripheral flow path, that is, the winding spring in the heater axial direction. 81 is preferably provided at a position in contact with the other plate surface 81b. In other words, the spring 11 is preferably provided in contact with the plate surface 81b that is the upstream surface of the winding spring 81.

  Moreover, in the heat exchanger 80 of this embodiment, the guide part 82 provided in the inner peripheral surface part of the case 83 is different from the case 83 like the spiral cylinder 71 provided in the heat exchanger 70 of the seventh embodiment. It can be constituted by a member. By adopting such a configuration, the heat exchanger 80 is manufactured by the following manufacturing method, for example. Hereinafter, a member constituting the guide portion 82 as a member different from the case 83 is referred to as a “spiral guide member”. The spiral guide member is a member configured in a substantially cylindrical shape, and has the guide portion 82 in the above-described embodiment on the inner peripheral side.

  In the manufacturing method of the heat exchanger 80, the spiral guide member and the winding spring 81 are assembled by inserting the winding spring 81 into the spiral guide member while being rotated. Here, for example, as described above, a winding spring 81 having an outer diameter larger than the inner diameter of the inner peripheral surface 83c of the case 83 is employed, and the winding spring 81 is in close contact with the inner peripheral surface 83c of the case 83 by elasticity. In this state, it is attached to the inner peripheral surface portion of the case 83.

  And as a manufacturing method of the heat exchanger 80 of this embodiment, in the manufacturing method of the heat exchanger 70 of 7th Embodiment mentioned above, the spiral cylinder 71 is replaced with the assembly of the spiral guide member and the winding spring 81. FIG. Is adopted. That is, in the manufacturing method of the heat exchanger 80 of the present embodiment, the assembly of the spiral guide member and the winding spring 81 is set in the heater 2 to which the spring 11 is attached, and the idling is performed. The assembly of the heater 2, the spiral guide member, and the winding spring 81 is assembled into the case 83 by being inserted into the case 83 and fixed. Thereby, the heat exchanger 80 of this embodiment is completed.

  By adopting the above-described configuration and manufacturing method in the heat exchanger 80 of the present embodiment, assembling can be easily performed as in the case of the seventh embodiment. Further, since the spiral guide member can be taken out from the case 83, maintenance of the guide portion 82 and the like included in the spiral guide member can be easily performed.

  A ninth embodiment of the present invention will be described with reference to FIG. The heat exchanger 90 according to the present embodiment is different from the heat exchanger 1 according to the first embodiment in that a spiral flow path is formed without using the inner peripheral portion of the case that accommodates the heater 2. That is, in the above-described embodiment, the spiral portion 12 formed on the inner peripheral surface portion of the case 3 is used as the second restricting portion constituting the water flow restricting means, whereas in the present embodiment, on the heater 2 side. A water flow control means is comprised only by the structure provided.

  Specifically, as shown in FIG. 17, the case 93 provided in the heat exchanger 90 of the present embodiment includes a case main body 93a having an inner peripheral surface 93c and a lid that closes an opening on one end side of the case main body 93a. 93b. And the heat exchanger 90 of this embodiment forms a helical flow path with the helical member 91 with which the heater 2 is mounted | worn. That is, in the heat exchanger 90 of the present embodiment, the water flow restricting means is formed by a spiral member 91 that is formed in a spiral shape along the heater outer peripheral surface 2 c and is provided in a state of being wound around the heater 2.

  The spiral member 91 is provided at a plate-like radial portion 91a formed along the radial direction of the heater 2 and an outer peripheral side end of the radial portion 91a, and is formed along the circumferential direction of the heater. And a circumferential portion 91b, and the cross-sectional shape is L-shaped. The radial portion 91a is a plate-like portion having the heater axial direction as the plate thickness direction. The circumferential direction portion 91b is a plate-like portion formed so as to protrude from the outer peripheral side end portion of the radial direction portion 91a in a direction perpendicular to the radial direction portion 91a (heater axial direction).

  The spiral member 91 makes the end on the side of the radial portion 91a of the L-shaped cross-sectional shape in contact with the heater outer peripheral surface 2c, and the end on the side of the circumferential portion 91b of the L-shaped cross-sectional shape. , Contact the back side (the side opposite to the side from which the circumferential portion 91b protrudes, the right side in FIG. 17) of the radial portion 91a of the adjacent circumferential portion located on one side (left side in FIG. 17) in the heater axial direction. . That is, as shown in FIG. 17, the spiral member 91 makes the inner peripheral end surface 91c of the radial direction portion 91a contact the heater outer peripheral surface 2c, and the end surface 91d of the circumferential direction portion 91b is adjacent to the circumferential portion of the heater in the axial direction. The outer peripheral flow path is partitioned into a spiral shape along the heater outer peripheral surface 2c.

  In other words, the spiral member 91 is in contact with the heater outer peripheral surface 2c by the radial portion 91a and is in contact with the circumferential portion adjacent to the heater axial direction by the circumferential portion 91b (the same angle in the rotational direction in the spiral shape). In a state where the portions of the two are in contact with each other. Here, the spiral member 91 has an inner diameter smaller than the outer diameter of the heater 2 as in the spring 11 of the first embodiment, and is expanded by elastic deformation to the heater outer peripheral surface 2c. Provided in close contact.

  Thereby, the heater outer peripheral surface 2c, the surface 91e on the side where the circumferential direction portion 91b of the radial direction portion 91a protrudes, the surface 91f on the inner peripheral side of the circumferential direction portion 91b, and the end surface 91d of the circumferential direction portion 91b come into contact. A spiral closed space is formed by the back surface 91g of the radial portion 91a of the adjacent circumferential portion. Thus, in the present embodiment, the spiral member 91 divides the outer peripheral flow path in a direction along the heater circumferential direction as viewed in the heater axial direction, and restricts the flow in the heater axial direction in the outer peripheral flow path.

  In addition, between the outer peripheral side of the spiral member 91 and the inner peripheral surface 93c of the case 93, in order to prevent the flow of water (outflow) between the outer side of the spiral member 91 and the inner peripheral surface 93c of the case 93. O-ring 92 is provided.

  According to the heat exchanger 90 of the present embodiment, since the spiral closed space can be formed around the heater 2 only by the spiral member 91, the structure can be simplified. Further, since the spiral member 91 can be easily brought into close contact with the heater outer peripheral surface 2c depending on the winding condition of the spiral member 91, the bending and dimensional tolerance of the heater 2 can be easily absorbed. Further, by not using a part of the case 93 to form a spiral flow path in the outer peripheral flow path, the flow path is formed without affecting the case 93 due to the bending of the heater 2 or the dimensional tolerance. be able to. As described above, according to the heat exchanger 90 of the present embodiment, the bending and dimensional tolerance of the heater 2 can be absorbed with a small number of parts, so that it is simple regardless of the bending or dimensional tolerance of the heater 2. The flow path can be reliably formed by the structure.

  Further, in the heat exchanger 90 of the present embodiment, after the spiral member 91 is wound around the heater 2, the outer peripheral side of the spiral member 91 is covered with a sheet of rubber or the like, or the case 93 is separated from the case 93. By storing the water, it is possible to prevent water from leaking from between the surrounding portions in contact with each other in the spiral member 91 (between the lines).

  A tenth embodiment of the present invention will be described with reference to FIGS. In addition, about the structure which is common in 10th Embodiment, description is abbreviate | omitted suitably using the same code | symbol. In the heat exchanger 100 of the present embodiment, as shown in FIG. 18, a plurality of annular plates provided with an interval in the heater axial direction so that the water flow regulating means protrudes in the radial direction of the heater 2. It is comprised by the metal ring 101 which is a member.

  The metal ring 101 is made of a material having a relatively high thermal conductivity, such as copper, stainless steel, or aluminum. As shown in FIG. 19A, the metal ring 101 is a donut-shaped plate-like member, and is held by the heater 2 in a state where the heater 2 is penetrated. As shown in FIG. 18, by attaching a plurality of metal wheels 101 to the heater 2, a plurality of hook-shaped portions that protrude from the heater outer peripheral surface 2 c in the radial direction of the heater 2 are formed. In FIG. 18, ten metal rings 101 are attached to the heater 2 at substantially equal intervals in the heater axial direction.

  The metal ring 101 is in close contact with the heater outer peripheral surface 2c by elastic deformation. As shown in FIG. 19, the metal ring 101 of the present embodiment has a plurality of tooth portions 101 a as portions that are in close contact with the heater outer peripheral surface 2 c by elastic deformation. The tooth portion 101a is formed by cutting out the edge portion on the inner peripheral side of the metal ring 101 by forming cut portions 101b at a plurality of locations from the inner diameter side of the metal ring 101 toward the outer side in the radial direction. The In the present embodiment, five tooth portions 101 a are formed by providing the cut portions 101 b at five locations in the circumferential direction of the metal ring 101.

  As shown in FIG. 19B, the tooth portion 101a is bent toward one side of the metal ring 101 in the plate thickness direction (upper side in FIG. 19B). The tooth portion 101 a is bent so that the inner diameter of the metal ring 101 is slightly smaller than the outer diameter of the heater 2. Therefore, as the heater 2 is inserted from the side opposite to the side where the tooth portion 101a is bent with respect to the metal ring 101, the bent tooth portion 101a is further deformed in a bending direction due to elasticity. Thereby, in a state where the metal ring 101 is mounted on the heater 2, the tooth portion 101a is pressed against the heater outer peripheral surface 2c by elasticity and is brought into close contact. Here, the bending state of the tooth portion 101a that is bent in advance is set such that, for example, when the metal ring 101 is attached to the heater 2, the heater outer peripheral surface 2c is not damaged.

  As described above, a plurality of tooth portions 101a that are provided as portions that are in close contact with the outer peripheral surface 2c of the metal ring 101 due to elastic deformation of the metal ring 101 are provided along the circumferential direction on the inner peripheral edge of the annular outer shape of the metal ring 101. And is pressed against the heater outer peripheral surface 2c by elasticity in a state of being bent toward the heater axial direction.

  The metal ring 101 is formed so that the outer peripheral end contacts the inner peripheral surface 93 c of the cylindrical case 93. That is, the outer diameter dimension of the metal ring 101 is set to be substantially the same as the inner diameter dimension of the case 93. Thus, the heater outer peripheral surface 2c and the case 93 are provided so that a plurality of metal rings 101 mounted on the heater 2 at intervals in the heater axial direction are in contact with the inner peripheral surface 93c of the case 93. The outer peripheral flow path formed between the inner peripheral surface 93c and the inner peripheral surface 93c is partitioned into a plurality in a direction perpendicular to the heater axial direction. That is, a plurality of annular spaces are formed by the heater outer peripheral surface 2c, the inner peripheral surface 93c of the case 93, and the pair of metal rings 101 adjacent to each other in the heater axial direction.

  And the metal ring 101 has the notch part 101c for ensuring the water flow in an outer peripheral side flow path. In the present embodiment, the notch 101 c is formed at one location in the circumferential direction of the metal ring 101 on the outer peripheral side of the metal ring 101. In the configuration in which a plurality of annular spaces are formed by the cutout portion 101 c in a state where the metal ring 101 attached to the heater 2 is in contact with the inner peripheral surface 93 c of the cylindrical case 93, Water flow between the available spaces is ensured. That is, the notch 101c forms an opening in the partition by the metal ring 101 together with the inner peripheral surface 93c of the case 93, and the water present in the space partitioned by the metal ring 101 is the opening formed by the notch 101c. Flows into the adjacent space (the left adjacent in FIG. 18).

  In the configuration in which a plurality of metal rings 101 are mounted on the heater 2, the phase (circumferential position) of the notch 101c included in each metal ring 101 is not particularly limited, but between the metal rings 101 adjacent to each other in the heater axial direction. In addition, it is preferable that the notch portions 101c of the respective metal rings 101 exist at positions shifted from each other in the circumferential direction. That is, it is preferable that the notches 101c of the metal rings 101 adjacent in the heater axial direction do not have a portion overlapping in the heater axial direction.

  As described above, the plurality of metal rings 101 are provided so that the notches 101c do not overlap with each other when viewed in the heater axis direction between the metal rings 101 adjacent in the heater axis direction. Thereby, since the notch part 101c which the adjacent metal ring | wheel 101 has is arrange | positioned in the position shifted | deviated to the circumferential direction, water passes continuously through the notch part 101c which each of the some metal ring | wheel 101 has, and water is a heater axial direction. Can be prevented from coming off. Thereby, the flow of a heater axial direction can be controlled and the flow velocity can be ensured.

  Moreover, it is preferable that the phase of the notch 101c included in each metal ring 101 is shifted by 180 ° between the adjacent metal rings 101. In this case, for example, when the notch 101c of a certain metal ring 101 is positioned on the upper side, the notch 101c included in the metal ring 101 adjacent to the metal ring 101 is disposed on the lower side. By using such a positional relationship of the notches 101c, water can be evenly distributed along the heater outer peripheral surface 2c between the heater outer peripheral surface 2c and the inner peripheral surface 93c of the case 93.

  Thus, in the case where the plurality of metal rings 101 are provided so that the phase of the notch 101c is shifted by 180 ° between the adjacent metal rings 101, the flow of water in the space portion partitioned by the metal rings 101 Is as follows. As shown in FIG. 18, the water that is about to pass through the metal ring 101 along the heater axial direction passes through the notch 101c (see arrow C1). The water that has passed through the notch 101c flows to the opposite phase along the periphery of the heater outer peripheral surface 2c (see arrow C2). Then, by passing through the notch 101c that is in the opposite phase to the notch 101c that has just passed, the metal wheel 101 flows into the next space portion (see arrow C3). Such a flow of alternately passing through the notches 101c in opposite phases for each metal ring 101 is repeated up to the water discharge port 5 in the outer peripheral side flow path.

  According to the heat exchanger 100 of the present embodiment, since the plurality of metal rings 101 are continuously provided in the heater axial direction, the structure for partitioning the flow path between the heater 2 and the case 93 is It becomes easy to follow the bending or dimensional tolerance of the heater 2. Thereby, even if the heater 2 has a bend, a dimensional tolerance, etc., the metal ring 101 can be contact | adhered to the heater 2 and a flow can be controlled reliably. Further, since the metal ring 101 is firmly adhered to the surface of the heater outer peripheral surface 2c by the plurality of tooth portions 101a, it is possible to prevent the metal ring 101 from being displaced during transportation or construction of the heat exchanger 100. .

  Moreover, in the heat exchanger 100 of this embodiment, the following merit can be acquired. In the heat exchanger 100 of the present embodiment, the water can flow uniformly around the heater 2 by changing the phase of the notch 101c of the metal ring 101 for each stage. Moreover, the flow of the heater axial direction along the heater outer peripheral surface 2c can be reliably controlled by shifting the phase of the cut portion 101b for forming the tooth portion 101a between the adjacent metal rings 101. Therefore, when adopting a configuration in which the notches 101c are alternately arranged by being shifted by 180 ° as described above, the number of the notches 101b provided at equal intervals in the circumferential direction is preferably an odd number. Thereby, the phase of the notch part 101b will shift | deviate automatically between the adjacent metal rings 101. FIG.

  Moreover, since the contact area with respect to the heater outer peripheral surface 2c of the metal ring 101 can be increased by the tooth portion 101a, the efficiency of heat transfer can be increased. Further, since the metal ring 101 can be made with a relatively small tolerance, it is difficult to generate a gap between the metal ring 101 and the case 93. Thereby, the flow (outflow) of the heater axial direction which passes the outer peripheral side of the metal ring | wheel 101 can be prevented effectively. Furthermore, by forming protruding portions (legs) along the heater axis direction on the metal wheel 101, it is possible to perform positioning (pitch determination) in the heater axis direction for the plurality of metal wheels 101. Such a protruding portion for positioning can be shared by the cut portion 101b of the metal ring 101 according to the present embodiment.

  In the present embodiment, the metal ring 101 made of metal is employed as the annular plate member. However, the annular plate member is made of another material such as resin. Also good.

  An eleventh embodiment of the present invention will be described with reference to FIGS. 20, 21, and 22. In addition, about the structure which is common in 9th embodiment, description is abbreviate | omitted suitably using the same code | symbol. As shown in FIG. 20, the heat exchanger 110 of this embodiment is provided with a space in the heater axial direction so that the water flow regulating means protrudes in the radial direction of the heater 2, as in the tenth embodiment. It is comprised by the metal ring 111 which is a some annular | circular shaped board member. And as shown in FIG. 21, the metal ring 111 is a substantially C-shaped plate-like member having a notch portion 111a in which a part in the circumferential direction in the annular shape is notched.

  The metal ring 111 is brought into close contact with the heater outer peripheral surface 2c by elastically deforming in the circumferential direction using the notch 111a. That is, the inner diameter of the metal ring 111 is set smaller than the outer diameter of the heater 2, and when the metal ring 111 is attached to the heater 2, it is elastically deformed so that the interval between the notches 111a is widened (arrow D1). reference). Moreover, the water flow in an outer peripheral side flow path is ensured by the notch part 111a which the metal ring 111 has. As in the case of the tenth embodiment, the phase of the notch 111a included in each metal ring 111 is preferably shifted by 180 ° between the adjacent metal rings 111.

  According to the heat exchanger 110 of the present embodiment, the notch 111a of the metal ring 111 can serve both as a function of ensuring water flow and as a function of absorbing bending, dimensional tolerance, and the like of the heater 2. Further, the metal ring 111 can follow the outer diameter tolerance of the heater 2 in a relatively wide range, and the metal ring 111 can be firmly attached to the heater 2.

  FIG. 22 shows a modification of the metal ring 111. As shown in FIG. 22, the metal ring 111 according to this example includes a plurality of bent portions 111b. The bent portion 111b is a protruding portion (a groove portion when viewed from the opposite surface) that is formed in a streak shape along the substantially radial direction of the metal ring 111 by bending the plate-like portion. A plurality of bent portions 111 b are formed in the circumferential direction of the metal ring 111. In this example, as shown in FIG. 22, the bent portions 111 b are formed at five locations at substantially equal intervals in the circumferential direction of the metal ring 111. Thus, the metal ring 111 is more easily elastically deformed by having the bent portion 111b, and the metal ring 111 can be easily attached to the heater 2.

  A twelfth embodiment of the present invention will be described with reference to FIG. In addition, about the structure which is common in 11th embodiment, description is abbreviate | omitted suitably using the same code | symbol. As shown in FIG. 23, the heat exchanger 120 of this embodiment includes a cylindrical sheet member 121 that covers the outer peripheral sides of the plurality of metal rings 111.

  The sheet member 121 is configured by an elastic body such as rubber or resin. The sheet member 121 is formed so as to be in contact with the outer peripheral ends of the plurality of metal wheels 111 attached to the heater 2. That is, the inner diameter of the sheet member 121 is approximately the same as the outer diameter of the metal ring 111. The sheet member 121 has a length that can cover all the metal rings 111 attached to the heater 2 from the outer peripheral side. For example, the sheet member 121 has substantially the same length as the length of the inner peripheral surface 93c of the case 93 in the heater axial direction. In the sheet member 121, an opening 121 a for communicating an internal space surrounded by the sheet member 121 with the water discharge port 5 is formed.

  As described above, in the heat exchanger 120 of the present embodiment, the water flow restricting means includes the cylindrical sheet member 121 that is formed of an elastic body and is in close contact with the outer peripheral ends of the plurality of metal rings 111. According to the heat exchanger 120 of the present embodiment, the sheet member 121 passes through the outer peripheral side of the metal ring 111 without generating a gap between the outer peripheral end of the metal ring 111 and the inner peripheral surface 93c of the case 93. It is possible to effectively prevent the flow in the heater axis direction (out-going). An O-ring for preventing the flow of water between the outer side of the sheet member 121 and the inner peripheral surface 93c of the case 93 is provided between the outer peripheral side of the sheet member 121 and the inner peripheral surface 93c of the case 93. It may be provided. Further, since the inclination of the heater 2 is absorbed by the elastic deformation of the sheet member 121, no gap is generated on the outer peripheral side of the metal ring 111 even when the heater 2 is inclined in the case 73. .

  A thirteenth embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 24, in the heat exchanger 130 of the present embodiment, a plurality of annular plates provided with a water flow restricting means spaced apart in the heater axial direction so as to protrude in the radial direction of the heater 2. It is comprised by the bush 131 which is a member.

  As shown in FIG. 25, the bush 131 includes a cylindrical tube portion 131a having the heater axis direction as the central axis direction, and a flange portion 131b protruding radially outward from one end side of the tube portion 131a. As shown in FIG. 25A, the bush 131 is a substantially C-shaped member having a notch 131c in which a part in the circumferential direction in the annular shape is notched. The bush 131 can be produced, for example, by deep drawing.

  As shown in FIG. 25 (b), the bush 131 has a locking projection 131d at one end in the heater axial direction for relative positioning in the circumferential direction in relation to the adjacent bush 131, A locking recess 131e is provided at the other end in the heater axial direction. The engaging protrusion 131d engages with the adjacent bush 131 on one side in the heater axial direction, thereby restricting relative rotation in the circumferential direction with respect to the adjacent bush 131 on one side. And the latching recessed part 131e fits the latching protrusion 131d which the adjacent bush 131 of the other side of a heater axial direction has, and controls the relative rotation of the circumferential direction with respect to the adjacent bush 131 of the other side.

  The locking protrusion 131d is formed as a triangular protrusion, and the locking recess 131e is formed as a triangular recess in which the locking protrusion 131d can be fitted along the heater axial direction. However, the locking protrusion 131d and the locking recess 131e are not particularly limited with respect to the shape, the number, the position, and the like. Further, as described above, when adopting a configuration in which the phase of the notch 131c is shifted by 180 ° between the adjacent bushes 131, the locking protrusion 131d and the locking recess 131e are both on the both sides in the circumferential direction from the notch 131c. It is preferable to be provided at two positions shifted by approximately 90 °. Accordingly, in the configuration in which the phase of the notch 131c is shifted by 180 °, the locking protrusion 131d and the locking recess 131e can be shared regardless of which phase the notch 131c is in, and a plurality of types of bushes can be used. 131 need not be prepared.

  According to the heat exchanger 130 of the present embodiment, the circumferential positioning of the bush 131 is facilitated, and the operation of shifting the phase of the notch 131c one step at a time is facilitated. Also, by defining the length of the cylindrical portion 131a of the bush 131, it is possible to automatically obtain a constant pitch between the plurality of bushes 131 by simply stacking the bush 131 on the heater 2, and easy assembly. It is. In the present embodiment as well, a configuration including the sheet member 121 can be employed as in the twelfth embodiment.

  A fourteenth embodiment of the present invention will be described. This embodiment is another implementation in that the heating element is provided with a folded portion, and a water flow restricting means for regulating the flow in the axial direction of the heating element is provided in the outer peripheral flow path formed around the folded portion. Different from form.

  As shown in FIG. 26, the heat exchanger 140 of the present embodiment includes a sheathed heater 142 as a heating element and a case 143 that houses the sheathed heater 142. The heat exchanger 140 includes straight portions 140a and 140a formed substantially parallel to each other, and a semicircular curved portion 140b that is curved in an arc shape connecting the straight portions 140a and 140a, and has a substantially U shape as a whole. Composed in a letter shape.

  In the heat exchanger 140, one end (the upper side in FIG. 26) of the straight portion 140a opposite to the side connected to the curved portion 140b is a water inlet 144, and the other (the lower side in FIG. 26) straight portion 140a. The end on the opposite side to the side connected to the curved portion 140b is a water outlet 145. That is, in the heat exchanger 140, the water that flows in from the water inlet 144 is warmed by the sheath heater 142 and becomes warm water and flows out from the water outlet 145.

  The sheathed heater 142 is a tubular heater in which a spiral heating wire is enclosed with a heat conductive insulating material such as MgO (magnesium oxide) inside a metal tube, and has terminals (not shown) at both ends. The sheathed heater 142 is formed in a substantially U shape by bending or the like, and has a shape that follows the shape of the heat exchanger 140 having the straight portions 140a and 140a and the curved portion 140b. That is, the sheathed heater 142 includes linear portions 142 a and 142 a that constitute the linear portions 140 a and 140 a of the heat exchanger 140, and a curved portion 142 b that constitutes the curved portion 140 b of the heat exchanger 140. The sheathed heater 142 heats water passing through the outer peripheral side of the sheathed heater 142 by heat generated from the outer peripheral surface (hereinafter referred to as “heater outer peripheral surface”) 142c.

  The case 143 is a portion that forms the exterior of the heat exchanger 140 that is configured in a substantially U shape as a whole, and is made of resin, metal, or the like corresponding to the shape of the sheathed heater 142 having a substantially U-shaped outer shape. It is configured in a substantially U-shaped pipe shape. The case 143 forms a substantially U-shaped space for accommodating the sheathed heater 142 along the shape of the substantially U-shaped sheathed heater 142. Therefore, the case 143 includes straight portions 143a and 143a that house the straight portions 142a and 142a of the sheathed heater 142, and a curved portion 143b that houses the curved portion 142b of the sheathed heater 142.

  The pipe-shaped case 143 accommodates the sheathed heater 142 so that the sheathed heater 142 is positioned at a substantially center (axial center) portion thereof. For this reason, a space is formed between the heater outer peripheral surface 142 c and the case 143 over the entire circumference in the circumferential direction of the sheathed heater 142 in each of the straight portions 140 a and 140 a and the curved portion 140 b of the heat exchanger 140. Such a space is used as the outer peripheral flow path.

  That is, the case 143 covers the outer periphery of the sheathed heater 142, and forms a flow path (outer peripheral flow path) of water heated by the sheathed heater 142 between the heater outer peripheral surface 142c. Specifically, in this embodiment, the heater outer peripheral surface 142c is the outer peripheral surface of the entire sheathed heater 142 including the straight portions 142a and 142a and the curved portion 142b. Further, the case 143 in which the sheathed heater 142 is accommodated has an inner peripheral surface portion formed as a substantially circumferential surface at each of the straight portions 143a and 143a and the curved portion 143b. Therefore, an outer peripheral flow path is formed between the heater outer peripheral surface 142c and the inner peripheral surface portion of the case 143 facing each other in each of the straight portions 140a and 140a and the curved portion 140b of the heat exchanger 140.

  Thus, in the heat exchanger 140 of this embodiment, the outer peripheral side flow path has a linear part formed in a linear shape and a curved part formed in a curved shape. Specifically, the straight line portion of the outer peripheral flow path is formed by the straight line portions 142 a and 142 a of the sheathed heater 142 and the straight line portions 143 a and 143 a of the case 143, and the curved portion of the outer peripheral flow path is the curve of the sheathed heater 142. A portion 142b and a curved portion 143b of the case 143 are formed. An annular opening formed by the heater outer peripheral surface 142 c and the inner peripheral surface portion of the case 143 at both ends of the heat exchanger 140 is a water inlet 144 or a water outlet 145 with respect to the outer peripheral flow path.

  In the heat exchanger 140 having the above-described configuration, the water flowing in from the water inlet 144 flows while being heated by the linear portion 142a of the sheathed heater 142 through the outer peripheral flow path in one linear portion 140a (see arrow J1). ), And flows into the outer peripheral flow path in the curved portion 140b of the heat exchanger 140. The water that has flowed into the outer circumferential side flow path of the curved portion 140b is heated by the curved portion 142b of the sheathed heater 142 to the outer circumferential side flow path in the other linear portion 140a of the heat exchanger 140 by the outer circumferential side flow path of the curved portion 140b. Carried. It flows while being heated by the linear portion 142a of the sheathed heater 142 (see arrow J2) through the outer peripheral flow path of the linear portion 140a, and discharged from the water outlet 145.

  In the heat exchanger 140 according to the present embodiment, in the curved portion 140b, the outer peripheral flow path is in a direction along the circumferential direction of the sheathed heater 142 (hereinafter referred to as “heater circumferential direction”) as viewed in the axial direction of the sheathed heater 142. In addition to partitioning, there is water flow restricting means for restricting the flow in the axial direction of the sheathed heater 142 (hereinafter referred to as “heater axial direction”) in the outer peripheral side flow path.

  As shown in FIG. 26, the heat exchanger 140 of the present embodiment is provided as a water flow restricting means on a spring 151 fitted on the curved portion 142b of the sheathed heater 142 and an inner peripheral portion of the curved portion 143b of the case 143. And a spiral portion 152 to be formed.

  The spring 151 is a wire formed in a spiral shape as a winding spring. As the spring 151, a spring having a relatively thin wire diameter (for example, a wire diameter of about 0.8 mm) is used. The spring 151 is provided in a state of being mounted over substantially the entire curved portion 142 b of the sheathed heater 142 inserted into the case 143.

  The spring 151 is fitted on the sheathed heater 142 in a state of being in close contact with the heater outer peripheral surface 142c of the curved portion 142b of the sheathed heater 142. Specifically, a spring 151 having an inner diameter smaller than the outer diameter of the curved portion 142b of the sheathed heater 142 is used. When the spring 151 is attached to the sheathed heater 142, the spring 151 is twisted in the direction opposite to the spiral direction to increase the inner diameter of the spring 151. In this state, the spring 151 is curved to the curved portion 142b of the sheathed heater 142. By releasing the twist of the spring 151, the spring 151 is returned by elasticity and is in close contact with the heater outer peripheral surface 142c. Here, the one where the wire diameter of the spring 151 is smaller is more securely attached to the heater outer peripheral surface 142c.

  As described above, in the heat exchanger 140 of the present embodiment, the spring 151 is attached to the curved portion 142b of the sheathed heater 142 in a state of being in close contact with the heater outer peripheral surface 142c, thereby spiraling along the heater outer peripheral surface 142c. The 1st control part provided so that it may protrude from is comprised. In other words, in the present embodiment, the spring 151 attached to the curved portion 142b of the sheathed heater 142 constitutes a first restricting portion included in the water flow restricting means. The spring 151 is fixed to the sheathed heater 142 by an elastic force in a state of being wound around the outer peripheral side of the curved portion 142b of the sheathed heater 142.

  The spiral portion 152 forms a spiral groove portion 152 a having the heater axis direction as the central axis direction of the turning direction on the inner peripheral surface portion of the curved portion 143 b of the case 143. In other words, the spiral portion 152 forms a spiral protrusion 152b having the heater axial direction as the central axis direction of the turning direction on the inner peripheral surface portion of the curved portion 143b of the case 143. Therefore, the spiral portion 152 appears as a plurality of tooth-like portions in a cross-sectional view as shown in FIG.

  The spiral portion 152 is formed such that the spiral winding number and pitch are substantially the same as the spring 151 winding number. And the spiral part 152 is formed so that the spiral groove part 152a may be along with the spring 151 of the state wound around the curve part 142b of the sheathed heater 142. FIG. Further, the spiral portion 152 is formed so that the width of the spiral groove portion 152 a is wider than the wire diameter of the spring 151. The spiral portion 152 and the spring 151 wound around the curved portion 142b of the sheathed heater 142 divide the outer peripheral flow path into a spiral shape, thereby forming a spiral flow path.

  As described above, in the heat exchanger 140 of the present embodiment, the spiral portion 152 formed on the inner peripheral surface portion of the curved portion 143b of the case 143 projects spirally along the inner peripheral surface of the case 143. A second restricting portion that is provided and forms a spiral flow path with the spring 151 is configured. That is, in the present embodiment, the spiral portion 152 formed on the inner peripheral side of the curved portion 143b of the case 143 constitutes a second restricting portion included in the water flow restricting means.

  As described above, in the heat exchanger 140 of the present embodiment, the substantially U-shaped sheathed heater 142 having the straight portions 142a and 142a and the curved portion 142b is used as a heating element for heating water. And the outer peripheral side flow path formed between the sheathed heater 142 and the case 143 has a linear part formed in a linear shape and a curved part formed in a curved shape, and at least the curved part has a spring. 151 and a water flow restricting means constituted by the spiral portion 152.

According to the heat exchanger 140 of the present embodiment having the above-described configuration, the spiral flow in the direction along the circumferential direction of the heater is maintained by the water flow restriction means configured by the spring 151 and the spiral portion 152. The flow in the heater axial direction in the outer peripheral channel is reliably regulated. Then, according to the water flow restricting means constituted by the spring 151 and the spiral portion 152, the flow in the heater axial direction can be more reliably regulated, so that the spiral flow is maintained and the spiral flow path is By forming, it is possible to sufficiently obtain the effect of narrowing the flow path area, and it is possible to increase the flow velocity. As a result, the efficiency of heat transfer can be sufficiently increased, the surface temperature of the sheathed heater 142 can be effectively lowered, and the effect of reducing boiling noise can be enhanced.

  Moreover, in the heat exchanger 140 of the present embodiment having the curved portion 140b, the following operations and effects can be obtained. If the heat exchanger 140 does not include the water flow restriction means in the curved portion 140b, the water contacts the sheathed heater 142 on the inner circumferential side and the outer circumferential side of the curved shape in the outer circumferential side flow path of the curved portion 140b. Since the length of the flow path (length of the outer peripheral flow path) is different, heat transfer is not performed uniformly. This adversely affects temperature characteristics such as bumping in the outer peripheral flow path and generation of boiling noise.

  Therefore, like the heat exchanger 140 of the present embodiment, the water flow restricting means is provided in the curved portion 140b, so that it is formed between the sheathed heater 142 and the case 143 in the outer peripheral flow path of the curved portion 140b. The flow rate of the water flowing through the outer peripheral side channel can be increased, and the efficiency of heat transfer between the sheathed heater 142 and the water can be improved. Thereby, the surface temperature of the sheathed heater 142 can be lowered, the occurrence of bumping can be suppressed, and the boiling sound can be reduced.

  Furthermore, the sheathed heater 142 having the curved portion 142b is advantageous in reducing the size of the heat exchanger 140 as compared with the case where the sheathed heater 142 has only the straight portion 142a. That is, according to the heat exchanger 140 of the present embodiment, when the heat exchanger 140 is reduced in size by providing the sheathed heater 142 with the curved portion 142b, bumping or boiling noise in the outer peripheral flow path in the curved portion 140b. Generation | occurrence | production etc. can be suppressed effectively.

  Further, by adopting the sheathed heater 142 as a heating element for heating water, the characteristics of the sheathed heater can be obtained as an advantage. The characteristics of the sheathed heater are, for example, being strong against vibrations and shocks, having a long life, being easy to process and adaptable to various shapes, and being able to safely perform direct heating due to electrical insulation. It is excellent in mass productivity and inexpensive.

  In the heat exchanger 140 of the present embodiment, the water flow restricting means is provided only on the curved portion 140b, but may be provided on the straight portion 140a. In this case, for example, as shown in FIG. 27, in the straight portion 140 a of the heat exchanger 140, the spring 151 </ b> A that is fitted on the straight portion 142 a of the sheathed heater 142 and the inner peripheral portion of the straight portion 143 a of the case 143 are provided. The spiral portion 152A constitutes a water flow restricting means. Note that the spring 151 </ b> A that is externally fitted to the linear portion 142 a of the sheathed heater 142 may be an integral spring with the spring 151 that is externally fitted to the curved portion 142 b of the sheathed heater 142. As described above, according to the water flow regulating means configured by the spring 151A and the spiral portion 152A in the linear portion 140a of the heat exchanger 140, the spring 11 and the spiral portion 12 in the heat exchanger 1 of the first embodiment described above. It is possible to obtain the same operation and effect as the water flow regulating means configured.

  Moreover, in the heat exchanger 140 of this embodiment, as a water flow control means, the spring 151 externally fitted to the sheathed heater 142 and the case, like the spring 11 and the spiral portion 12 of the heat exchanger 1 of the first embodiment, Since the configuration having the spiral portion 152 provided on the inner peripheral portion of 143 is employed, the preferred configurations of the spring 11 and the spiral portion 12 as described above can be appropriately employed. Therefore, for example, in the heat exchanger 140, preferably, the spring 151 and the spiral portion 152 at least partially overlap in the heater axial direction view. Moreover, it is preferable that the overlapping part of the spring 151 and the spiral part 152 is in contact with each other.

  Moreover, in the heat exchanger 140 of this embodiment, the structure which has the spring 151 and the spiral part 152 similarly to the heat exchanger 1 of 1st embodiment as a water flow control means is employ | adopted, but the other mentioned above The structure with which the heat exchanger of embodiment is provided as a water flow control means is employable. That is, in the heat exchanger 140 of the present embodiment, as the spring 151, a spring having a square cross section (see the third embodiment), a spring having a L-shaped cross section (see the fourth embodiment), or a cross section has a cross section. A spring (see the fifth embodiment) having a thin plate shape in an oblique direction that contacts the heater outer peripheral surface 142c may be used. Further, in the heat exchanger 140 of the present embodiment, a part of the sheathed heater 142 forms a first restricting portion of the water flow restricting means (see the sixth embodiment), or a water flow restricting member that is separate from the case 143. A second restricting portion of the means may be configured (see the seventh and eighth embodiments), or the water flow restricting means may be configured only by the configuration provided on the sheathed heater 142 side (see the ninth embodiment). . Further, in the heat exchanger 140 of the present embodiment, the water flow restricting means is constituted by a plurality of annular plate members provided at intervals in the heater axial direction so as to protrude in the radial direction of the sheathed heater 142. (Refer to the tenth, eleventh, and thirteenth embodiments), a configuration having a cylindrical sheet member that covers the outer peripheral side of the plurality of annular plate members is employed (see the twelfth embodiment). Also good.

  It should be noted that the water flow regulating means exemplified in each embodiment as described above improves the heat transfer by increasing the flow rate of the water flowing through the flow path formed in the case 3 (case 143), thereby improving the heat transfer of the heater 2 ( The surface temperature of the sheathed heater 142) is lowered. For this reason, according to the water flow restricting means, since the flow rate of water is increased, the generation of scale generated on the surface of the heater 2 (seeds heater 142) can be suppressed, and the heater 2 (seeds heater 142) is suppressed. It is also possible to expect the effect of peeling off the scale generated on the surface. Further, as with the scale, bubbles existing on the surface of the heater 2 (seeds heater 142) and causing bubbles to reduce heat transfer between the heater 2 (seeds heater 142) and water have a high flow rate by the water flow regulating means. By this function, the effect of peeling from the surface of the heater 2 (seeds heater 142) can be defined. Thus, according to the water flow regulating means, it is possible to expect an effect of removing scales and bubbles generated on the surface of the heater 2 (seeds heater 142) by increasing the flow velocity, and effectively suppressing a decrease in heat transfer. can do.

  Below, an example of the sanitary washing apparatus provided with the heat exchanger which concerns on each embodiment as mentioned above is demonstrated using FIG. 28 and FIG. As shown in FIG. 28, the sanitary washing device 200 according to the present embodiment is provided in a state where the toilet device 300 is installed on a western-style seat toilet 301.

  The sanitary washing device 200 includes a main body portion 201, a toilet seat 202 and a toilet lid 203 that are pivotally supported to be openable and closable with respect to the main body portion 201, and a nozzle 204. The nozzle 204 is provided so as to be able to advance and retreat from the main body 201 to the inside of the bowl of the western seat toilet 301 in accordance with a switch operation or the like by the user of the toilet apparatus 300. The sanitary washing device 200 injects washing water from a water outlet provided at the tip of the nozzle 204 in a state where the nozzle 204 extends into the bowl of the western seat toilet 301. The cleaning water sprayed from the nozzle 204 cleans the local part of the human body.

  As shown in FIG. 29, the sanitary washing device 200 supplies water supplied from a water supply source 205 such as a water supply or a water storage tank to the heat exchanger 1 through a valve unit 206. Then, in the heat exchanger 1, the supplied water is warmed and supplied to the nozzle 204 as cleaning water. The valve unit 206 has a valve mechanism such as an electromagnetic on-off valve or a pressure regulating valve that functions as a water stop valve.

  As described above, the sanitary washing device 200 according to this embodiment includes the heat exchanger 1 according to the first embodiment, and uses the warm water generated by the heat exchanger 1 as washing water, and discharges this washing water from the nozzle 204. By doing so, the local part of the human body is washed. Thus, according to the sanitary washing device 200 including the heat exchanger 1 according to the present embodiment, it is possible to reduce the boiling noise in the heat exchanger that is uncomfortable for the user who receives the local washing. Note that the sanitary washing device 200 is not limited to the heat exchanger 1 of the first embodiment, and can be similarly applied to heat exchangers of other embodiments.

1 Heat exchanger 2 Heater (heating element)
3 Case 11 Spring 12 Spiral part 31 Spring 41 Spring 51 Spring 61 Spiral protrusion 71 Spiral cylinder 72 Spiral part 73 Case 81 Winding spring 82 Guide part 91 Spiral member 91a Radial part 91b Circumferential part 93 Case 101 Metal ring (annular) Plate member)
101a tooth part 101c notch part 111 metal ring (annular plate member)
111a cutout portion 121 sheet member 131 bush 142 sheathed heater 142a linear portion 142b curved portion 143 case 143a linear portion 143b curved portion 151 spring 152 spiral portion 200 sanitary washing device

Claims (13)

A heat exchanger that warms water to warm water,
A heating element having a cylindrical outer shape and heating water;
A case that covers the outer periphery of the heating element and forms a flow path of water heated by the heating element between the outer peripheral surface of the heating element;
A water flow restricting means for partitioning the flow path in a direction along a circumferential direction of the heating element in an axial view of the heating element, and restricting a flow in the axial direction of the heating element in the flow path;
A heat exchanger comprising: The water flow regulating means is
A first restricting portion provided so as to protrude spirally along the outer peripheral surface of the heating element;
A second restricting portion provided so as to protrude spirally along the inner peripheral surface of the case, and forming a spiral flow path together with the first restricting portion;
The heat exchanger according to claim 1, comprising:   3. The heat exchanger according to claim 2, wherein at least a part of the first restricting portion and the second restricting portion overlap each other when viewed in the axial direction of the heating element.   The heat exchanger according to claim 3, wherein overlapping portions of the first restricting portion and the second restricting portion are in contact with each other.   5. The heat exchanger according to claim 4, wherein the first restricting portion is in contact with the second restricting portion on the downstream side in the flow path of the water.   The first restricting portion is a winding spring having an inner diameter smaller than an outer diameter of the heating element, and is fixed to the heating element by an elastic force in a state of being wound around an outer peripheral side of the heating element. The heat exchanger as described in any one of Claims 2-5.   The heat exchanger according to any one of claims 2 to 5, wherein the first restricting portion is formed integrally with the heating element. The heating element is assembled to the case by being inserted into the case in the axial direction of the heating element,
The first restricting portion is constituted by a winding spring that is separate from the heating element and has a spiral pitch wider than that of the second restricting portion,
When the heating element is assembled to the case, the winding spring is compressed in the axial direction of the heating element by the second restricting portion and overlaps with the second restricting portion. The heat exchanger according to claim 3, wherein the heat exchanger is held in a state of being pressed against the second restricting portion by the elasticity of the heat exchanger. The water flow regulating means is
It is composed of a plurality of annular plate members provided at intervals in the axial direction of the heating element so as to protrude in the radial direction of the heating element,
2. The heat according to claim 1, wherein the annular plate member has a notch portion that is brought into close contact with the outer peripheral surface of the heating element by elastic deformation and ensures water flow in the flow path. Exchanger. The water flow regulating means is
The heat exchanger according to claim 7, comprising a cylindrical sheet member that is formed of an elastic body and is in close contact with outer peripheral ends of the plurality of annular plate members. The water flow regulating means is
It is formed in a spiral shape along the outer peripheral surface of the heating element, and is constituted by a spiral member provided in a state wound around the heating element,
The spiral member is
A plate-like radial portion formed along the radial direction of the heating element;
A plate-shaped circumferential portion provided at an outer peripheral side end of the radial portion and formed along the circumferential direction of the heating element;
The inner circumferential end surface of the radial direction portion is brought into contact with the outer circumferential surface of the heating element, and the end surface of the circumferential direction portion is brought into contact with a circumferential portion adjacent to the axial direction of the heating element, whereby the flow path is The heat exchanger according to claim 1, wherein the heat exchanger is partitioned in a spiral shape along the outer peripheral surface of the heating element. The heating element is a sheathed heater,
The said flow path has a linear part formed in a linear form, and a curved part formed in a curved shape, and has the said water flow control means in the said curved part at least. The heat exchanger as described in any one of. The heat exchanger according to any one of claims 1 to 12, comprising:
A sanitary washing apparatus, wherein hot water generated by the heat exchanger is used as washing water, and the washing water is discharged from a nozzle to wash a local part of the human body.

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