JP2010107113A - Spiral heat exchanger and engine performance testing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To efficiently exchange heat between high viscosity fluid and a heat exchange medium and accurately control the temperature of the high viscosity fluid for a short time. <P>SOLUTION: This spiral heat exchanger 7 includes a medium flowing part 72 which is formed by winding an inner wall 72b and an outer wall 72a spirally with respect to an axial line CL and where the heat exchange medium is made to flow in the direction approximately orthogonal to the axial line CL in a space surrounded by the inner wall 72b and outer wall 72a. A spiral clearance 78 sandwiched between the outer peripheral side of the inner wall 72b and the inner peripheral side of the outer wall 72a and a central clearance 77 sandwiched between a central wall 72e and the inner wall 72b are formed outside the medium flowing part 72. The maximum width of the central clearance 77 is set larger than that of the spiral clearance 78, and heat exchange is performed between the high viscosity fluid made to flow in the central clearance 77 and the spiral clearance 78 and the heat exchange medium. Block walls 81-83 for preventing inflow of the high viscosity fluid to the central clearance 77 are provided. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention includes a medium circulation part that is formed in a spiral shape and in which a heat exchange medium circulates, and between the high-viscosity fluid that flows in a gap outside the medium circulation part and the heat exchange medium. The present invention relates to a spiral heat exchanger that performs heat exchange, and an engine performance test apparatus that includes the spiral heat exchanger.

Conventionally, a spiral heat exchanger is known as a heat exchanger that performs heat exchange between fluids. As a spiral heat exchanger, a so-called cross flow type in which the flow direction of one fluid and the flow direction of the other fluid are orthogonal has been proposed (see, for example, Patent Document 1). . Such a cross flow type spiral heat exchanger is preferably used when the viscosity of one fluid is larger than the viscosity of the other fluid. For example, as shown in FIGS. 5 and 6, the spiral heat exchanger 90 includes an outer wall 91a, an inner wall 91b, and the like that are spirally wound, and ends of the outer wall 91a and the inner wall 91b at the center portion. Is provided with a medium distribution part 91 connected by a central wall 91c. Then, one fluid (for example, a high-viscosity fluid) passes along the axis CL through a spiral gap formed between the outer peripheral side of the outer wall 91a and the inner peripheral side of the inner wall 91b. A circulation pump (not shown) and a circulation pump (not shown) provided outside the spiral heat exchanger 90 along the inner space of the medium circulation part 91 (parts with a dotted pattern in FIG. 6). When the other fluid (for example, a heat exchange medium) flows in a spiral shape, heat exchange between the two fluids is performed.
Japanese Utility Model Publication No. 2-85265

  By the way, as described above, the outer wall 91a and the inner wall 91b are connected by the central wall 91c. Therefore, the width of the gap formed between the outer peripheral side of the outer wall 91a and the inner peripheral side of the inner wall 91b, and the gap formed between the inner peripheral side of the inner wall 91b and the central wall 91c. It is very difficult to make the widths equal. Therefore, in general, a relatively wide gap (center gap) 92 is formed in the central portion (between the inner wall 91b and the center wall 91c) of the medium circulation portion 91.

  Here, when one of the fluids is a high-viscosity fluid, the high-viscosity fluid does not easily flow into a spiral gap (spiral gap) 93 having a relatively narrow width due to its own viscosity. It flows in a concentrated manner with respect to the wide central gap 92. Therefore, the heat transfer area is reduced. Further, since the high-viscosity fluid has low fluidity (heat transferability), the high-viscosity fluid and the heat flowing into the central portion 94 of the central gap 92 due to the presence of the high-viscosity fluid located in the vicinity of the wall surface of the medium flow portion 91. There is a possibility that heat exchange with the exchange medium cannot be performed efficiently. As a result, it may be difficult to adjust the high-viscosity fluid to a desired temperature, or it may take a long time to adjust to the desired temperature.

  In particular, as shown in FIG. 7, a fluid whose viscosity suddenly increases when the temperature is lower than a specific temperature (for example, engine oil, etc .; , B shows the relationship between the viscosity and the temperature), the occurrence of the above-mentioned problem is further concerned. That is, the engine oil that is in contact / proximity with respect to the wall surface of the medium circulation portion 91 is cooled by the wall surface of the medium circulation portion 91 cooled by the heat exchange medium, so that its viscosity increases rapidly. It becomes difficult to move, and as a result, it acts as a low heat transfer film covering the wall surface of the medium flow part 91. On the other hand, the engine oil passing through a position relatively separated from the wall surface of the medium circulation portion 91 (for example, the central portion 94) is not sufficiently cooled due to the presence of the oil whose viscosity has increased rapidly. The viscosity does not increase so much, and as a result, it becomes a shear flow without being mixed with the oil whose viscosity increases rapidly, which acts like the low heat transfer film. Therefore, the engine oil that passes through the central portion 94 passes through the central portion 94 relatively quickly, and the heat transfer time during heat exchange is relatively short. That is, as the difference in viscosity inside the engine oil increases, the efficiency of heat exchange may be further deteriorated.

  The present invention has been made in view of the above circumstances, and the purpose thereof is to efficiently perform heat exchange between the high-viscosity fluid and the heat exchange medium, and thus, temperature adjustment of the high-viscosity fluid in a short time, Another object of the present invention is to provide a spiral heat exchanger that can be accurately performed, and an engine performance test apparatus including the spiral heat exchanger.

  In the following, each means suitable for solving the above-described object will be described in terms of items. In addition, the effect specific to the means to respond | corresponds as needed is added.

Means 1. An inner wall and an outer wall provided at a predetermined interval with respect to the inner wall are spirally formed with respect to the axis, and the inside of the spiral space surrounded by the inner wall and the outer wall is substantially the same as the axis. Comprising a medium flow part through which the heat exchange medium flows in the orthogonal direction;
Outside the media distribution unit,
A spiral gap formed between the inner peripheral side of the inner wall and the outer peripheral side of the outer wall, forming a spiral shape, and
A central gap is formed between the inner wall and the central wall that connects at least the axial side end of the inner wall and the axial side end of the outer wall, and is connected to the spiral gap. ,
The maximum width of the central gap is set larger than the maximum width of the spiral gap; and
A spiral heat exchanger for exchanging heat between the high-viscosity fluid flowing through the central gap and the spiral gap in a direction substantially along the axis, and the heat exchange medium,
A labyrinth seal-like fluid movement suppression means is provided in the center gap, and when the high viscosity fluid has a maximum viscosity that can flow through the center gap, a pressure loss when the high viscosity fluid flows through the center gap is A spiral heat exchanger characterized in that the high-viscosity fluid is substantially equal to a pressure loss when flowing through the spiral gap.

  Note that “the end on the axial side of the inner wall (outer wall)” indicates the terminal portion on the side of the center (axis) of the spiral formed by the inner wall (outer wall) when viewed from the end in the axial direction. (Hereinafter the same).

  According to the means 1, by providing the fluid movement suppressing means in the center gap, the pressure when the high viscosity fluid flows through the center gap when the high viscosity fluid has the highest viscosity that can flow through the center gap. The loss and the pressure loss when the high viscosity fluid flows through the spiral gap can be made substantially equal. For this reason, the high-viscosity fluid flowing through the center gap can be subjected to heat exchange at the same level as the high-viscosity fluid flowing through the spiral gap, and heat exchange between the high-viscosity fluid and the heat exchange medium can be performed efficiently. . As a result, the high-viscosity fluid can be accurately adjusted to a desired temperature in a relatively short period of time.

  As the fluid movement suppressing means, any means may be used as long as it is provided in the center gap and can serve as a resistance of the high viscosity fluid flowing in the center gap. Therefore, for example, in order to increase the flow resistance of a high-viscosity fluid, the flow of fluid while having a gap in the radial direction or the axial direction due to unevenness provided on the inner wall or the center wall of the medium flow portion forming the center gap. First, labyrinth seal-like processing that provides resistance can be cited. For example, in order to increase the flow resistance of the high-viscosity fluid, secondly, the flow path resistor is composed of a plurality of mesh members provided across the inner wall and the center wall of the medium flow part forming the center gap. be able to.

Mean 2. An inner wall and an outer wall provided at a predetermined interval with respect to the inner wall are spirally formed with respect to the axis, and the inside of the spiral space surrounded by the inner wall and the outer wall is substantially the same as the axis. Comprising a medium flow part through which the heat exchange medium flows in the orthogonal direction;
Outside the media distribution unit,
A spiral gap formed between the inner peripheral side of the inner wall and the outer peripheral side of the outer wall, forming a spiral shape, and
A central gap is formed between the inner wall and the central wall that connects at least the axial side end of the inner wall and the axial side end of the outer wall, and is connected to the spiral gap. ,
The maximum width of the central gap is set larger than the maximum width of the spiral gap; and
A spiral heat exchanger for exchanging heat between the high-viscosity fluid flowing through the central gap and the spiral gap in a direction substantially along the axis, and the heat exchange medium,
A pressure when the high-viscosity fluid flows through the central gap when the high-viscosity fluid has a maximum viscosity at which the high-viscosity fluid can flow through the central gap is provided in the central gap with a fluid flow suppression means using a net-like channel resistor A spiral heat exchanger characterized in that the loss is substantially equal to the pressure loss when the high-viscosity fluid flows through the spiral gap.

  According to the means 2, basically the same effects as those of the means 1 are obtained.

Means 3. An inner wall and an outer wall provided at a predetermined interval with respect to the inner wall are spirally formed with respect to the axis, and the inside of the spiral space surrounded by the inner wall and the outer wall is substantially the same as the axis. Comprising a medium flow part through which the heat exchange medium flows in the orthogonal direction;
Outside the media distribution unit,
A spiral gap formed between the inner peripheral side of the inner wall and the outer peripheral side of the outer wall, forming a spiral shape, and
A central gap is formed between the inner wall and the central wall that connects at least the axial side end of the inner wall and the axial side end of the outer wall, and is connected to the spiral gap. ,
The maximum width of the central gap is set larger than the maximum width of the spiral gap; and
A spiral heat exchanger for exchanging heat between the high-viscosity fluid flowing through the central gap and the spiral gap in a direction substantially along the axis, and the heat exchange medium,
A spiral heat exchanger comprising an inflow restricting means for restricting inflow of the high-viscosity fluid into the center gap.

  According to the means 3, the inflow of the high-viscosity fluid into the center gap can be restricted by providing the inflow restricting means. As a result, a situation in which the high-viscosity fluid concentrates and flows with respect to the central portion of the central gap does not occur, and the high-viscosity fluid passes through the spiral gap. Therefore, heat exchange between the high-viscosity fluid and the heat exchange medium can be performed efficiently, and the high-viscosity fluid can be adjusted to a desired temperature in a relatively short period of time and with high accuracy.

  Means 4. 4. The spiral according to claim 3, wherein the inflow restricting means is constituted by an opening at both ends in the axial direction of the center gap, and a closed wall portion that closes a boundary between the center gap and the spiral gap. Type heat exchanger.

  According to the means 4, basically the same effects as the means 3 are obtained. In addition, according to the present means 4, the inflow restricting means is a relatively simple method in which the opening at both ends in the axial direction of the center gap and the boundary between the center gap and the spiral gap are closed by the closing wall. Can be realized. Therefore, it is possible to suppress as much as possible the cost associated with the arrangement of the inflow restricting means, the increase in labor required to dispose the inflow restricting means, and the like.

Means 5. Comprising the spiral heat exchanger according to any one of means 1 to 4,
An engine performance test apparatus configured to supply a high-viscosity fluid cooled by the spiral heat exchanger to the engine.

  In the engine performance test apparatus for supplying a high-viscosity fluid to the engine as in the above means 5, the temperature of the high-viscosity fluid may be adjusted by a spiral heat exchanger such as the above-described means 1. In this case, basically the same effects as those of the means 1 and the like are obtained.

  Hereinafter, an embodiment will be described with reference to the drawings. FIG. 1 is a block diagram of a high-viscosity fluid cooling system 1 as an engine performance test apparatus including a spiral heat exchanger 7 which is a feature of the present invention. In this embodiment, the high-viscosity fluid cooling system 1 is mainly used when testing engine performance in a low temperature environment.

  As shown in FIG. 1, the high-viscosity fluid cooling system 1 includes a vacuum pump 3 that sucks engine oil after a predetermined test that lubricates each friction portion of the engine 2, an engine oil extracted from the engine 2, and a predetermined engine oil. A cooler 4 that exchanges heat between cooling water, an oil tank 5 that can store engine oil cooled by the cooler 4, and an engine that is temporarily stored in the oil tank 5 and the passage of engine oil before and after the oil tank 5 A spiral heat exchanger 7 that performs heat exchange between oil and brine (coolant) as a heat exchange medium cooled by the cooling device 8 is provided. In FIG. 1, the circulation circuit of the cooling water supplied to the cooler 4 is omitted for convenience. In the present embodiment, the engine oil corresponds to a high viscosity fluid.

  First, the engine oil circulation circuit will be mainly described. The engine oil passage (flow path) includes a first flow path 11 that communicates between the engine 2 and the cooler 4, a second flow path 12 that communicates between the cooler 4 and the oil tank 5, and an oil tank 5 and a spiral type. A third flow path 13 that communicates with the heat exchanger 7, and a supply branch path 14 a that extends from the spiral heat exchanger 7 and communicates with the engine 2 and a circulation branch path 14 b that communicates with the oil tank 5. There is a fourth flow path 14 that branches into The circulation branch 14 b is directly connected to the oil tank 5 and does not merge with the second flow path 12 and the third flow path 13.

  The engine oil circulation circuit includes a first valve 21 for opening and closing the first flow path 11, a second valve 22 for opening and closing the second flow path 12, a third valve 23 for opening and closing the supply branch 14a, and a circulation branch. A fourth valve 24 that opens and closes the passage 14b and a fifth valve 25 that opens and closes a vent pipe that ventilates the inside of the cooler 4 and the space of the external environment such as the atmosphere are provided. For example, when the engine oil in the engine is drained after the engine bench test is performed under different conditions, the first valve 21, the second valve 22, and the fifth valve 25 are closed and the vacuum is set. The pump 3 is operated for an arbitrary time, and the space between the first valve 21 and the second valve 22 is set to a vacuum state. Thereafter, by opening the first valve 21, warm engine oil in the engine 2 is extracted and collected in the cooler 4. After the engine oil is cooled to some extent in the cooler 4, the second valve 22 and the fifth valve 25 are opened, so that the engine oil is drawn by gravity or the oil pump 6 provided in the third flow path 13. It is transferred from the cooler 4 to the oil tank 5 by force.

  Further, when the engine oil is cooled in the spiral heat exchanger 7, the first valve 21, the second valve 22, and the third valve 23 are closed, and the fourth valve 24 is opened. . As a result, the engine oil is cooled in the spiral heat exchanger 7 while circulating through the third flow path 13, the fourth flow path 14, and the circulation branch 14b. In this embodiment, the oil pump 6 smoothly circulates and conveys the engine oil described above.

  On the other hand, when supplying engine oil to the engine 2, the third valve 23 is opened, and the first valve 21 and the fourth valve 24 are closed. As a result, the engine oil circulated by the conveying force of the oil pump 6 and cooled to a predetermined temperature is sequentially sent to the oil pan of the engine 2 through the supply branch 14a. The amount of engine oil supplied to the engine 2 is measured by a flow meter 9 provided in the supply branch 14a. When a predetermined amount of engine oil is supplied to the engine 2, the third valve 23 is It is supposed to be closed.

  Next, a brine circulation circuit that is supplied to the spiral heat exchanger 7 and exchanges heat with engine oil will be described. As the flow path of the brine, the recovery path 31 for sending the brine discharged from the spiral heat exchanger 7 to the cooling device 8, and the sending for sending the brine cooled in the cooling device 8 to the spiral heat exchanger 7 The communication path 32, the recovery path 31 and the delivery path 32, the first bypass path 33 capable of sending brine from the circuit path 31 side to the delivery path 32 side, and the recovery path 31 and the delivery path 32, A second bypass path 34 capable of sending brine from the delivery path 32 side to the recovery path 31 side is provided. Of the delivery path 32, the part closer to the cooling device 8 than the first bypass path 33 and the part closer to the spiral heat exchanger 7 than the second bypass path 34 (of both connecting portions with the bypass paths 33 and 34). The flow path between them is referred to as the pre-adjustment delivery path 32a and the part closer to the spiral heat exchanger 7 than the first bypass path 33 is referred to as the post-adjustment delivery path 32b.

  In the connecting portion between the first bypass path 33 and the delivery path 32, the flow rate of brine flowing from the first bypass path 33 to the adjusted delivery path 32b and the flow from the pre-adjustment delivery path 32a to the adjusted delivery path 32b. A three-way valve 41 capable of adjusting the flow rate of the brine is provided. By adjusting the three-way valve 41, the flow rate of the brine flowing through the first bypass path 33 and the pre-adjustment delivery path 32a is adjusted, and thereby the spiral heat exchanger 7 is adjusted through the post-adjustment delivery path 32b. It is possible to adjust the temperature of the brine supplied to, that is, the cooling capacity of the spiral heat exchanger 7. The second bypass passage 34 is still provided with a return valve 42 that can adjust the flow rate of the brine flowing through the second bypass passage 34.

  In addition, refrigerant pumps 47 and 48 are provided in the middle of the delivery path 32 to smoothly circulate the brine described above. Further, the adjusted delivery path 32b is provided with a refrigerant temperature measuring device 49 for measuring the temperature of the brine. Thereby, the temperature of the brine supplied to the spiral heat exchanger 7 can be grasped.

  Further, an oil temperature measuring device 43 for measuring the temperature of the engine oil sent from the spiral heat exchanger 7 is provided in the vicinity of the engine oil outlet of the spiral heat exchanger 7 in the fourth flow path 14. Is provided. Further, based on the brine temperature supplied to the spiral heat exchanger 7 output from the refrigerant temperature measuring device 49 and the engine oil temperature output from the oil temperature measuring device 43, the three-way valve 41 and A controller 45 that controls the return valve 42 is provided. The controller 45 adjusts the engine oil supplied to the engine 2 to a desired temperature.

  Here, the engine oil temperature adjustment method will be described in detail. For example, when it is desired to greatly reduce the temperature of the engine oil, the controller 45 disables the first bypass path 33 and the second bypass path 34 and sends the output before adjustment. The three-way valve 41 and the return valve 42 are adjusted so that all the brine that has passed through the cooling device 8 passes through the passage 32a. As a result, the brine circulates in the recovery path 31 and the delivery path 32, and the brine heat-exchanged in the spiral heat exchanger 7 is always cooled by the cooling device 8, and the brine cooled by the cooling device 8 remains as it is. It is sent to the spiral heat exchanger 7.

  On the other hand, for example, when it is not desired to lower the temperature of the engine oil, the controller 45 disconnects between the pre-adjustment delivery path 32a and the post-adjustment delivery path 32b, and the brine spirals with respect to the first bypass path 33. The three-way valve 41 and the return valve 42 are adjusted to pass the same amount as passing through the heat exchanger 7. Thereby, the brine discharged from the spiral heat exchanger 7 is directly cooled without being cooled by the cooling device 8 via the recovery path 31, the first bypass path 33, and the adjusted delivery path 32b. The brine returned to the vessel 7 and supplied from the cooling device 8 is directly supplied to the spiral heat exchanger 7 without being supplied to the spiral heat exchanger 7 via the delivery path 32, the second bypass path 34, and the recovery path 31. Returned to 8.

  The two examples introduced here are those in an extreme case. Usually, in the three-way valve 41, the uncooled brine flowing in from the first bypass passage 33 and the pre-adjustment sending passage 32a flowed in. The brine whose temperature is adjusted by mixing with the cooled brine is supplied to the spiral heat exchanger 7.

  Next, the configuration of the spiral heat exchanger 7 which is a feature of the present invention will be described in detail. In the present embodiment, the spiral heat exchanger 7 includes a cylindrical casing 71 and a medium circulation portion 72 disposed in the casing 71 as shown in FIGS. 2 and 3. It is configured.

  The casing 71 is formed of a relatively thick metal material, has sufficient mechanical strength, and includes an internal space 71a extending along the direction of the axis CL. A hole 71 b communicating with the delivery path 32 is formed in a substantially central portion in the axis CL direction of the outer peripheral wall portion of the casing 71. Furthermore, a lid portion 73 and a bottom portion 74 are provided at both ends of the casing 71 in the direction of the axis CL so as to close both end openings of the casing 71. The lid portion 73 extends along the axis CL, and includes an oil inlet 73a for introducing engine oil into the casing 71. The oil inlet 73a extends from the oil pump 6. It communicates with the road 13. On the other hand, the bottom portion 74 includes a first oil delivery port 74a extending along the axis CL and a second oil delivery port 74b extending in a direction orthogonal to the axis CL. The oil outlets 74a and 74b communicate with the fourth flow path 14, and the engine oil flows out to the fourth flow path 14 through the oil outlets 74a and 74b. It is like that.

  The medium circulation part 72 is a member in which a hollow member is wound in a spiral shape, and brine supplied from the cooling device 8 side circulates therein. That is, the medium circulation part 72 includes an outer wall 72a and an inner wall 72b that face each other at a predetermined interval on most of the side surfaces, an end portion on the axis line CL side (one end side) of the outer wall 72a, and an axis line CL of the inner wall 72b. And a central wall 72e for connecting the side (one end side) end portions. In addition, the medium flow portion 72 has both end openings formed between both end edges in the axis CL direction of the outer wall 72a and both end edges in the axis CL direction of the inner wall 72b and the center wall 72e adjacent to the inside of the outer wall 72b. In addition, the opening on both ends formed between the both ends of the outer wall 72a on the outer peripheral side of the axial line CL direction and the inner peripheral surface of the casing 71 facing the inner peripheral surface of the casing 71 is closed and spirally viewed in plan view. An upper wall portion 72c and a lower wall portion 72d.

  In addition, the outer peripheral side (other end side) end of the inner wall 72b protrudes from the inner peripheral surface of the casing 71 and is joined to a rod-shaped first connection wall 75 extending in the direction of the axis CL. . On the other hand, the outer peripheral side (other end side) end of the outer wall 72a protrudes from the inner peripheral surface of the casing 71 at a position facing the first connecting wall 75 across the axis CL. It joins with respect to the formed rod-shaped 2nd connection wall 76. FIG. Thereby, the delivery path 32 and the internal space of the medium circulation part 72 are communicated with each other through the hole 71b, and the internal space 71a in the casing 71 and the internal space of the medium circulation part 72 are divided. In other words, the engine oil and brine are not mixed. In addition, one end portion of the medium circulation portion 72 extends to the outside of the casing 71 and communicates with the recovery path 31 at the center portion (axis CL side) of the medium circulation portion 72. A cylindrical discharge cylinder 72f having an end communicating with the internal space near the axis CL of the medium circulation part 72 is provided. As a result of such a configuration, a flow path of brine that flows spirally in a direction substantially perpendicular to the axis CL from the hole 71b to the discharge tube 72f is formed inside the medium circulation portion 72 (in FIG. A part with a pattern) is formed.

  Further, the engine oil flowing in from the oil inlet 73a can pass between the outer peripheral side of the outer wall 72a of the medium flow part 72 and the inner peripheral side of the inner wall 72b, and between the inner wall 72b and the central wall 72e. A gap is formed. Specifically, the gap is formed by being sandwiched between the outer peripheral side of the outer wall 72a and the inner peripheral side of the inner wall 72b, and forms a spiral gap 78 that forms a spiral shape when viewed from the end side of the axis CL. And a central gap 77 formed by being sandwiched between the central wall 72e and the inner peripheral side of the inner wall 72b and spatially connected to the spiral gap 78. Here, in the present embodiment, the maximum width of the central gap 77 is made larger than the maximum width of the spiral gap 78. That is, the central gap 77 has a relatively large cross-sectional area in a cross section orthogonal to the axis CL, and engine oil tends to flow more concentratedly to the central gap 77 than the spiral gap 78. In other words, the engine oil is likely to drift.

  Therefore, in the present embodiment, in order to restrict the inflow of engine oil into the center gap 77, closed wall portions 81, 82, 83 as inflow restricting means are provided. More specifically, the closing wall portions 81 and 82 are made of a semicircular metal plate, and are joined to the opening portions at both ends so as to close both ends openings in the direction of the axis Cl of the center gap 77. . Further, the closing wall portion 83 is made of a flat metal plate having a length substantially the same as the length along the axis CL of the medium circulation portion 72 so as to close the boundary portion between the central gap 77 and the spiral gap 78. Thus, it is joined to the outer wall 72a, the inner wall 72b and the like located at the boundary portion.

  As described above in detail, according to the present embodiment, it is possible to regulate the inflow of engine oil into the center gap 77 by providing the closing wall portions 81 to 83 as inflow regulating means. As a result, a situation in which the engine oil flows in a concentrated manner to the center portion of the center gap 77 (a drift occurs) does not occur, and the engine oil mainly passes through the spiral gap 78. Become. Therefore, the heat exchange between the engine oil and the brine can be performed efficiently, and the engine oil can be adjusted to the desired temperature in a relatively short period of time and with high accuracy.

  Further, the inflow restricting means closes the opening at both ends of the center gap 77 in the axis CL direction and the boundary portion between the center gap 77 and the spiral gap 78 by the closing wall portions 81 to 83, that is, relatively simple. It is realized by the method. Therefore, it is possible to suppress as much as possible the cost associated with the arrangement of the inflow restricting means, the increase in labor required to dispose the inflow restricting means, and the like.

  In addition, it is not limited to the description content of the said embodiment, For example, you may implement as follows. Of course, other application examples and modification examples not illustrated below are also possible.

  (A) In the above embodiment, the closed wall portions 81 to 83 are provided to prevent the engine oil from flowing into the center gap 77. However, as shown in FIG. By providing the buried body 85, the engine oil may be prevented from flowing into the center gap 77. In this case, the same effects as those of the above embodiment are achieved.

  (B) In the above embodiment, the closed wall portions 81 to 83 are provided to prevent the engine oil from flowing into the center gap 77, thereby preventing the engine oil from drifting, and thus heat exchange between the engine oil and the brine. It is comprised so that it may perform efficiently. On the other hand, after allowing the engine oil to flow into the center gap 77, the pressure loss when the engine oil at the time of high viscosity (for example, engine oil of −20 ° C. to 0 ° C.) passes through the center gap 77. And a fluid movement restraining means for making the pressure loss when the engine oil passes through the spiral gap 78 substantially equal to prevent the engine oil from drifting to the center gap 77, It is good also as improving the heat exchange efficiency in between. As the fluid movement restricting means, for example, in order to increase the flow resistance of engine oil, it is provided on the inner wall 72b or the center wall 72e of the medium flow part 72 forming the center gap 77, and the gap in the radial direction or the axis CL direction is provided. A labyrinth seal-like uneven body that provides resistance to the flow of engine oil while holding the flow, and a flow composed of a plurality of mesh members provided across the inner wall 72b and the center wall 72e of the medium flow portion 72 that forms the center gap 77. A road resistor etc. can be mentioned.

  (C) The high-viscosity fluid cooling system in the above embodiment is mainly intended for cooling the engine oil supplied to the engine 2, but the engine is provided with a heater for heating engine oil, brine, and the like. The oil temperature may be adjusted over a wider range. In the above embodiment, the engine oil can be heated to some extent by utilizing the heat generated in the engine 2.

It is a block diagram which shows the structure of a high-viscosity fluid cooling system. It is a partially broken perspective view which shows the structure of a spiral type heat exchanger. It is a cross-sectional schematic diagram which shows the structure of a spiral heat exchanger. It is a partially broken perspective view which shows the structure of the spiral heat exchanger in another embodiment. It is a partially broken perspective view which shows the structure of the spiral type heat exchanger in a prior art. It is a cross-sectional schematic diagram which shows the structure of the spiral type heat exchanger in a prior art. It is a graph which shows the relationship between a viscosity and temperature in two types of engine oil.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... High viscosity fluid cooling system as an engine performance test apparatus, 2 ... Engine, 7 ... Spiral heat exchanger, 72 ... Medium distribution part, 72a ... Outer wall, 72b ... Inner wall, 72e ... Center wall, 77 ... Center gap, 78 ... spiral gap, 81, 82, 83 ... closed wall portion as inflow restricting means, 85 ... buried body as inflow restricting means, CL ... axis.

Claims (5)

An inner wall and an outer wall provided at a predetermined interval with respect to the inner wall are spirally formed with respect to the axis, and the inside of the spiral space surrounded by the inner wall and the outer wall is substantially the same as the axis. Comprising a medium flow part through which the heat exchange medium flows in the orthogonal direction;
Outside the media distribution unit,
A spiral gap formed between the inner peripheral side of the inner wall and the outer peripheral side of the outer wall, forming a spiral shape, and
A central gap is formed between the inner wall and the central wall that connects at least the axial side end of the inner wall and the axial side end of the outer wall, and is connected to the spiral gap. ,
The maximum width of the central gap is set larger than the maximum width of the spiral gap; and
A spiral heat exchanger for exchanging heat between the high-viscosity fluid flowing through the central gap and the spiral gap in a direction substantially along the axis, and the heat exchange medium,
A labyrinth seal-like fluid movement suppression means is provided in the center gap, and when the high viscosity fluid has a maximum viscosity that can flow through the center gap, a pressure loss when the high viscosity fluid flows through the center gap is A spiral heat exchanger characterized in that the high-viscosity fluid is substantially equal to a pressure loss when flowing through the spiral gap. An inner wall and an outer wall provided at a predetermined interval with respect to the inner wall are spirally formed with respect to the axis, and the inside of the spiral space surrounded by the inner wall and the outer wall is substantially the same as the axis. Comprising a medium flow part through which the heat exchange medium flows in the orthogonal direction;
Outside the media distribution unit,
A spiral gap formed between the inner peripheral side of the inner wall and the outer peripheral side of the outer wall, forming a spiral shape, and
A central gap is formed between the inner wall and the central wall that connects at least the axial side end of the inner wall and the axial side end of the outer wall, and is connected to the spiral gap. ,
The maximum width of the central gap is set larger than the maximum width of the spiral gap; and
A spiral heat exchanger for exchanging heat between the high-viscosity fluid flowing through the central gap and the spiral gap in a direction substantially along the axis, and the heat exchange medium,
A pressure when the high-viscosity fluid flows through the central gap when the high-viscosity fluid has a maximum viscosity at which the high-viscosity fluid can flow through the central gap is provided in the central gap with a fluid flow suppression means using a net-like channel resistor A spiral heat exchanger characterized in that the loss is substantially equal to the pressure loss when the high-viscosity fluid flows through the spiral gap. An inner wall and an outer wall provided at a predetermined interval with respect to the inner wall are spirally formed with respect to the axis, and the inside of the spiral space surrounded by the inner wall and the outer wall is substantially the same as the axis. Comprising a medium flow part through which the heat exchange medium flows in the orthogonal direction;
Outside the media distribution unit,
A spiral gap formed between the inner peripheral side of the inner wall and the outer peripheral side of the outer wall, forming a spiral shape, and
A central gap is formed between the inner wall and the central wall that connects at least the axial side end of the inner wall and the axial side end of the outer wall, and is connected to the spiral gap. ,
The maximum width of the central gap is set larger than the maximum width of the spiral gap; and
A spiral heat exchanger for exchanging heat between the high-viscosity fluid flowing through the central gap and the spiral gap in a direction substantially along the axis, and the heat exchange medium,
A spiral heat exchanger comprising an inflow restricting means for restricting inflow of the high-viscosity fluid into the center gap.   The said inflow control means is comprised by the closed wall part which closes the axial direction both ends opening part of the said center gap, and the boundary part of the said center gap and the said spiral-shaped gap. Spiral heat exchanger. A spiral heat exchanger according to any one of claims 1 to 4, comprising:
An engine performance test apparatus configured to supply a high-viscosity fluid cooled by the spiral heat exchanger to the engine.

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