JP2011144989A - Heat transfer tube for heat exchanger, heat exchanger, refrigerating cycle device and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a heat transfer tube for a heat exchanger or the like improving adhesion between the heat transfer tube and a fin and capable of achieving a predetermined heat transfer performance without increasing pipe interior pressure loss. <P>SOLUTION: High mountains 22a and mountains 22b lower than the high mountains are formed spirally in the pipe axial direction on the inner face of the pipe 20 with a prescribed height. The high mountains 22a are provided to form 11-19 lines, and the low mountains 22a are provided to form 3-6 lines between the high mountains 22a. In the high mountains 22a, crests have a planar trapezoidal cross sectional shape before pipe expansion, and a ratio W1/D between the tip width W1 of the crest portion and the outer diameter D of the heat transfer tube 20 after pipe expansion is set to be 0.011-0.040. The high mountains 22a before pipe expansion are formed to be higher than the low mountains 22b by ≥0.04 mm. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a heat exchanger tube for a heat exchanger having a groove on the inner surface of the tube, a heat exchanger, a refrigeration cycle apparatus, and an air conditioner.

  2. Description of the Related Art Conventionally, in a heat exchanger used for a refrigeration apparatus, an air conditioner, a heat pump, or the like, generally, a plurality of fins arranged at a predetermined interval are provided with through holes, and heat transfer tubes having grooves formed on the inner surfaces are arranged in the through holes. The heat transfer tube becomes a part of the refrigerant circuit in the refrigeration cycle apparatus, and the refrigerant (fluid) flows inside the tube.

  The groove on the inner surface of the tube is processed so that the tube axis direction and the direction in which the groove extends form a certain angle. Here, although the inner surface of the tube is uneven by forming the groove, the space of the concave portion is defined as a groove portion, and the convex portion formed by the side wall of the adjacent groove is referred to as a peak portion.

  And the refrigerant | coolant which flows through such a heat exchanger tube carries out a phase change (condensation or evaporation) by heat exchange with the air etc. outside a heat exchanger tube. In order to efficiently perform this phase change, the heat transfer performance of the heat transfer tube is improved by increasing the surface area in the tube, the fluid stirring effect due to the groove, the liquid film holding effect between the grooves due to the capillary action of the groove, etc. (For example, refer to Patent Document 1).

JP-A-60-142195 (2nd page, FIG. 1)

  The heat transfer tube of Patent Document 1 as described above is generally made of a metal of copper or a copper alloy. And in manufacture of a heat exchanger, the tube expansion system which pushes a tube expansion ball in a pipe | tube, expands a heat exchanger tube from the inside, and adhere | attaches a fin and a heat exchanger tube closely was performed. However, when the pipe is expanded, there is a problem that the peak portion falls down due to the expanded pipe ball, the adhesion between the heat transfer pipe and the fin is lowered, the pressure loss in the pipe is increased, and the heat transfer performance is lowered.

  The present invention has been made in order to solve the above-described problems. For heat exchangers, the adhesion between the heat transfer tubes and the fins is improved, and a predetermined heat transfer performance can be obtained without increasing the pressure loss in the tubes. An object of the present invention is to provide a heat transfer tube, a heat exchanger using the heat transfer tube, a refrigeration cycle apparatus using the heat exchanger, and an air conditioner using the refrigeration cycle apparatus.

  In the heat exchanger tube for a heat exchanger according to the present invention, a high mountain and a lower mountain are spirally formed in the tube axis direction on the inner surface of the tube at a predetermined height, and the high mountain is formed from 11 to 19, The low mountain is formed between 3 and 6 between the high mountains, and the high mountain has a flat cross-sectional trapezoidal shape before the pipe expansion, the tip width of the mountain peak part after the pipe expansion and the outer diameter of the heat transfer tube The ratio is 0.011 to 0.040.

  A heat exchanger according to the present invention includes a plurality of fins for performing heat exchange and the heat transfer tube according to any one of the above that penetrates the fins, and pressurizes and expands the tube from the inner surface side of the heat transfer tube. The fin is joined to the heat transfer tube.

  Further, the refrigeration cycle apparatus according to the present invention includes a compressor that compresses the refrigerant, a condenser that condenses the refrigerant by heat exchange, expansion means for depressurizing the condensed refrigerant, and heat exchange of the reduced refrigerant. A refrigerating cycle device that constitutes a refrigerant circuit that circulates a refrigerant by connecting a pipe to an evaporator that evaporates by using the heat exchanger according to any one of the above, and either or both of the condenser and the evaporator Is provided.

  In addition, an air conditioner according to the present invention is configured to cool and heat a target space using the above-described refrigeration cycle apparatus.

According to the heat transfer tube for a heat exchanger according to the present invention, when the heat transfer tube is expanded by a mechanical tube expansion method, the expanded ball comes into contact with a high mountain and the peak portion is crushed and flattened, but the peak portion falls down. As compared with the conventional heat transfer tube, the heat transfer performance in the tube can be improved without increasing the pressure loss. Further, the outer surface of the heat transfer tube is processed into a polygonal shape, so that the spring back in the heat transfer tube can be suppressed and the adhesion between the heat transfer tube and the fin can be improved.
And using this heat exchanger tube, a highly efficient heat exchanger, a refrigerating cycle device, and an air harmony device can be provided.

It is the perspective view of the heat exchanger which concerns on Embodiment 1 of this invention, and the side surface sectional drawing which cut | disconnected the heat exchanger parallel to the fin surface. It is sectional drawing before the pipe expansion of the heat exchanger tube which expanded the A section of FIG. 1, and after a pipe expansion. It is explanatory drawing which shows the pipe expansion state by the mechanical pipe expansion system of the heat exchanger tube of FIG. It is a diagram which shows the relationship between the streak number of the high mountain of the heat exchanger tube which concerns on Embodiment 1, and a heat exchange rate. It is a diagram which shows the relationship between the ratio of the front-end | tip width | variety of the high peak after expanding the heat exchanger tube which concerns on Embodiment 1, and the outer diameter of a heat exchanger tube, and a heat exchange rate. It is sectional drawing which shows the pipe inner surface shape after expanding the heat exchanger tube which concerns on Embodiment 2 of this invention. It is a diagram which shows the relationship between the difference of the groove part and peak part after expanding the heat exchanger tube which concerns on Embodiment 2, and a heat exchange rate. It is front sectional drawing of the pipe | tube inner surface of the heat exchanger tube which concerns on Embodiment 3 of this invention. It is a diagram which shows the relationship between the lead angle of the spiral groove of the heat exchanger tube which concerns on Embodiment 3, and a heat exchange rate. It is sectional drawing which shows the pipe inner surface shape of the heat exchanger tube which concerns on Embodiment 4 of this invention. It is a diagram which shows the relationship between the top angle | corner of the high peak of the heat exchanger tube which concerns on Embodiment 4, and a heat exchange rate. It is a system circuit diagram of the air conditioning apparatus which concerns on Embodiment 5 of this invention.

Embodiment 1 FIG.
In FIG. 1, a heat exchanger 1 is a fin tube type heat exchanger that is widely used as an evaporator or condenser such as a refrigeration apparatus or an air conditioner.
The heat exchanger 1 includes a plurality of heat exchanger fins 10 and heat transfer tubes 20. A plurality of through holes 11 are provided in each of the fins 10 arranged at a predetermined interval, and the heat transfer tubes 20 pass through the through holes 11. The heat transfer tube 20 becomes a part of the refrigerant circuit in the refrigeration cycle apparatus, and the heat transfer area is expanded by transferring heat of the refrigerant flowing inside the heat transfer tube 20 and the air flowing outside through the fins 10, and the refrigerant and air The heat exchange is efficiently performed.

  As shown in FIG. 2, the inner surface of the heat transfer tube 20 is provided with a groove portion 21 and a ridge portion 22 by groove formation. The ridge portion 22 is further divided into a high mountain 22 a and a low mountain as shown in FIG. 2. It consists of two types of peaks with 22b. A plurality of low peaks 22b are formed between the high peaks 22a, and the high peaks 22a have a trapezoidal cross-sectional shape in which the top of the peak is formed in a planar shape before the pipe expansion (FIG. 2B). The ratio, W1 / D, of the tip width W1 of the summit portion (FIG. 2A) and the outer diameter D of the heat transfer tube 20 is 0.011 to 0.040. Moreover, the height t1 of the low peak 22b before the pipe expansion is lower than the height t2 of the high peak 22a by t3, that is, 0.04 mm or more. However, even if there is too much difference between the high peak 22a and the low peak 22b (even if the low peak 22b is too low), the thermal performance may be reduced due to a decrease in the surface area in the pipe. The difference is close to 0.04 mm.

  In FIG. 3, first, the heat exchanger 1 is bent into a hairpin shape at a predetermined bending pitch at the center in the longitudinal direction, and a plurality of hairpin tubes to be the heat transfer tubes 20 are manufactured. Next, after the hairpin tube is inserted into the through hole 11 of the fin 10, the hairpin tube is expanded by a mechanical tube expansion method to form the heat transfer tube 20, and the heat transfer tube 20 is brought into close contact with the fin 10 and joined. The mechanical tube expansion system is a method in which a rod 31 having a tube ball 30 having a diameter slightly larger than the inner diameter of the heat transfer tube 20 is passed through the tube of the heat transfer tube 20 and the outer diameter of the heat transfer tube 20 is expanded. It is the method of making it adhere.

  When the pipe is expanded by the mechanical pipe expansion system, the expanded ball 30 contacts, so that the peak portion of the high mountain 22a is crushed and becomes flat, and the height of the mountain is lowered. On the other hand, the low mountain 22b is not deformed because the mountain top portion is lower than the collapsed height of 0.04 m (see FIG. 2). And since the pressure of tube expansion ball 30 insertion is not applied to all the crest parts in a pipe like the past, pressure is applied only to the part of high crest 22a, and the outer surface of heat exchanger tube 20 is polygonal. The springback of the heat transfer tube 20 can be suppressed. Thereby, the adhesiveness of the heat exchanger tube 20 and the fin 10 improves, and the efficiency which concerns on heat exchange can be improved.

  FIG. 4 shows the relationship between the number of the high ridges 22a and the heat exchange rate. On the inner surface of the heat transfer tube 20, the high ridges 22a having 11 to 19 ridges are continuously formed spirally in the axial direction. Further, a low mountain 22b of 3 to 6 is formed between the high mountain 22a and the high mountain 22a.

  As described above, in the heat exchanger 1, the high mountain 22a of the heat transfer tube 20 is set in the range of 11 to 19 when the pipe is expanded, the expanded ball 30 comes into contact with the high mountain 22a and the peak portion is 0. .04 mm is crushed and flattened, and the height of the mountain is lowered. However, if the number of the high ridges 22a of the heat transfer tube 20 is less than 11, the summit portion of the low ridge 22b is also crushed and flattened. It is because thermal performance falls. On the other hand, when the number of high ridges is larger than 19, the number of low ridges 22b decreases, and the heat transfer performance in the pipe deteriorates.

  In the heat transfer tube 20 after the expansion, the ratio W1 / D between the tip width W1 of the peak portion of the high peak 22a and the outer diameter D of the heat transfer tube 20 is set to 0.011 to 0.040 ( (See FIG. 2).

  FIG. 5 shows the relationship between the ratio W1 / D of the tip width W1 of the high crest 22a after expansion and the outer diameter D of the heat transfer tube 20 and the heat exchange rate. The tip width W1 after expansion and the heat transfer tube When the ratio W1 / D with the outer diameter D of 20 is 0.011 or less, when expanding the tube using the expanded ball 30, the top of the peak is crushed and the pressure due to insertion is weakened. Therefore, the expansion of the heat transfer tube 20 is insufficient, the adhesion between the heat transfer tube 20 and the fins 10 is deteriorated, and the heat exchange rate is significantly reduced. Further, if the ratio W1 / D between the tip width W1 and the outer diameter D of the heat transfer tube 20 is set to 0.040 or more, the cross-sectional area of the groove portion 21 is reduced, so that the liquid film of the refrigerant becomes thick and heat transfer. The rate drops significantly.

  On the other hand, when the curvature radius R1 of the tip portion (peak portion) of the low mountain 22b is 0.03 mm to 0.035 mm, the skirt width of the mountain is narrowed and formed as a whole, so that the heat transfer area increases. The heat transfer coefficient in the tube is improved (see FIG. 2).

  By forming the high mountain 22a into a trapezoidal cross section in which the peak is formed in a plane before the expansion, the pressure at the peak is reduced and the amount of collapse of the peak is reduced. However, if the curvature radii of the top surface of the mountain peak and both side surfaces are set to 0.01 mm or less, the manufacturing cost of the heat transfer tube 20 may increase. Therefore, it is desirable that the curvature radius between the flat surface of the peak and both side surfaces is 0.01 to 0.03 mm.

  As mentioned above, according to the heat exchanger 1 of Embodiment 1, the peak part 22 which consists of the high peak 22a and the low peak 22b on the pipe inner surface of the heat exchanger tube 20 is formed helically with respect to the pipe axis direction. The ridges 22a having a predetermined height in the range of 11 to 19 are trapezoidal in cross section in which the peak is formed in a plane before the expansion, and the tip width W1 of the peak after expansion and the outside of the heat transfer tube 20 The ratio W1 / D with the diameter D was set to 0.011 to 0.040, the height was lower than the high peak 22a, and it was formed in the range of 3 to 6 between the high peak 22a and the high peak 22a. Since the low peak 22b has a curvature radius R1 of the peak of 0.03 mm to 0.045 mm, the heat transfer performance in the heat transfer tube 20 can be improved. Further, since the expanded ball 30 is in contact with only the high mountain 22a to expand the tube, the outer surface of the heat transfer tube 20 is processed into a polygonal shape, suppressing the spring back of the heat transfer tube 20, and the adhesion between the heat transfer tube 20 and the fin 10 The heat exchange rate (the ratio of the amount of heat before and after passing through the heat transfer tube) can be increased to save energy. Further, it is possible to reduce the size of the refrigerant in the refrigerant circuit while maintaining a reduced amount of the refrigerant and high efficiency.

Embodiment 2. FIG.
FIG. 6 shows the shape of the inner surface of the heat transfer tube 20 according to the second embodiment of the present invention, and the configuration of the heat exchanger 1 is the same as that of the first embodiment. In addition, the same code | symbol is attached | subjected to the part which plays the role which is the same as that of Embodiment 1, or equivalent (same also in the following embodiment). In the present embodiment, a difference H between the groove portion 21 and the peak portion 22 after the pipe expansion will be described.

FIG. 7 shows the relationship between the difference between the groove portion 21 and the ridge portion 22 after expansion (the high ridge 22a after expansion) and the heat exchange rate. In the heat transfer tube 20, the groove portion 21 and the ridge portion 22 after expansion. The greater the difference H, the higher the heat transfer rate, for example, by increasing the surface area in the tube. However, when the difference H between the groove portion 21 and the peak portion 22 is greater than 0.26 mm, the amount of increase in pressure loss is greater than the amount of increase in heat transfer coefficient, and thus the heat exchange rate is reduced. On the other hand, when the difference H between the groove portion 21 and the peak portion 22 is less than 0.1 mm, the heat transfer coefficient is not improved. Therefore, in the heat transfer tube 20, the high peak 22a and the low peak 22b are formed so that the difference H between the groove part 21 and the peak part 22 after the pipe expansion is 0.1 mm to 0.26 mm.
As described above, according to the heat exchanger 1 of the second embodiment, the high peak 22a and the low peak 22b are set so that the difference H between the groove part 21 and the peak part 22 after the pipe expansion is 0.1 mm to 0.26 mm. Since it formed, the heat transfer performance in the heat exchanger tube 20 can be improved.

Embodiment 3 FIG.
FIG. 8 shows the shape of the inner surface of the heat transfer tube 20 according to the third embodiment of the present invention. The straight line and the groove (spiral groove) 21 (mountain 22) parallel to the tube axis direction on the inner surface of the heat transfer tube 20 are shown. The angle (lead angle or torsion angle) γ formed by the direction in which) extends is 10 degrees to 50 degrees.

  FIG. 9 shows the relationship between the lead angle γ of the groove (spiral groove) 21 of the heat transfer tube 20 and the heat exchange rate. Basically, the lead angle γ of the groove (spiral groove) 21 of the heat transfer tube 20 is set to 10. The reason why it is set in the range of 50 degrees to 50 degrees is that when the lower limit of the lead angle γ of the groove portion (spiral groove) 21 is set to 10 degrees or less, the heat exchange rate decreases significantly, and the groove portion (spiral groove). This is because if the upper limit of the lead angle γ of 21 is 50 degrees or more, the pressure loss in the tube increases. As a result, a flow that flows over the groove portion (spiral groove) 21 is less likely to occur, the pressure loss in the pipe does not increase, the heat exchange rate can be improved, and a highly efficient air conditioner is obtained. .

  As described above, according to the heat exchanger 1 of the third embodiment, the mountain is formed so that the lead angle γ of the groove portion (spiral groove) 21 of the heat transfer tube 20 is 10 degrees to 50 degrees. The heat transfer performance at 20 can be improved.

Embodiment 4 FIG.
FIG. 10 shows the shape of the inner surface of the heat transfer tube 20 according to Embodiment 4 of the present invention. In the heat exchanger 1, the apex angle α of the high peak 22a of the heat transfer tube 20 is set to 15 degrees to 30 degrees. The apex angle β of the low peak 22b is 5 degrees to 15 degrees.

  Basically, the smaller the apex angle at the peak, the larger the heat transfer area of the heat transfer tube 20 as a whole, so that the heat transfer coefficient increases. However, as shown in FIG. 11, when the apex angle α of the high ridge 22a is smaller than 15 degrees, the workability in manufacturing the heat exchanger 1 is remarkably deteriorated, so that the heat exchange rate is finally lowered. It will be. On the other hand, when the apex angle α is larger than 30 degrees, the cross-sectional area of the groove portion 21 is reduced, and the liquid film of the refrigerant overflows from the groove portion 21 and is covered with the liquid film up to the summit portion. It will be.

  On the other hand, by setting the apex angle β of the low mountain 22b to 5 to 15 degrees, the skirt width of the mountain is also narrowed, and by forming it thin as a whole, the heat transfer area is increased and the heat transfer in the tube is increased. The rate increases.

  As described above, according to the heat transfer tube 20 of the fourth embodiment, the high peak 22a is set such that the apex angle α of the high peak 22a is 15 degrees to 30 degrees and the apex angle β of the low peak 22b is 5 degrees to 15 degrees. Since the low mountain 22b is formed, the heat transfer performance in the heat transfer tube 20 can be improved.

Embodiment 5 FIG.
FIG. 12 shows an air conditioner that is a refrigeration cycle apparatus according to Embodiment 5 of the present invention, and this air conditioner includes a heat source side unit (outdoor unit) 100 and a load side unit (indoor unit) 200, These are connected by refrigerant piping, constitute a refrigerant circuit, and circulate the refrigerant. Among the refrigerant pipes, a pipe through which a gas refrigerant (gas refrigerant) flows is referred to as a gas pipe 300, and a pipe through which a liquid refrigerant (in some cases, a liquid refrigerant or a gas-liquid two-phase refrigerant) flows is referred to as a liquid pipe 400. Here, as the refrigerant, for example, HC single refrigerant or a mixed refrigerant containing HC refrigerant, R32, R410A, R407C, tetrafluoropropene (for example, 2,3,3,3-tetrafluoropropene), and more than this tetrafluoropropene A non-azeotropic refrigerant mixture composed of an HFC refrigerant having a low boiling point, carbon dioxide, or the like is used.

  In the present embodiment, the heat source side unit 100 includes a compressor 101, an oil separator 102, a four-way valve 103, a heat source side heat exchanger 104, a heat source side fan 105, an accumulator 106, and a heat source side expansion device (expansion valve) 107. The refrigerant heat exchanger 108, the bypass expansion device 109, and the heat source side control device 110 are configured by each device (means).

  The compressor 101 has an electric motor, sucks the refrigerant, compresses the refrigerant, puts the refrigerant into a high-temperature / high-pressure gas state, and flows the refrigerant into the refrigerant pipe. Regarding the operation control of the compressor 101, for example, a master-side inverter circuit, a slave-side inverter circuit, and the like are provided in the compressor 101, and the capacity of the compressor 101 (refrigerant per unit time is sent out by arbitrarily changing the operation frequency. (Amount) can be changed finely.

  The oil separator 102 separates lubricating oil discharged from the compressor 101 mixed with refrigerant. The separated lubricating oil is returned to the compressor 101. The four-way valve 103 switches the refrigerant flow between the cooling operation and the heating operation based on an instruction from the heat source side control device 110. The heat source side heat exchanger 104 is configured using the heat exchanger 1 described in the first to fourth embodiments, and performs heat exchange between the refrigerant and air (outdoor air). For example, during the heating operation, it functions as an evaporator, performs heat exchange between the low-pressure refrigerant that has flowed in through the heat source side expansion device 107 and air, and evaporates and vaporizes the refrigerant. Further, during the cooling operation, it functions as a condenser and performs heat exchange between the refrigerant compressed in the compressor 101 flowing in from the four-way valve 103 side and air, thereby condensing and liquefying the refrigerant. The heat source side heat exchanger 104 is provided with a heat source side fan 105 in order to efficiently exchange heat between the refrigerant and the air. The heat source side fan 105 may also have an inverter circuit (not shown), and the fan motor operating frequency may be arbitrarily changed to finely change the rotation speed of the fan.

  The inter-refrigerant heat exchanger 108 exchanges heat between the refrigerant flowing in the main flow path of the refrigerant circuit and the refrigerant branched from the flow path and adjusted in flow rate by the bypass expansion device 109 (expansion valve). . In particular, when it is necessary to supercool the refrigerant during the cooling operation, the refrigerant is supercooled and supplied to the load side unit 200. The inter-refrigerant heat exchanger 108 is also configured using the heat exchanger 1 described in the first to fourth embodiments.

  The liquid flowing through the bypass throttling device 109 is returned to the accumulator (liquid separator) 106 via the bypass pipe. The accumulator 106 is means for storing, for example, liquid excess refrigerant. The heat source side control device 110 is composed of, for example, a microcomputer and can communicate with the load side control device 204 by wire or wirelessly. For example, based on data relating to detection by various detection means (sensors) in the air conditioner. The operation of the entire air conditioner is controlled by controlling each means related to the air conditioner, such as the operation frequency control of the compressor 101 by inverter circuit control.

  On the other hand, the load side unit 200 includes a load side heat exchanger 201, a load side expansion device (expansion valve) 202, a load side fan 203, and a load side control device 204. The load-side heat exchanger 201 is also configured using the heat exchanger 1 described in the first to fourth embodiments, and performs heat exchange between the refrigerant and the air in the space to be air-conditioned. For example, during heating operation, it functions as a condenser, performs heat exchange between the refrigerant flowing in from the gas pipe 300 and air, condenses and liquefies the refrigerant (or gas-liquid two-phase), and moves to the liquid pipe 400 side. Spill. On the other hand, during the cooling operation, it functions as an evaporator, performs heat exchange between the refrigerant and the air whose pressure is reduced by the load-side throttle device 202, causes the refrigerant to take heat of the air, evaporates it, and vaporizes it. It flows out to the piping 300 side. In addition, the load side unit 200 is provided with a load side fan 203 for adjusting the flow of air for heat exchange. The operating speed of the load-side fan 203 is determined by, for example, user settings. The load side expansion device 202 adjusts the pressure of the refrigerant in the load side heat exchanger 201 by changing the opening degree.

  Further, the load side control device 204 is also composed of a microcomputer or the like, and can communicate with the heat source side control device 110 by wire or wireless, for example. Based on an instruction from the heat source side control device 110 and an instruction from a resident or the like, for example, each device (means) of the load side unit 200 is controlled such that the room has a predetermined temperature. Further, a signal including data related to detection by the detection means provided in the load side unit 200 is transmitted.

  Next, the operation of the air conditioner will be described. First, basic refrigerant circulation in the refrigerant circuit during cooling operation will be described. Due to the driving operation of the compressor 101, the high-temperature, high-pressure gas (gas) refrigerant discharged from the compressor 101 is condensed by passing through the heat source side heat exchanger 104 from the four-way valve 103 and becomes a liquid refrigerant. The side unit 100 flows out. The refrigerant flowing into the load side unit 200 through the liquid pipe 400 evaporates as the low temperature and low pressure liquid refrigerant whose pressure is adjusted by adjusting the opening degree of the load side expansion device 202 passes through the load side heat exchanger 201. leak. Then, it flows into the heat source side unit 100 through the gas pipe 300, is sucked into the compressor 101 through the four-way valve 103 and the accumulator 106, and is circulated by being pressurized and discharged again.

  Further, basic refrigerant circulation in the refrigerant circuit during heating operation will be described. Due to the driving operation of the compressor 101, the high-temperature, high-pressure gas (gas) refrigerant discharged from the compressor 101 flows into the load side unit 200 from the four-way valve 103 through the gas pipe 300. In the load-side unit 200, the pressure is adjusted by adjusting the opening degree of the load-side expansion device 202, and condensed by passing through the load-side heat exchanger 201 to become an intermediate-pressure liquid or a gas-liquid two-phase refrigerant. And flows out of the load side unit 200. The refrigerant flowing into the heat source side unit 100 through the liquid pipe 400 is pressure-adjusted by adjusting the opening degree of the heat source side expansion device 107, evaporates by passing through the heat source side heat exchanger 104, and becomes a gas refrigerant. Then, the refrigerant is sucked into the compressor 101 through the four-way valve 103 and the accumulator 106, and circulated by being pressurized and discharged as described above.

  As described above, according to the air conditioner of Embodiment 5, heat exchange is performed on the heat source side heat exchanger 104 of the heat source side unit 100, the inter-refrigerant heat exchanger 108, and the load side heat exchanger 201 of the load side unit 200. Since the high-efficiency heat exchanger 1 according to the first to fourth embodiments is used as an evaporator and a condenser, COP (Coefficient of Performance) can be improved and energy saving can be achieved. Etc. can be achieved.

  Embodiment 5 mentioned above demonstrated application to an air conditioning apparatus regarding the heat exchanger which concerns on this invention, However, this invention is not limited to these apparatuses, For example, refrigerant | coolants, such as a refrigeration apparatus, a heat pump apparatus, etc. The present invention can also be applied to other refrigeration cycle apparatuses that constitute a circuit and have a heat exchanger that serves as an evaporator and a condenser.

  Examples of the present invention will be described below in comparison with comparative examples that are out of the scope of the present invention. As shown in Table 1, a heat exchanger 1 having an outer diameter of 7 mm, a bottom wall thickness of the groove 21 of 0.25 mm, a lead angle of 30 degrees, and a high crest 22a with 11 and 19 streaks was produced. (Example 1 and Example 2). In addition, as a comparative example, heat exchangers having an outer diameter of 7 mm, a groove bottom thickness of 0.25 mm, and high ridges of 6 and 30 were manufactured (Comparative Example 1 and Comparative Example 2).

  As is clear from Table 1, the heat exchange rates of the heat exchangers 1 of Example 1 and Example 2 are 101.3% and 101%, and the heat exchange rates of the heat exchangers of Comparative Example 1 and Comparative Example 2 99% and 99.5%, and the heat exchangers 1 of Example 1 and Example 2 both have higher heat exchange rates than the heat exchangers of Comparative Example 1 and Comparative Example 2, and the pipe transfer Thermal performance was improved.

  Next, as shown in Table 2, the outer diameter is 7 mm, the bottom thickness of the groove 21 is 0.25 mm, the lead angle is 30 degrees, the tip width W1 of the high peak 22a and the outer diameter D of the heat transfer tube 20 A heat exchanger 1 having a ratio W1 / D of 0.011, 0.020, and 0.040 was produced (Example 3, Example 4, and Example 5). Further, as a comparative example, the outer diameter is 7 mm, the bottom thickness of the groove is 0.25 mm, the lead angle is 30 degrees, and the ratio W1 / D between the high peak width and the outer diameter of the heat transfer tube is 0.005. And the heat exchanger which is 0.050 was produced (Comparative Example 3 and Comparative Example 4).

  As is clear from Table 2, the heat exchange rates of the heat exchangers 1 of Example 3, Example 4 and Example 5 are 101.2%, 101.8% and 101%, and Comparative Example 3 and Comparative Example The heat exchange rates of the heat exchanger No. 4 are 99.2% and 98%, and the heat exchangers 1 of Example 3, Example 4 and Example 5 are all the heat of Comparative Example 3 and Comparative Example 4. Compared to the exchanger, the heat exchange rate was high, and the heat transfer performance in the tube was improved.

  Next, as shown in Table 3, the outer diameter is 7 mm, the bottom thickness of the groove 21 is 0.25 mm, the lead angle is 30 degrees, and the groove depth after tube expansion is 0.1 mm and 0.26 mm. The heat exchanger 1 was produced (Example 6 and Example 7). As a comparative example, the outer diameter is 7 mm, the bottom wall thickness of the groove is 0.25 mm, the lead angle is 30 degrees, the groove depth after tube expansion is 0.05 mm, and the groove depth after tube expansion is 0.00. A heat exchanger of 3 mm was produced (Comparative Example 5 and Comparative Example 6).

  As is apparent from Table 3, the heat exchange rates of the heat exchangers 1 of Example 6 and Example 7 are 101.5% and 101.2%, and the heat exchangers of Comparative Example 5 and Comparative Example 6 The heat exchange rates are 99% and 99.4%, and the heat exchangers 1 of Example 6 and Example 7 both have a heat exchange rate as compared with the heat exchangers of Comparative Example 5 and Comparative Example 6. High heat transfer performance in the pipe.

  Next, as shown in Table 4, the outer diameter is 7 mm, the bottom wall thickness of the groove 21 is 0.25 mm, the apex angle is 30 degrees, and the lead angle γ is 10 degrees, 30 degrees, and 50 degrees. The exchanger 1 was produced (Example 8, Example 9 and Example 10). As a comparative example, a heat exchanger having an outer diameter of 7 mm, a groove bottom thickness of 0.25 mm, an apex angle of 30 degrees, and lead angles of 5 degrees and 60 degrees was manufactured (Comparative Example 7). And Comparative Example 8).

  As is apparent from Table 4, the heat exchangers 1 of Example 8, Example 9 and Example 10 have heat exchange rates of 100.9%, 101.5% and 101.8%, and Comparative Example 7 and The heat exchange rates of the heat exchanger of Comparative Example 8 are 99.2% and 99.5%, and the heat exchangers 1 of Example 8, Example 9 and Example 10 are both Comparative Example 7 and Compared with the heat exchanger of Comparative Example 8, the heat exchange rate was high, and the heat transfer performance in the tube was improved.

  Next, as shown in Table 5, the heat exchanger 1 having an outer diameter of 7 mm, a bottom thickness of the groove 21 of 0.25 mm, a lead angle of 30 degrees, and an apex angle α of 15 degrees and 30 degrees. It produced (Example 11 and Example 12). As a comparative example, a heat exchanger having an outer diameter of 7 mm, a bottom wall thickness of 0.25 mm, a lead angle of 30 degrees, and a vertex angle of 10 degrees and 40 degrees was manufactured (Comparative Example 9 and Comparative Example). 10).

  As is apparent from Table 5, the heat exchangers 1 of Example 11 and Example 12 have heat exchange rates of 101% and 101.3%, and the heat exchange of the heat exchangers of Comparative Example 9 and Comparative Example 10 The rates are 99% and 99.3%, and the heat exchangers 1 of Example 11 and Example 12 both have higher heat exchange rates than the heat exchangers of Comparative Example 9 and Comparative Example 10, The heat transfer performance in the pipe was improved.

  DESCRIPTION OF SYMBOLS 1 Heat exchanger, 10 Fin, 11 Through-hole, 20 Heat exchanger tube, 21 Groove part, 22 Mountain part, 22a High mountain (mountain part), 22b Low mountain (mountain part), 30 Expanded ball, 31 Rod, 100 Heat source side unit , 101 Compressor, 102 Oil separator, 103 Four-way valve, 104 Heat source side heat exchanger, 105 Heat source side fan, 106 Accumulator, 107 Heat source side throttle device, 108 Inter-refrigerant heat exchanger, 109 Bypass throttle device, 110 Heat source side Control device, 200 load side unit, 201 load side heat exchanger, 202 load side throttle device, 203 load side fan, 204 load side control device, 300 gas piping, 400 liquid piping, α high peak angle, β low peak Apex angle, direction in which the ridges extend with respect to the γ tube axis direction (lead angle), D heat transfer tube outer diameter, H high ridge height after tube expansion, R1 The radius of curvature of the top of the mountain, W1 The tip width of the top of the high mountain after pipe expansion.

Claims (11)

A high peak spirally in the direction of the pipe axis on the inner surface of the pipe and a lower peak than this are provided at a predetermined height,
The high mountain is formed from 11 to 19, and the low mountain is formed from 3 to 6 between the high mountain,
The high mountain has a flat cross-sectional trapezoidal shape before pipe expansion, and the ratio between the tip width of the mountain peak part after expansion and the outer diameter of the heat transfer tube is 0.011 to 0.040. Heat transfer tubes for heat exchangers.   The heat exchanger tube for a heat exchanger according to claim 1, wherein the high mountain before the expansion is 0.04 mm or more higher than the low mountain.   The heat transfer tube for a heat exchanger according to claim 1 or 2, wherein each of the high peaks before expansion has a radius of curvature of 0.01 mm to 0.03 mm between the plane of the peak and both side surfaces.   The heat exchange according to any one of claims 1 to 3, wherein an apex angle of the high mountain before expansion is 15 degrees to 30 degrees, and an apex angle of the low mountain is 5 degrees to 15 degrees. Heat transfer tube for equipment.   The heat transfer tube for a heat exchanger according to any one of claims 1 to 4, wherein a radius of curvature of a peak of the low mountain is 0.03 mm to 0.045 mm.   The heat transfer tube for a heat exchanger according to any one of claims 1 to 5, wherein a direction in which the peak portion extends in a tube axis direction is 10 degrees to 50 degrees. A plurality of fins for heat exchange;
The heat transfer tube according to any one of claims 1 to 6, which penetrates the fin,
A heat exchanger, wherein the heat transfer tube is pressurized from the inner surface side and expanded, and the heat transfer tube is joined to the fin.   The heat exchanger according to claim 7, wherein a height of the high mountain after the tube expansion is 0.10 mm to 0.26 mm. A pipe connecting a compressor for compressing the refrigerant, a condenser for condensing the refrigerant by heat exchange, an expansion means for decompressing the condensed refrigerant, and an evaporator for evaporating the decompressed refrigerant by heat exchange A refrigeration cycle apparatus constituting a refrigerant circuit for circulating the refrigerant,
A refrigeration cycle apparatus comprising the heat exchanger according to claim 7 or 8 in both or either of the condenser and the evaporator.   Non-azeotropic refrigerant mixture or carbon dioxide consisting of HC single refrigerant or mixed refrigerant containing HC, R32, R410A, R407C, tetrafluoropropene, and HFC refrigerant having a boiling point lower than that of tetrafluoropropene as the refrigerant Any one of these is used, The refrigeration cycle apparatus of Claim 9 characterized by the above-mentioned.   An air conditioner that cools and heats a target space by the refrigeration cycle apparatus according to claim 9 or 10.

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