JP2007003080A - Evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To equalize inflow amounts of refrigerant to each of tubes from an inlet side to a depth side of a tank to equalize a temperature of heat exchanged-air in the entire evaporator. <P>SOLUTION: In this evaporator 1 comprising the plurality of tubes 2A-2F, the inlet-side tank 4 in which one end side of each of the tubes 2A-2F is inserted to be communicated therewith, an outlet-side tank 5 in which the other end of each of the tubes 2A-2F is inserted to be communicated therewith, a refrigerant inlet pipe 6 connected with the inlet-side tank 4 for supplying a refrigerant 11 into the inlet-side tank 4, and a refrigerant outlet pipe 7 connected with the outlet-side tank 5 and discharging the refrigerant 11 flowing in the tubes 2A-2F to the external, SC/SA=0.3-0.6 is satisfied, when a tank internal cross-sectional area at a position where the tube 2 is inserted into the inlet-side tank 4 is SA, and a refrigerant passing cross-sectional area through which the refrigerant 11 can be passed at that position is SC. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an evaporator used, for example, in an automobile air conditioner.

  Conventionally, as this type of evaporator, for example, an evaporator 101 having a structure as shown in FIGS. 5 and 6 has been disclosed (see, for example, Patent Document 1).

  As shown in FIG. 5, the evaporator 101 has a flat liquid passage tube 103 in which a plurality of parallel and independent branching flow passages 102 are formed, connected from an inlet portion 104 at one end to an outlet portion 105 at the other end. In this structure, the corrugated fins 107 are interposed between the liquid passing pipes 103 in the meandering portion 106.

  In this evaporator 101, as shown in FIG. 6, from the downstream end in the air flow direction A of the fluid supply conduit 108 provided at the inlet 104 and the fluid discharge conduit 109 provided at the outlet 105. The upstream end portion is configured so that the distance between the conduits 108 and 109 and the inner walls 108a and 109a becomes wider. That is, at the upstream end portion in the air flow direction A, the interval between the inner peripheral walls 108a and 109a of the respective conduits 108 and 109 and the opening ends 110 and 111 of the branch flow path 102 is set large, and this is reduced on the downstream side. This makes it difficult for fluid (refrigerant) to flow through the branch channel on the side in contact with the inflowing air.

With this configuration, the fluid that has flowed in from the fluid supply conduit 108 does not easily flow into the open end 110a of the branch flow channel 102 that is positioned on the near side when flowing into the liquid passage tube 103, and has a wide back space. A large amount will flow from the open end 110a of the partial branch flow path 102. If the flat fluid passage 103 protruding to the respective conduits 108 and 109 is flattened without being inclined in this way, a large amount of fluid flows into the branch channel 102 near the fluid inlet, and the fluid flows into the rear branch channel 102. The inflow is reduced, and the air temperature that is heat-exchanged by the part of the evaporator varies due to the flow rate variation. However, with this structure, the heat exchange effect is homogenized over the entire evaporator, and the heat exchange efficiency is improved.
Japanese Utility Model Publication No. 59-3251 (see page 2, FIGS. 4 to 6)

  However, in the evaporator 101 described in Patent Document 1, as shown in FIG. 7, the fluid 112 flows between the flat liquid passage 103 and the conduits 108 and 109 through the side surface of the flat liquid pipe 103. There are gaps 113A and 113B.

  Therefore, even if the amount of protrusion of the flat liquid passage 103 on the fluid inlet side is increased to make it difficult for the fluid 112 to flow into the branch flow path 102 on the inlet side, the side surface of the flat liquid passage 103 and the conduit 108, The fluid 112 flows from the gaps 113 </ b> A and 113 </ b> B with respect to 109, and as a result, a large amount of the fluid 112 flows into the branch channel 102 near the inlet.

  Therefore, the present invention has been made in view of the above-described problems, and uniformizes the inflow amount of refrigerant into each tube from the inlet side to the back side of the tank, and the temperature of the air to be heat-exchanged there is an evaporator. An object is to provide an evaporator that can be uniformized as a whole.

  The invention described in claim 1 includes a plurality of tubes, an inlet side tank in which one end side of each tube is inserted and communicated, an outlet side tank in which the other end side of each tube is inserted and communicated, and Evaporation comprising a refrigerant inlet pipe connected to the inlet side tank for supplying refrigerant into the inlet side tank, and a refrigerant outlet pipe connected to the outlet side tank for discharging the refrigerant flowing through the tubes. SC / SA = 0 where SA is the cross-sectional area in the tank where the tube is inserted into the inlet side tank, and SC is the cross-sectional area through which the refrigerant can pass at that position. .3 to 0.6.

  A second aspect of the present invention is the evaporator according to the first aspect, wherein the tube with SC / SA = 0.3 to 0.6 is at least near the inlet side of the inlet side tank. It is characterized by providing.

  Invention of Claim 3 is an evaporator of Claim 1 or Claim 2, Comprising: The insertion part of the tube inserted in the said inlet side tank has obstruct | occluded the flow path in a tank. It is characterized by.

  According to the first aspect of the present invention, when the cross-sectional area in the tank at the position where the tube is inserted into the inlet side tank is SA, and the refrigerant passing cross-sectional area through which the refrigerant can pass at that position is SC. , SC / SA = 0.3 to 0.6, the refrigerant passage cross-sectional area through which the refrigerant can pass is narrowed by the tube protruding into the tank, so that the flow velocity of the refrigerant flowing therethrough increases and the depth from the inlet increases. More refrigerant flows into the Therefore, the refrigerant flows evenly to each tube from the state where more refrigerant flows more easily on the inlet side than on the back side of the tank, and the amount of refrigerant flowing into each tube from the tank inlet to the back is made uniform. The temperature of the air to be heat exchanged can be made uniform throughout the evaporator.

  According to the second aspect of the present invention, each tube inserted into the inlet side tank is provided at least in the vicinity of the inlet side of the inlet side tank with a tube having SC / SA = 0.3 to 0.6. The flow rate of the refrigerant flowing to the tube can be made uniform.

  According to the invention described in claim 3, since the insertion portion of the tube inserted into the inlet side tank closes the tank flow path, the refrigerant is prevented from flowing from between the tube side surface and the tank. it can.

  Hereinafter, specific embodiments to which the present invention is applied will be described in detail with reference to the drawings. In addition, this Embodiment is an example which applied this invention to the evaporator of the air conditioning apparatus for motor vehicles.

  FIG. 1 is a perspective view of the evaporator according to the present embodiment, FIG. 2 is an enlarged cross-sectional view of the main part at the position AA in FIG. 1, and FIG. 3A is an enlarged main part at the position BB in FIG. FIG. 3B is a cross-sectional view, FIG. 3B is an enlarged cross-sectional view of a main part at the position of line CC in FIG. 2, and FIG.

  As shown in FIGS. 1 and 2, the evaporator 1 includes a plurality of tubes 2 (2 </ b> A to 2 </ b> F), a corrugated outer fin 3 disposed between the tubes 2, and one end side of each tube 2. The inlet side tank 4 inserted and communicated with each other, the outlet side tank 5 inserted and communicated with the other end side of each tube 2, and the inlet side tank 4 connected to the inlet side tank 4 receive the refrigerant in the inlet side tank 4. A refrigerant inlet pipe 6 to be supplied and a refrigerant outlet pipe 7 that is connected to the outlet side tank 5 and discharges the refrigerant circulated through the tubes 2 to the outside are provided.

  The tube 2 is formed as a flat tube having a refrigerant flow hole 8 through which a refrigerant flows. In the present embodiment, six tubes 2 are used. The outer fin 3 has a corrugated shape and is provided in contact with the tubes 2 arranged at a predetermined interval.

  The inlet side tank 4 includes a seat plate 4A for inserting and holding one end side of the tube 2 at a predetermined interval, and a tank member 4B attached to the seat plate 4A, and is formed by the seat plate 4A and the tank member 4B. This space is used as the in-tank flow path 9 for refrigerant inflow.

  Similarly to the inlet side tank 4, the outlet side tank 5 includes a seat plate 5A for inserting and holding the other end of the tube 2 at a predetermined interval, and a tank member 5B attached to the seat plate 5A. A space formed by the plate 5A and the tank member 5B is used as an in-tank flow path for refrigerant outflow (not shown).

  The refrigerant inlet pipe 6 is attached to one side surface of the tank member 4 </ b> B in the inlet side tank 4 and allows the refrigerant to flow into the inlet side tank 4. The refrigerant outlet pipe 7 is attached to one side surface of the tank member 5 </ b> B in the outlet side tank 5, and causes the refrigerant to flow out of the evaporator 1 from the outlet side tank 5.

  In the present embodiment, the inlet side tank 4 and the tube 2 are, as shown in FIG. 3, the insertion portion 2a of the tube 2 (2A) inserted into the inlet side tank 4 being the inner wall surface of the tank member 4B. 4b is provided in contact with the gap so as not to occur, and the lower end side of the in-tank flow path 9 is closed. The outlet side tank 5 and the tube 2 have the same structure.

  In the present embodiment, as shown in FIG. 2, the three tubes 2 </ b> A, 2 </ b> B, and 2 </ b> C from the inlet side of the inlet side tank 4 toward the back have an insertion portion 2 a of about H in the tank. It protrudes to half the position. The remaining three tubes 2D, 2E, and 2F differ from the tubes 2A, 2B, and 2C in the vicinity of the inlet side, and their insertion portions 2a slightly protrude into the tank.

  Further, in the present embodiment, the three tubes 2A, 2B, 2C provided in the vicinity of the inlet side have a tank cross-sectional area SA at the tube insertion position, and the refrigerant 11 can pass therethrough. SC / SA = 0.3 to 0.6 when the refrigerant cross-sectional area is SC.

  As described above, the structure in which the lower half of the in-tank flow path 9 is closed by the insertion portion 2a of the tube 2 allows the refrigerant 11 flowing from the refrigerant inlet pipe 6 into the inlet side tank 4 to flow into the inlet side. It flows in from the tube 2A to the back tube 2B, 2C,. At this time, in the portion where the three tubes 2A, 2B, and 2C provided in the vicinity of the inlet side are disposed, the refrigerant passage interruption described above compared to the three tubes 2D, 2E, and 2F provided on the back side. Since the area SC is narrowed, the speed at which the refrigerant 11 gets over each of the tubes 2A, 2B, 2C is increased, and more refrigerant 11 flows from the inlet side of the inlet side tank 4 to the back.

  As a result, the refrigerant 11 flows evenly to the tubes 2A to 2F from the state in which the refrigerant 11 more easily flows on the inlet side than on the back side of the tank, and reaches the tubes 2A to 2F extending from the tank inlet to the back. The inflow amount of the refrigerant 11 is made uniform, and the temperature of the air exchanged therewith can be made uniform throughout the evaporator.

  The inventors increase the amount of projection of the three tubes 2A, 2B, 2C provided in the vicinity of the inlet side into the inlet side tank 4 (narrow the refrigerant passage cross-sectional area SC), and the refrigerant 11 It was confirmed by experiments that the speed at which the tubes 2A, 2B and 2C were moved over was increased and the amount of refrigerant passing through was increased. In the experiment, among the six tubes 2A to 2F, the amount of protrusion of the three tubes 2A, 2B and 2C on the inlet side into the tank is changed, and the flow rate of the refrigerant flowing into each tube 2A to 2F at that time Was measured. The result is shown in FIG.

  As can be seen from this result, if the refrigerant passage cross-sectional area SC is narrowed within a certain range by the protrusion of the tube 2, the flow rate variation of the refrigerant 11 flowing into each tube 2 can be eliminated to a negligible level. Specifically, if SC / SA is in the range of 0.3 to 0.6, the variation in the refrigerant flow rate flowing into the tubes 2A to 2F can be ignored in practice.

  As described above, according to the evaporator 1 of the present embodiment, the cross-sectional area in the tank at the position where the tube 2 is inserted into the inlet side tank 4 is SA, and the cross-sectional area through which the refrigerant 11 can pass at that position. If SC / SA = 0.3-0.6, the refrigerant passage cross-sectional area SC through which the refrigerant 11 can pass is narrowed by the tube 2 protruding into the tank, and flows therethrough. The flow rate of the refrigerant 11 increases and more refrigerant 11 flows from the inlet to the back. Accordingly, the refrigerant 11 flows evenly from the state where the refrigerant 11 flows more easily on the inlet side than the rear side of the inlet side tank 4 to the tubes 2A to 2F, and to the tubes 2A to 2F extending from the tank inlet to the back. The flow rate of the refrigerant 11 is made uniform, and the temperature of the air exchanged therewith can be made uniform throughout the evaporator 1.

  Further, according to the evaporator 1 of the present embodiment, if the tubes 2A to 2C with SC / SA = 0.3 to 0.6 are provided at least in the vicinity of the inlet side of the inlet side tank 4, the inlet The flow rate of the refrigerant 11 flowing to the tubes 2A to 2F inserted in the side tank 4 can be made uniform.

  Moreover, according to the evaporator 1 of this Embodiment, since the insertion part 2a of the tubes 2A-2F inserted in the inlet side tank 4 has block | closed the flow path 9 in a tank, a tube side surface, a tank, It can prevent that the refrigerant | coolant 11 flows from between.

  Although specific embodiments to which the present invention is applied have been described above, the above-described embodiments are merely examples of the present invention, and the present invention is not limited to these embodiments.

It is a perspective view of the evaporator of this Embodiment. It is a principal part expanded sectional view in the AA line position of FIG. 3A is an enlarged cross-sectional view of the main part at the position of the line BB in FIG. 2, and FIG. 3B is an enlarged cross-sectional view of the main part at the position of the line CC in FIG. It is a characteristic view which shows the refrigerant | coolant flow volume distribution which flows in into each tube. It is a perspective view of the conventional evaporator. 6A is a cross-sectional view of the main part on the fluid inlet side in FIG. 5, and FIG. 6B is a cross-sectional view of the main part on the fluid outlet side in FIG. It is a principal part expanded sectional view which shows the state by which the liquid penetration pipe was inserted in the conduit | pipe of the evaporator of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Evaporator 2 (2A-2F) ... Tube 3 ... Outer fin 4 ... Inlet side tank 4A ... Seat plate 4B ... Tank member 5 ... Outlet side tank 5A ... Seat plate 5B ... Tank member 6 ... Refrigerant inlet pipe 7 ... Refrigerant Outlet pipe 8 ... Refrigerant flow passage 9 ... Tank passage 11 ... Refrigerant

Claims (3)

Multiple tubes (2), an inlet side tank (4) in which one end side of each tube (2) is inserted and communicated, and an outlet side in which the other end side of each tube (2) is inserted and communicated A tank (5), a refrigerant inlet pipe (6) connected to the inlet side tank (4) and supplying refrigerant into the inlet side tank (4), and each tube connected to the outlet side tank (5) (2) In the evaporator (1) provided with the refrigerant outlet pipe (7) for discharging the refrigerant (11) circulated inside to the outside,
When the sectional area in the tank at the position where the tube (2) is inserted into the inlet side tank (4) is SA and the sectional area through which the refrigerant (11) can pass at that position is SC. SC / SA = 0.3-0.6 The evaporator characterized by the above-mentioned. The evaporator according to claim 1, comprising:
The tubes (2A to 2C) having SC / SA = 0.3 to 0.6 are provided at least in the vicinity of the inlet side of the inlet side tank (4). An evaporator according to claim 1 or claim 2, wherein
The evaporator, wherein the insertion portion (2a) of the tube (2) inserted into the inlet side tank (4) closes the tank flow path (9).

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