JP2009085484A - Outdoor unit for air conditioner - Google Patents

Abstract

Non-stop heating operation can be realized without reversing the refrigeration cycle itself during heating operation of an air conditioner.
For this purpose, the present invention divides an outdoor heat exchanger, which becomes an evaporator during heating, into a plurality of heat exchanger parts based on a refrigerant diversion path, and discharge gas from a compressor corresponding to each of them. By providing a bypass circuit for bypassing and an electromagnetic on-off valve for controlling the bypass state, by performing defrost operation alternately for each heat exchanger section without reversing the refrigeration cycle itself during heating operation of the air conditioner, It was made possible to realize heating operation at the stop.
[Selection] Figure 3

Description

  The present invention relates to a configuration of a heat exchanger part of an outdoor unit for an air conditioner.

  When an evaporator of an outdoor unit for an air conditioner during heating operation has a heat transfer surface of zero degrees or less, moisture in the air condenses and freezes on the heat transfer surface, resulting in frost. Such frost hinders heat transfer from the air to the refrigerant by increasing the thickness. In addition, the air flow path becomes narrower and the air volume is reduced, further promoting the growth of frost. If the frost is left, the amount of heat exchange decreases, the evaporation pressure drops abnormally, and the refrigerant liquid returns to the compressor.

  Therefore, in general, when frost grows to some extent by detecting a decrease in evaporation pressure, a time switch, etc., a defrosting operation is performed, for example, by reversing the refrigerant cycle (for example, a conventional reversible refrigerant cycle configuration). As an example, see Patent Document 1).

  An example of the configuration of the outdoor unit for an air conditioner having such a configuration and the configuration of the refrigeration circuit portion is shown in FIGS.

  7 to 9, reference numeral 1 denotes an outdoor unit. The outdoor unit 1 is divided into two upper and lower positions, which are individually covered by a fan guard having a grill structure. Front side plate 1a having outlets 13a, 13b, rear side plate 1b having an air suction port 3 extending in the vertical direction, right side having a bowl-like cross section covering machine room B in which compressor 8 and the like are provided together with a part of back plate 1b Face plate 1c, left side plate 1d having an air suction port 3 extending in the vertical direction, top plate 1e constituting the top plate, bottom plate 1f constituting the floor, partition for separating the air passage A side and the machine room B side The bell mouth 6a for installing the blower at the position corresponding to the first and second air outlets 13a and 13b while partitioning the plate 1g, the air passage A side and the first and second air outlets 13a and 13b side Main body comprising partition plate 16 and the like forming 6b And it includes a pacing. The main body casing as a whole is configured, for example, in a box shape that is thin in the front-rear direction and longer in the vertical direction than in the left-right direction.

  The back plate 1b and the left side plate 1d are arranged from the upper end side to the lower end side of the panel surface excluding the machine room B portion defined by the partition plate 1e between the left and right side plates 1c and 1d as described above. An air suction port 3 is provided extending in the vertical direction, and an outdoor heat exchange having a bowl shape in plan view that is long in the vertical direction is provided in the uppermost stream portion of the air passage A formed inside the air suction port 3. The container 4 is provided so as to face the opening surface of the air suction port 3.

  A partition plate 16 that partitions the air passage A from the first and second air outlets 13a and 13b is located downstream of the air inlet 3 and the outdoor heat exchanger 4, and the first and first air outlets 13a and 13b. Is provided adjacent to the front plate 1a having two air outlets 13a and 13b, and is located at the upper and lower portions corresponding to the first and second air outlets 13a and 13b. The first and second bell mouths 6a and 6b are provided to provide two blowers (for example, propeller fans) 5a and 5b, and are loosely fitted in the first and second bell mouths 6a and 6b. In this manner, the impellers of the first and second blowers 5a and 5b are provided so as to be rotationally driven by the first and second fan motors 7a and 7b.

  When the first and second blowers 5a and 5b are rotated, the air sucked from the air suction ports 3 and 3 respectively formed in the back plate 1b and the left side plate 1d is passed through the outdoor heat exchanger 4. It blows out from the 1st, 2nd air blower outlets 13a and 13b, and performs heat exchange between the outdoor heat exchanger 4 and air.

  Next, FIG. 10 has shown the structure of the freezing circuit which performs the defrost driving | operation by the reverse cycle of the outdoor unit 1 for the air conditioner.

  That is, the outdoor unit 1 for an air conditioner includes, for example, a compressor 15 whose capacity can be controlled by an inverter control device, an accumulator 16 for gas-liquid separation, an oil separator 17 for oil synthesis separation, and at least two upper and lower refrigerants. The above-described outdoor heat exchanger 4 composed of a cross fin heat exchanger having a diversion path (diversion circuit) is provided, and these are connected to the inside of the refrigerant pipes 11a, 11b, and 11c via the four-way switching valve 18 as shown in FIG. By reversibly connecting to the indoor heat exchanger 14 on the side of the machine 2, a refrigeration circuit (refrigeration cycle) capable of cooling and heating the room by the indoor heat exchanger 14 is configured.

  In the case of this embodiment, the outdoor heat exchanger 4 described above will be described in more detail. For example, as shown in FIG. 11, the outdoor heat exchanger 4 is composed of a cross-fin coil heat exchanger having a two-pass structure that is long in the vertical direction. The compressed refrigerant supplied from the compressor 15 via the refrigerant pipe 11b flows through the first and second upper and lower path portions via the two-pass structure refrigerant distribution header 41 and is provided corresponding to each path portion. After exchanging heat (dissipating heat) with the external air supplied by the above-described first and second blowers 5a and 5b, the refrigerant pipe 11c via the corresponding first and second refrigerant distribution pipes 42a and 42b. And is supplied to the indoor unit 2 side indoor heat exchanger (evaporator) 14 through one electronic expansion valve EV which is a throttle device to be evaporated, and further through the four-way switching valve 18 and the accumulator 16, the compressor. Return to 15 It has become as to be.

In the case of the same configuration, the compressor 15 is configured such that its capacity is inverter-controlled according to the load state at that time, and at the intermediate part of the path and the path outlet side of the outdoor heat exchanger 4 respectively. Temperature sensors T ₄ and T ₅ are provided, so that accurate control can be achieved with respect to fluctuations in the air conditioning load, the refrigerant temperature of each part is detected, and the refrigerant pressure is adjusted to the degree of opening of the electronic expansion valve EV. The refrigerant pressure is appropriately adjusted to be reduced by fine control.

  And now, for example, if the four-way switching valve 18 is in the state of practice shown in the figure and the outdoor heat exchanger 4 is frosted, the four-way switching valve 18 is switched to the state of the broken line in the figure. . Then, the high-temperature discharge gas from the compressor 15 is supplied to the outdoor heat exchanger 4 functioning as an evaporator, and defrosting is thereby performed.

In FIG. 10, reference numeral T ₁ is a sensor for detecting the temperature of the refrigerant sucked by the compressor 15, T ₂ is a sensor for detecting the temperature of the refrigerant discharged from the compressor 15, and T ₃ is an outside air temperature detecting sensor.

Japanese Patent Application Laid-Open No. 6-341741 (Descriptions on pages 3 and 4 and description of FIG. 1)

  However, in the conventional defrost method by changing the cycle direction of the refrigerant circuit with respect to such a single heat exchanger 14, there is a disadvantage that the heating performance and the indoor comfort are lost during the defrosting operation time. When the time elapses, the frost forms again, so that a regular defrosting operation is required, and the heating performance and the indoor comfort are lost each time.

  The present invention has been made to solve such a problem, and an outdoor heat exchanger that becomes an evaporator during heating is divided into a plurality of heat exchanger parts based on a refrigerant diversion path, and each of them corresponds to each of them. By providing a bypass circuit that bypasses the discharge gas from the compressor and an electromagnetic on-off valve that controls the bypass state, the air conditioner is operated alternately for each heat exchanger section without reversing the refrigeration cycle itself during heating operation. An object of the present invention is to provide an air conditioner capable of realizing non-stop heating operation by performing defrost operation.

  In order to achieve the above object, the present invention is configured with the following problem solving means.

(1) The invention of claim 1 The present invention relates to a main body casing, an air suction port provided at one end of the main body casing, an air outlet provided at the other end of the main body casing, An air passage provided between the air inlet and the air outlet; an evaporation heat exchanger provided on the air inlet side of the air passage; and the evaporation heat In the refrigerating apparatus comprising: a blower provided between the exchanger and the air outlet; and a compressor for flowing a refrigerant through the refrigerating circuit including the evaporating heat exchanger, the evaporating heat exchange A bypass circuit that divides the compressor into at least two heat exchanger parts based on the refrigerant distribution path and bypasses the discharge gas from the compressor corresponding to each of them, and an electromagnetic that controls the bypass state of the bypass circuit On-off valve Provided, it is characterized in that to perform the defrosting operation alternately for each heat exchanger section which is the divided without reversing the refrigeration cycle of the refrigeration circuit.

  According to such a configuration, unlike the case of reversing the refrigeration cycle of the entire evaporation heat exchanger, the defrost operation is performed alternately for each divided heat exchanger section, and the blower corresponding to the defrost side heat exchanger By stopping only the one side, even if the one side heat exchanger part is in the defrosted state, the refrigeration function can be maintained in the other side heat exchanger part, so that it is possible to realize non-stop indoor unit heating operation after all it can.

  Therefore, the heating function of the indoor unit of the air conditioner can be maintained even during defrosting.

(2) Invention of Claim 2 This invention is the structure of the invention of said Claim 1, The said ventilation path is mutually partitioned off with the partition plate corresponding to each of each said divided | segmented heat exchanger. It is characterized by that.

  According to such a configuration, it is possible to reliably prevent the air blower on the heat exchanger section side in the other side operation state from sucking the air that has passed through the defrost side heat exchanger at the time of the defrosting. All through the heat exchanger part in the cooling operation state.

  As a result, the evaporation efficiency of the heat exchanger portion is improved and the refrigeration performance is improved.

(3) Invention of Claim 3 This invention is the structure of the invention of the said Claim 1 or 2, The said heat exchanger for evaporation is long formed up and down, The upper side heat exchanger of the said divided | segmented heat exchanger It is characterized in that a drain pan is provided at the lower part of.

  According to such a configuration, the molten water when the upper side heat exchanger part becomes defrosted is recovered by the drain pan, and is prevented from flowing down to the lower side heat exchanger part, and the air in the lower side heat exchanger part is avoided. And good heat exchange performance is maintained.

(4) Invention of Claim 4 This invention is the structure of the invention of Claim 1, 2 or 3, wherein a plurality of the blowers are installed corresponding to each of the divided heat exchangers. Each blower is characterized in that the rotational speed is individually variably controlled.

  According to such a configuration, at the time of defrosting, the heat exchange performance can be individually improved, for example, by increasing the rotation speed of the blower on the side of the heat exchanger that is not in the defrost state to increase the evaporation capacity.

  As a result, according to the present invention, it is possible to efficiently perform the defrost operation without stopping the heating function on the indoor unit side.

(Best Embodiment 1)
1 to 4 show the configuration of an air conditioner outdoor unit according to the first embodiment of the present invention.

  First, in FIG. 1 and FIG. 2, reference numeral 1 denotes an outdoor unit. The outdoor unit 1 is divided into two upper and lower positions, and each is individually covered by a fan guard having a grill structure. A front plate 1a having outlets 13a and 13b, a rear plate 1b having first and second air suction ports 3a and 3b divided into two upper and lower positions, a compressor 8 and the like are provided together with a part of the rear plate 1b. A right side plate 1c having a bowl-shaped cross-section covering the machine room B, a left side plate 1d having first and second air suction ports 3a and 3b divided into two upper and lower positions, an upper surface plate 1e constituting a top plate part, The bottom plate 1f constituting the floor portion, the partition plate 1g that partitions the air passage A side and the machine room B side, the air passage A side and the first and second air outlets 13a, 13b side and the first and A blower is installed at a position corresponding to the second air outlets 13a and 13b. Bell mouth 6a of use, and includes a main body casing formed of the partition plate 16, etc. forming the 6b. The main body casing as a whole is configured, for example, in a box shape that is thin in the front-rear direction and longer in the vertical direction than in the left-right direction.

  The back plate 1b and the left side plate 1d are arranged from the upper end side to the lower end side of the panel surface excluding the machine room B portion defined by the partition plate 1e between the left and right side plates 1c and 1d as described above. The first and second air suction ports a and 3b are provided extending in the vertical direction, and the uppermost stream of the air passage A formed inside the first and second air suction ports 3a and 3b. The section includes an outdoor heat exchanger 4 in a plan view obtained by dividing a heat exchanger that is long in the vertical direction into two upper and lower heat exchanger sections 4a and 4b, and the first and second air suction ports 3a, It is provided so as to face each opening surface of 3b.

  A partition plate 16 that partitions the air passage A from the first and second air outlets 13a and 13b is located downstream of the air inlet 3 and the outdoor heat exchanger 4, and the first and first air outlets 13a and 13b. Is provided adjacent to the front plate 1a having two air outlets 13a and 13b, and is located at the upper and lower portions corresponding to the first and second air outlets 13a and 13b. The first and second bell mouths 6a and 6b for providing two blowers (for example, propeller fans) 5a and 5b are provided, and the first and second bell mouths 6a and 6b are idled. The impellers of the first and second blowers 5a and 5b are provided so as to be rotationally driven by the first and second fan motors 7a and 7b.

  When the first and second blowers 5a and 5b rotate, the air sucked from the first and second air suction ports 3a and 3b respectively formed on the back plate 1b and the left side plate 1d is heated to the outdoor heat. It blows out from the 1st, 2nd air blower outlet 13a, 13b via the exchanger 4, and performs heat exchange between each heat exchanger part 4a, 4b of the outdoor heat exchanger 4 and air.

  Next, FIG. 3 shows the configuration of the refrigeration circuit during the cooling operation of the outdoor unit 1 for the air conditioner.

  That is, as shown in FIG. 3, the outdoor unit 1 for an air conditioner is similar to the conventional example described above, for example, a compressor 15 capable of controlling compression capacity (capacity) by an inverter control device, a gas-liquid separation, and the like. An accumulator 16 for oil separation, an oil separator 17 for oil separation, an outdoor heat exchanger 4 including a cross-fin heat exchanger having at least two refrigerant paths, and the like via a four-way switching valve 18 A refrigerating circuit (refrigeration cycle) capable of cooling and heating the room by the indoor heat exchanger 14 by reversibly connecting to the indoor unit 2 side indoor heat exchanger 14 as illustrated by the refrigerant pipes 11a, 11b, and 11c. Is configured.

In the case of this embodiment, the outdoor heat exchanger 4 is a cross-fin coil type heat exchanger having a two-pass structure that is long in the vertical direction, as shown in FIG. 4, for example, from the compressor 15 to the refrigerant pipe 11b. External air supplied by blowers 5a and 5b provided corresponding to the respective paths by flowing the refrigerant supplied through the upper and lower first and second paths through the distribution header 41 having an upper and lower two-pass structure. After the heat exchange with the refrigerant pipe 11c, the refrigerant pipe 11c is joined via the corresponding first and second branch pipes 42a and 42b having the electronic expansion valves EV ₁ and EV ₂ as the expansion devices, respectively. Yes.

  In the case of such a heat exchanger 4 having a two-stage upper and lower path structure, during operation in the cooling cycle, since the circulation amount of the refrigerant flowing in the rated state with a large load is large, the first and second refrigerant distribution pipes 42a, The pressure loss of the refrigerant flowing through 42b is almost uniform, and the state of the refrigerant at the outlet side of the heat exchanger (supercooling degree) is uniform, but at the medium load (intermediate period) when the load is small, the circulation amount of the refrigerant Therefore, the pressure loss of the refrigerant flowing through the first and second branch pipes 42a and 42b is reduced, and it is easily affected by the head in the height direction of the heat exchanger.

  As a result, the lower side of the heat exchanger is likely to be supercooled, and the refrigerant stagnates on the lower side of the heat exchanger, resulting in a problem that the heat exchange performance is degraded.

Therefore, in this embodiment, as described above, the outdoor heat exchanger 4 is divided into at least the upper heat exchanger portion 4a where the refrigerant does not sleep with reference to the upper and lower two-stage paths, and the lower heat exchanger portion that sleeps. 4b is divided into two heat exchanger sections, and first and second electronic expansion valves EV ₁ and EV ₂ and temperature sensors T ₄ and T are respectively provided in the first and second refrigerant distribution pipes 42a and 42b. ₅ , T ₆ , T ₇ are installed, and the refrigerant pressure is individually adjusted by the control signals C ₁ and C ₂ of the control unit 19 to make the pressure loss and the degree of supercooling uniform, and at the time of intermediate load (intermediate period) While reducing the heat exchange performance, the total input amount including the drive input to the fans 5a and 5b is reduced by changing the rotation speed of the fans 5a and 5b (control signals C ₃ and C ₄ ). Energy saving performance (APF: period consumption) So that to promote the improvement of the rate).

  That is, in the case of the same configuration, the capacity (capacity) of the compressor 15 is controlled by the inverter control device (the rotational speed is controlled by changing the power supply frequency of the compressor drive motor), and the refrigeration load is In the interim period other than summer and winter when the capacity of the compressor decreases and becomes excessive, the capacity of the compressor 5 is reduced to prevent the evaporation pressure from decreasing, and the operation of the apparatus under the desired conditions is economical. It is possible.

  At the same time, the rotational speeds of the upper and lower fans 5a and 5b of the outdoor heat exchanger 4 are also controlled in accordance with the fluctuations in the load so that the drive input of the fan motors 7a and 7b can be as small as possible. The energy consumption efficiency (APF) of electric power throughout the year is increased.

  However, as described above, during the cooling operation, the refrigerant flowing through the path portion of the lower heat exchanger section 4b of the outdoor heat exchanger 4 stagnates, and the refrigerant flowing through the upper heat exchanger section 4a decreases to reduce the degree of supercooling. Decreases and does not contribute to heat exchange, the heat exchange efficiency of the outdoor heat exchanger 4 as a whole is lowered, and the consumption efficiency (APF) of electric power energy throughout the year is also lowered.

However, in this case, refrigerant temperature sensors T ₅ and T _{7 for} monitoring the temperature of the refrigerant in each of the upper and lower heat exchanger units 4a and 4b of the outdoor heat exchanger 4 and a condensation sensor T for detecting the condensation temperature. ₄ and T ₆ are provided to detect the temperature and the condensation start state of the refrigerant in each of the upper and lower passes, and the degree of supercooling in the lower heat exchanger section 4b increases according to the detection result. , while controlling the upper side a first direction of closing the electronic expansion valve EV ₁ of the first refrigerant distribution pipe 42a portion of the first path, the second refrigerant distribution pipe 42b portion of the lower side second pass the If the opening degree of the electronic expansion valve EV ₂ of ₂ is increased to promote the flow of the refrigerant, the pressure loss and the degree of supercooling are made uniform, and the heat exchange efficiency of the lower heat exchanger section 4b is increased. Improved (improved), eventually the heat exchange effect of the outdoor heat exchanger 4 itself There was improvement is also improved consumption efficiency of power energy throughout the year (APF).

  At this time, for example, the rotation speed of the blower 5b corresponding to the lower heat exchanger section 4b is decreased to increase the high pressure, while the rotation speed of the blower 5a corresponding to the upper heat exchanger section 4a is increased to decrease the high pressure. If it becomes, it becomes more effective.

In FIG. 3, reference numeral T ₁ is a sensor for detecting the temperature of refrigerant sucked in the compressor 15, T ₂ is a sensor for detecting the temperature of refrigerant discharged from the compressor 15, and T ₃ is an outside air temperature detecting sensor.

In this way, the outdoor heat exchanger 4 is divided into two parts, that is, an upper side heat exchanger part 4a in which at least the refrigerant does not sleep and a lower side heat exchanger part 4b in which the refrigerant sleeps, based on the path, and each of them is electronically expanded. Valves EV ₁ and EV ₂ and heat exchange sensors T ₄ , T ₅ , T ₆ and T ₇ (heat exchange thermo and intermediate thermo) are installed, and the expansion valves EV ₁ and EV ₂ are individually connected to the heat exchangers 4a and 4b. When the opening degree is controlled to prevent the heat exchange performance from being lowered during the intermediate period (other than winter and summer), the rotational speed of the blowers 5a and 5b is also made variable so that the input of the blowers 5a and 5b is changed. The total amount of input including the power can be reduced to improve the energy saving performance (APF performance improvement) as much as possible.

  On the other hand, in the case of this type of outdoor heat exchanger 4, the outdoor switch is also used in the winter heating operation in which the four-way switching valve 18 is switched from the solid line state to the broken line state in FIG. Contrary to the above, the exchanger 4 becomes a heat exchanger for evaporation, and frost formation occurs. Therefore, if necessary, defrost operation in a reverse cycle as in the prior art is required.

  However, if the defrost operation is simply performed in the reverse cycle, the entire outdoor heat exchanger 4 (4a, 4b) is a condenser (the indoor unit side is the evaporator → the fan is stopped during the defrosting). The heating function on the 2nd side is stopped and the influence in cold regions is great.

Therefore, in this embodiment, as shown in FIG. 3, in addition to the above-described configuration, the compressor discharge gas (hot) is supplied to the first and second heat exchanger sections 4a and 4b divided above and below. By providing bypass circuits (bypass piping) 11d, 11e for bypassing gas) and corresponding electromagnetic on-off valves EV ₃ , EV ₄ and opening the on-off valves EV ₃ , EV ₄ as necessary (control signal C _5, reference C _6), without reversing the refrigeration cycle itself during the heating operation of the apparatus (4-way valve 18 as it) the first, second heat exchanger section 4a, for each 4b (i.e. vertical half Step by step, defrosting operation is performed alternately to realize non-stop heating operation. The control unit 19 also performs opening / closing control of these electromagnetic opening / closing valves EV ₃ , EV ₄ .

  In this case, a twin blower 5a, 5b structure is employed so that the defroster blower can be individually stopped.

(Best Mode 2)
In the configuration of the above-described best embodiment 1, the outlet side first and second refrigerant branch flows of the first and second heat exchanger parts 4a and 4b divided into the upper and lower parts of the outdoor heat exchanger 4 are described. The electronic expansion valves EV ₁ and EV ₂ are disposed in the pipes 42a and 42b, respectively, and the corresponding _first and _second opening degrees of the electronic expansion valves EV ₁ and EV ₂ according to the target degree of supercooling at that time. The rotational speeds of the second blowers 5a and 5b are variably controlled. In the same configuration, for example, as the second preferred embodiment, the first and second electronic expansion valves EV ₁ and EV ₂ are arranged. Without increasing the degree of supercooling, the rotational speed of the blower on the side of the heat exchanger lower than the target supercooling degree is increased according to the target subcooling degree, while the supercooling degree is increased. A structure that only reduces the supercooling degree by lowering the rotational speed of the blower on the heat exchanger side. It can also be a.

  Even with such a simple configuration, appropriate and efficient blower drive control according to the refrigerant flow state of the upper and lower first and second heat exchanger sections 4a and 4b of the outdoor heat exchanger 4 is possible and effective. Energy saving performance can be improved.

(Best Mode 3)
Next, FIG. 5 shows an outdoor unit for an air conditioner according to the third preferred embodiment of the present invention.

  In the case of this embodiment, in the configuration of the outdoor heat exchanger 4 of the best embodiment 1 described above (configuration divided into two upper and lower heat exchanger portions 4a and 4b), the upper and lower heat exchanger portions 4a, 4b is separated into a separate structure, and a dedicated drain pan 9 is provided on the lower portion of the upper first heat exchanger section 4a. This is the same as the configuration of the outdoor unit 1 according to the first embodiment.

As described above, in the outdoor unit 1 of the best embodiment 1, the discharge gas bypass circuit 11d that bypasses the discharge gas from the compressor 15 with respect to the first and second heat exchanger units 4a and 4b. 11e provided solenoid valve EV _3, EV ₄ provided with a, thereby enabling the defrost operation by individually hot gas bypass without reversing the refrigeration cycle.

  In this case, there is no problem when the upper side first heat exchanger part 4a performs normal heating operation and the lower side second heat exchanger part 4b is defrosted, but in the opposite case, That is, when the upper first heat exchanger section 4a is defrosted, the melted water may flow down through the lower second heat exchanger section 4b.

  Therefore, this is received by the drain pan 9 so as not to flow directly downward. As a result, it is not necessary to lower the heat exchange efficiency and heat exchange performance of the lower second heat exchanger section 4b.

(Fourth Embodiment)
Next, FIG. 6 shows a configuration of an outdoor unit for an air conditioner according to the fourth embodiment of the present invention.

In the case of this embodiment, in the configuration of the outdoor heat exchanger 4 of the best embodiment 3 described above, the bottom plate portion of the drain pan 9 provided at the lower portion of the upper first heat exchanger section 4a is used as the front side partition plate. By extending horizontally up to 16 parts, the first and second blower passages A ₁ and A ₂ of the first and second blowers 5a and 5b are defined. .

  As described above, the outdoor heat exchanger 4 is divided into two heat exchanger parts, that is, an upper side first heat exchanger part 4a and a lower side second heat exchanger part 4b, and the defrosting operation is independently performed. In the case where it is possible to do so, the blower on the defrost side is naturally stopped, but it is not necessary that the air passing through the defrost side heat exchanger is blown out by the action of the suction force of the other blower.

Therefore, in this embodiment, by providing the partition plate 20 as described above, the upper and lower first and second heat exchanger sections 4a and 4b, the upper and lower first and second blowers 5a and 5b, The air passages A ₁ and A _{2 of the} first and second air outlets 13a and 13b are completely partitioned so that such a problem does not occur.

  In this case, it goes without saying that the partition plate 20 may be formed completely separately from the drain pan 9.

  The other configurations are all the same as those in the best embodiment 3, and operate in the same manner.

It is a front view which shows the structure of the outdoor unit for air conditioners which concerns on the best Embodiment 1 of this invention. It is sectional drawing which cut | disconnected the center part of the outdoor unit up and down and the front-back direction, and was seen from the left side. It is a figure which shows the structure of the freezing circuit of the outdoor unit. It is a side view which shows the structure of the heat exchanger shunt circuit part which is the principal part of the outdoor unit. It is sectional drawing similar to FIG. 2 which shows the structure of the outdoor unit for air conditioners which concerns on best Embodiment 2 of this invention. It is sectional drawing similar to FIG. 2 which shows the structure of the outdoor unit for air conditioners which concerns on best Embodiment 3 of this invention. It is a front view which shows the structure of the outdoor unit for air conditioners which concerns on a prior art example. It is a top view which shows the structure of the outdoor unit. It is sectional drawing which cut | disconnected the center part of the outdoor unit up and down and the front-back direction, and was seen from the left side. It is a figure which shows the structure of the freezing circuit of the outdoor unit. It is a side view which shows the structure of the heat exchanger shunt circuit part which is the principal part of the outdoor unit.

Explanation of symbols

1 is an outdoor unit, 2 is an indoor unit, 3a and 3b are first and second air inlets, 4 is an outdoor heat exchanger, 4a and 4b are first and second heat exchanger units, and 5a and 5b are First and second blowers, 6a and 6b are first and second bell mouths, 7a and 7b are first and second fan motors, 11a, 11b and 11c are refrigerant pipes, and 11d and 11e are hot gas bypasses. piping, the control unit 19, 42a, 42b are first, second refrigerant distribution pipe, the EV _1, EV ₂ first, second electronic expansion valve, EV _3, EV ₄ is a solenoid valve.

Claims (4)

  A main casing, an air inlet provided at one end of the main casing, an air outlet provided at the other end of the main casing, and between the air inlet and the air outlet in the main casing. A ventilation passage located in the air passage, an evaporation heat exchanger located on the air inlet side of the ventilation passage, and between the evaporation heat exchanger and the air outlet. A refrigeration apparatus comprising: a blower provided as a compressor; and a compressor for flowing a refrigerant through a refrigeration circuit including the evaporating heat exchanger, wherein the evaporating heat exchanger is at least 2 with respect to a refrigerant diversion path. A refrigeration cycle of the above refrigeration circuit is provided with a bypass circuit that divides the heat exchanger into two heat exchanger parts and bypasses the discharge gas from the compressor corresponding to each of them, and an electromagnetic on-off valve that controls the bypass state of the bypass circuit. Air conditioning apparatus outdoor unit, characterized in that to perform the defrosting operation alternately for each of the divided each heat exchanger section was without reversing.   The air conditioner outdoor unit according to claim 1, wherein the air passage is partitioned by a partition plate corresponding to each of the divided heat exchangers.   The air conditioner according to claim 1 or 2, wherein an evaporating heat exchanger is formed long vertically, and a drain pan is provided at a lower portion of the upper heat exchanger of the divided heat exchanger. Outdoor unit.   2. A plurality of blowers are installed corresponding to each of the divided heat exchangers, and the rotation speed of each of the plurality of blowers is individually variably controlled. , 2 or 3 outdoor unit for air conditioner.

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