KR20020054726A - capillary tube type Heat exchanger - Google Patents

Abstract

PURPOSE: A fine diameter pipe type heat exchanger is provided to improve efficiency of heat transfer by reducing heat resistance due to remaining condensed water. CONSTITUTION: A heat exchanger includes a fine diameter pipe whose outer diameter is smaller than 6mm; fins(20b) having pipe insertion holes(21) formed in longitudinal direction on a part to which air flows in and a part from which air is discharged; and slits(22b',22b'') formed between the pipe insertion holes so that shapes of the slits are different between the slits formed on upper parts of the fins, from an upper end to 2/3 of the lengths of the fins, and the slits formed on lower parts of the fin, from 2/3 of the lengths of the fins to the lower end of the fins.

Description

Capillary tube type heat exchanger

The present invention relates to a narrow tubular heat exchanger, and more particularly, to a slit shape formed on the fin surface.

Generally, the tubular heat exchanger is used in an air conditioner, a heat pump, and the like to control the temperature of air by using heat exchange between a refrigerant and air.

As illustrated in FIG. 1, the narrow tubular heat exchanger 1 includes a thin tubular tube 10 connected to each other by a U-shaped band through a refrigerant passing therein and formed of copper, or the like, such that aluminum may radiate heat. It is made of a pin (20a) formed.

At this time, the narrow tubular heat exchanger (1) is a heat exchanger using a narrow diameter tube (10) of 6mm or less, without using a tube having an outer diameter of 9.52mm to 7mm as in the prior art, which can withstand the high pressure of the refrigerant By forming pressure resistance, it is possible to reduce pressure loss and to cope with alternative refrigerant and material cost.

And, the fin 20a of the narrow tubular heat exchanger 1, as shown in Figure 2, when dividing the fin in accordance with the direction of air inflow, a plurality of tube insertion holes in the longitudinal direction in the air entering portion and the exiting portion 21 is formed, respectively, the tube insertion hole 21 formed in the exit portion and the tube insertion hole 21 formed in the entry portion are formed at a predetermined angle to form a zigzag.

At this time, four rows of slits 22a are formed between the tube insertion holes 21 in the longitudinal direction of the pin 20a, and each of the slits 22a has a longitudinal side surface symmetrical with each other, such as a louver. Cut out and exerted one side by applying force to the central part.

In general, the first row slits 221 'and 221 "and the four row slits 224' and 224" formed on the surface of the fin 20a are divided into two details in which the upper and lower parts are divided in order to make the flow rate of the inlet air uniform. The second row slits 222 'and 222 " and the third row slits 223' and 223 " are formed into one piece.

And, each slit (22a ', 22a ") is formed so that the end portion has a certain angle so as to surround the capillary tube is installed in the upper and lower parts to guide the inlet air to one of the three capillary tube to increase the flow rate.

When a narrow tubular heat exchanger having such a structure is used as an evaporator, a low temperature low pressure refrigerant flows in the narrow tubular tube, and air flows in a direction orthogonal thereto to exchange heat between the refrigerant and the inlet air.

At this time, the heat exchange between the refrigerant and the air absorbs the heat of the air by the difference in temperature when the heat of the air is transferred to the refrigerant by the temperature difference, and when the surface temperature of the fin and the tubular tube is lower than the dew point temperature of the air. It consists of latent heat transfer.

Accordingly, the condensate 30 formed by condensation of inlet air at the dew point temperature is formed on the surface of the heat exchanger 1, and the condensate 30 is fin 20a of the tubular heat exchanger 1. And it rides down the surface of the tubular tube 10 by gravity to be discharged to the outside of the heat exchanger.

However, since the diameter of the tubular heat exchanger 1 is small, the gap between the tube (see Fig. 1, 10) and the tube 10 and the gap between the fin 20a and the fin 20a are narrowly formed. Although the amount of the condensate 30 increases as the lower portion of the heat exchanger 1 decreases, the condensate 30 is not drained smoothly to the lower portion due to the surface tension by the slit 22a formed in the fin. See FIG. 2, 22a ', 22a ").

Such residual condensed water 30 interferes with heat transfer between the refrigerant and the fins 20a and heat transfer between the fins 20a and the inlet air, thereby reducing the heat transfer efficiency.

In addition, since the condensate 30 blocks the slits 22a '. 22a ", the pressure loss on the air side passing through the slits 22a', 22a" is increased to increase the power consumption of the fan for introducing air. .

In addition, the residual condensate 30 flows along the air flow direction, and is introduced into the room together with the air flowing into the room after heat exchange, thereby causing water splashing to the consumer, thereby reducing consumer reliability.

In addition, when the capillary heat exchanger is used in the heat pump, defrost water is generated according to the defrost, and the defrost water acts as a nucleus to generate frost, thereby rapidly creating frost, thereby lowering the capacity of the heat pump and reducing energy efficiency. Let's do it.

In order to solve the above problems, the present invention improves the heat transfer performance by reducing the thermal resistance caused by residual condensed water by improving the slit shape of the lower end of the fin so that condensed water can be smoothly discharged from the heat exchanger, while improving the pressure loss of air. The purpose of the present invention is to reduce power consumption and to reduce fan resistance, thereby improving power consumption.

In addition, when the capillary heat exchanger is used in the heat pump, the purpose is to reduce the efficiency of the heat pump by preventing the generation of frost by the residual defrost water.

1 is a perspective view showing a conventional tubular heat exchanger

2 is a front sectional view of a conventional tubular heat exchanger shown in FIG.

3 is a cross-sectional view A-A of FIG. 1 showing the flow of condensate;

Figure 4 is a front sectional view showing a fin constituting the tubular heat exchanger according to the first embodiment of the present invention

5 is a sectional view showing the main parts of the lower part of FIG.

6 is a front sectional view showing a fin constituting the tubular heat exchanger according to a second embodiment of the present invention.

`Shear view showing the fins constituting the tubular heat exchanger according to a third embodiment of the present invention

9 is a front sectional view showing a fin constituting the tubular heat exchanger according to a fourth embodiment of the present invention.

* Explanation of symbols in main part of drawing *

1: narrow tube type heat exchanger 10: narrow tube

20a, 20b, 20c, 20d, 20e: pin 21: tube insertion hole

22a, 22b, 22c, 22d: slit 30: condensate

221 ', 221 ": first row slit 222', 222 ″: second row slit

223 ', 223 ″: third row slit 224 ′, 224 ″: fourth row slit

To this end, the present invention is a narrow diameter tube having an outer diameter of 6 mm or less, and the tube insertion hole through which the narrow diameter tube passes is formed in a lengthwise direction in each of an inlet and an outlet portion bisected in the flow direction of air, and a total of two-thirds in the upper surface It is to provide a narrow tubular heat exchanger having a fin formed differently in the shape of the slit formed between the upper end portion up to the height and the lower end portion up to 1/3 height in the total longitudinal direction 1/3 height.

When describing the configuration and operation process according to the accompanying drawings, the tubular heat exchanger according to the present invention.

Figure 4 is a front sectional view showing a fin constituting the tubular heat exchanger according to the first embodiment of the present invention, Figure 5 is a sectional view of the main portion showing the lower end of Figure 4, Figure 6 according to a second embodiment of the present invention It is a front sectional view which shows the fin which comprises a tubular heat exchanger, and FIG. 7 is a principal sectional drawing which shows the lower end of the fin shown in FIG.

8 is a front sectional view showing fins constituting the tubular heat exchanger according to the third embodiment of the present invention, and FIG. 9 is a front sectional view showing fins constituting the tubular heat exchanger according to the fourth embodiment of the present invention. to be.

The narrow tubular heat exchanger according to the present invention is formed of a narrow tube (see Fig. 1, 10), which is a circular tube having a refrigerant flowing therein and an outer diameter of 6 mm or less, and an aluminum fin, which is used as a heat sink to effectively conduct heat transfer between the refrigerant and air ( 20b).

At this time, the fin 20b of the tubular heat exchanger, as shown in Figure 4, when dividing the fin 20b into a portion entering and exiting along the direction in which air flows, the tubular tube ( 10) is inserted into a plurality of pipe insertion holes 21 are spaced apart from each other in the longitudinal direction, the insertion and exit portion of the tube insertion hole 21 is located in a zigzag at a predetermined angle.

In the upper surface of the upper end of the fin, which is the height of the entire pin up to two-thirds of the length of the pin, four rows of slits enter and exit portions between the tube insertion hole 21 and the tube insertion hole 21. Each is formed.

At this time, the fourth row slit formed at the upper end of the pin 20b according to the present invention cuts out both side surfaces in the longitudinal direction which are symmetrical to each other, and extrudes by applying pressure to the central part thereof. The top and bottom are divided into two detail pieces so that the flow rate is uniformly formed, the second row and the third row are formed into one detail piece, and the ends of each slit are manufactured at a predetermined angle as in the prior art.

On the other hand, as shown in Fig. 5, between the tube insertion hole 21 and the tube insertion hole 21 on the surface of the pin 20b of the lower end of the pin, which is the height from the bottom surface of the pin to 1/3 of the total length of the pin Two rows of slits 22b 'and 22b "are provided, wherein only the first row slit 221' and the third row slit 223 'are formed in the entry portion of the fin 20b, and the second row slit is provided in the exit portion. Only 222 " and the fourth row slit 224 " are formed.

At this time, the first row slit 221 ′ and the fourth row slit 224 ″ are formed of two detailed pieces divided into upper and lower sides, and the slits 22b 'and 22b at both ends of the air inlet and the outgoing portion. The pin tip distance Lt up to ") is 0.5 mm or more to prevent pin tearing when the slits 22b 'and 22b' are manufactured.

Accordingly, both edges of the respective slits 221 'and 223' are formed at a pin tip length Lt of 0.5 mm or more at the lower end of the portion to be entered, and then the slit width (at the remaining length except the pin tip length Lt). The first row slit 221 'and the third row slit 223' are formed by forming the same Lw) and the slit gap Ls.

In addition, after leaving the pin tip length Lt of 0.5 mm or more at the lower end of the outgoing portion in the same manner as the slit formed at the lower end of the entering portion, the slit width Lw and the remaining length except for the two pin tip length Lt and The second row slit 222 " and the fourth row slit 224 " are formed to have the same slit gap Ls.

At this time, the first row slit 221 ′ and the third row slit 223 ′ of the air inlet portion are for inducing air into the tubules so that heat transfer is promoted, and the second row slit of the air outlet portion. Forming only 222 " and the fourth row slit 224 " is for uniformly forming the air flow rate after the heat exchanger.

Meanwhile, in the second embodiment according to the present invention, as shown in FIG. 6, four rows of slits are formed at the upper end of the fin 20c as in the first embodiment, and two rows of slits 22c 'and 22c "are formed at the lower end of the fin 20c. Pins 20c that are formed but not identical in shape are shown.

In other words, only the first row slit 221 ', 221 "and the third row slit 223', 223" are formed in the lower end of the fin 20c similarly to the entry part and the exit part.

The first row slits 221 ′ and 221 ″ are formed of two detailed pieces divided up and down, and the ends of each slit 22 c ′ and 22 c ″ have a predetermined slope.

Referring to FIG. 7 in more detail with reference to FIG. 7, the first row slit 221 ′, 221 ″ and the third row slit 223 ′, 223 formed in the entry and exit portions of the lower part 20c. ") Spaces the pin tip length Lt of 0.5 mm or more from both edges, and the slit width Lw and the slit gap Ls are equally formed at the remaining length except for each pin tip length Lt. 20c is fabricated on the upper surface, and each slit 221 ', 223' has the same width.

Alternatively, the fin 20d shown in the third embodiment of the present invention shown in FIG. 8 has a second row slit 222 ', 222 "between the entry and exit tube insertion holes 21 of the lower end of the fin. ) And the fourth row slit 224 ′, 224 ″.

The second row slits 22d 'and 22d " formed at the lower end of the pin are also left with a pin tip length Lt of 0,5 mm or more, as described in the above embodiment, and the slit width and the remaining length except the pin tip length. The second slit 222 'and 222 "and the fourth row slit 224' and 224" are formed by calculating the same slit interval.

Meanwhile, in the fourth exemplary embodiment according to the present invention, as shown in FIG. 9, the second row slits 22e 'and 22e "are formed at the lower end of the fin 20e, but the second row slits 222' are formed at the lower part of the fin 20e. Only the fourth row slit 224 ′ is formed, and the first row slit 221 ″ and the third row slit 223 ″ are formed in the exit portion.

Accordingly, the second row 222 ′ and the fourth row slit 224 ′ formed between the tube insertion holes of the portion into which the slit 22e ′ is uniformly divided by the remaining length except for the pin tip length Lt. The first row 221 " and the third row slit 223 "

According to the present invention, when a narrow tubular heat exchanger having fins 20b, 20c, 20d, and 20e having two rows of slits formed at the lower end thereof is used in an air conditioner and a heat pump, the air introduced in accordance with the rotation of the fan has a low temperature and low pressure. The refrigerant flows in a direction orthogonal to the narrow tubular tube 10 through which the refrigerant flows, and passes through the fins 20b, 20c, 20d, and 20e and the narrow tubular tube 10, and is discharged from the heat exchanger.

At this time, the air flow rate is reduced due to obstructions such as the tubular tube 10, but the air flow passes through the slits 22b, 22c, 20d, and 20e formed on the surfaces of the fins 20b, 20c, 20d, and 20e. The air flow rate of the inlet and the outlet portion guided by the uniformly formed to form a heat exchange with the refrigerant.

That is, inlet air is sensible heat transferred due to the temperature difference with the refrigerant on the surface of the heat exchanger, and the temperature drops. When the surface temperature of the fin and the tubular tube is lower than the dew point temperature of the air, latent heat is also transferred due to the humidity difference. The air, which has been formed into the furnace and whose temperature has fallen, is reintroduced into the room.

The condensate 30 formed as described above flows downward by gravity due to the surfaces of the fins 20b, 20c, 20d, and 20e of the heat exchanger and the tubular tube 10, thereby increasing the width and spacing between the slits 20b. 20c, 20d, and 20e are easily discharged to the outside.

At this time, in the first and second embodiments in which the first heat slit 221 'and the third heat slit 221' are formed in a portion where air enters, air is induced into the tubular tube to promote heat transfer. In the first and third embodiments in which only the second row slit 222 " and the fourth row slit 224 " are formed in the outgoing portion, the air flow rate downstream of the heat exchanger is formed uniformly, thereby reducing the flow noise.

In addition, in the third and fourth embodiments in which the second row slit 222 'and the fourth row slit 224' are formed in a portion where air enters, the flow rate of air flowing into the exit portion is uniformly formed. Heat transfer with the refrigerant flowing in the portion is promoted.

In the second and fourth embodiments, as shown in the inlet, the air flows into the pipe along the fin having the first row slit 221 " and the third row slit 223 " By induction, the heat transfer rates of the refrigerant and the air in the outgoing portion which are lower than the heat transfer rates of the refrigerant and the air occurring in the inlet portion are increased than before.

As described above, in the present invention, the upper end of the fin forms four rows of slits and the lower end of the fin forms two rows of slits, thereby guiding the flow of air to increase the flow rate, while condensate generated by heat exchange is smoothly at the lower part. Since it is discharged to the outside to reduce the heat resistance of the condensate, heat transfer performance is improved.

In addition, since residual condensed water does not remain in the slit, pressure loss of the air is reduced, thereby reducing fan resistance for introducing air, and thus power consumption.

In addition, when the heat exchanger is used in the heat pump, defrost water according to the defrost is generated to prevent the defrost water from acting as a nucleus to generate frost can prevent the reduction of the capacity and energy efficiency of the heat pump.

In addition, since the residual condensed water is smoothly discharged from the heat exchanger, it is introduced into the room to prevent water splashing to the consumer (carry over phenomena), thereby improving consumer reliability.

Claims (5)

Fine diameter tube less than 6mm of outer diameter, The tubular insertion hole through which the tubular tube passes is formed in the lengthwise direction at each of the inlet and the outlet portion divided into the air flow direction, and the upper end portion up to the entire 2/3 height from the upper side and the entire longitudinal direction 1/3 at the lower side. A narrow tubular heat exchanger having fins having different shapes of slits formed between the respective tube insertion holes at the lower end up to the height. The method of claim 1, The fin has a tubular heat exchanger, characterized in that four rows of slits are formed in each tube insertion work on the upper surface, and only two rows of slits are formed in each pipe insertion work on the lower surface. The method of claim 2, In the two rows of slits formed at the lower end of the fin, the first row and the fourth row are formed of two subpieces, and the second row and the third row are formed of one subpiece, so that the two subpieces and one subpiece are intersected. A tubular heat exchanger, characterized in that formed to be. The method of claim 2, The first and fourth rows of slits formed in the lower end of the fin is a narrow tubular heat exchanger, characterized in that the length of the tip of the fin is 0.5mm or more. The method of claim 4, wherein The slit formed on the lower end of the fin is a narrow tubular heat exchanger, characterized in that the remaining length except the length of the fin tip is the same as the slit width and the slit interval.