WO2007148645A1 - Outdoor unit for air conditioner - Google Patents
Outdoor unit for air conditioner Download PDFInfo
- Publication number
- WO2007148645A1 WO2007148645A1 PCT/JP2007/062211 JP2007062211W WO2007148645A1 WO 2007148645 A1 WO2007148645 A1 WO 2007148645A1 JP 2007062211 W JP2007062211 W JP 2007062211W WO 2007148645 A1 WO2007148645 A1 WO 2007148645A1
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- WO
- WIPO (PCT)
- Prior art keywords
- fan
- propeller
- outdoor unit
- air conditioner
- fans
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/38—Fan details of outdoor units, e.g. bell-mouth shaped inlets or fan mountings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/007—Axial-flow pumps multistage fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/024—Multi-stage pumps with contrarotating parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/40—Vibration or noise prevention at outdoor units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/46—Component arrangements in separate outdoor units
- F24F1/48—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow
- F24F1/54—Inlet and outlet arranged on opposite sides
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/46—Improving electric energy efficiency or saving
Definitions
- the present invention relates to a heat exchange accelerating blower used for an outdoor unit of an air conditioner, and more particularly to a technique for improving fan efficiency (static pressure efficiency) of the blower.
- This type of air conditioner forms a refrigeration cycle by connecting an indoor unit having a heat exchanger and a blower and an outdoor unit having a compressor, a heat exchanger, and a blower by piping. Air conditioning is performed indoors by cooling operation or heating operation by heat transfer of the refrigerant filled inside.
- the blower is configured to include a fan and a fan motor to promote heat exchange of the heat exchanger.
- the air volume of this blower greatly affects the performance of the air conditioner and includes noise. The performance is greatly affected.
- a blower for promoting heat exchange used for an outdoor unit of an air conditioner, and a technology related to a rear stationary blade for the purpose of reducing noise by increasing the efficiency of recovering its dynamic pressure are disclosed (for example, see JP2002-81695A).
- FIG. 19 is a cross-sectional view of an outdoor unit of a conventional air conditioner.
- the outdoor unit 80 includes a compressor space 83, a heat exchanger 81, a fan motor 82 and a blower 85 for heat exchange promotion, a rear stationary blade 86 for recovering dynamic pressure, and an orifice 87 in a main body outer box 84.
- 85 and a rear stationary vane 86 that recovers the dynamic pressure are arranged on the same axis of the fan motor 82 as windward force.
- the unit is kg 'sec 2 ' m 4 and the unit of C and V is m / sec).
- the present invention solves the above-described conventional problems, and improves the fan efficiency (static pressure efficiency) of the blower to increase the static pressure and the air volume.
- the purpose is to provide an outdoor unit for an air conditioner that can suppress noise and reduce noise.
- an outdoor unit of an air conditioner includes a compressor, a heat exchanger, and two propeller fans as fans for promoting heat exchange of the heat exchanger.
- the two propeller fans are provided close to each other on the same axis, and are configured such that the airflow directions are the same while rotating in the opposite directions (reverse rotation).
- the rotational energy of the wake behind the propeller fan that is on the windward side of the two propeller fans (the energy that is wasted due to the rotational flow) is closely counter-rotated (rotated in the opposite direction to each other).
- the propeller fan on the leeward side can be recovered, and the rotational flow after the leeward propeller fan can be made almost zero. That is, the operating point static pressure efficiency is improved as compared with the case of using only one propeller fan (the depth is equivalent to two propeller fans of the present invention) for the outdoor unit of the air conditioner. It is possible to increase the static pressure and air flow, or to suppress the decrease of air flow against the air blowing resistance and reduce the noise. As a result, the fan motor input can be reduced, and the COP (Coefficient of performance), period power consumption, and noise of the air conditioner can be reduced.
- the outdoor unit of the air conditioner of the present invention collects the rotational energy (waste energy associated with the rotational flow) downstream of the windward propeller fan with a counter-rotating leeward propeller fan, and further leeward propeller fan. Since the rotational flow of the wake can be reduced to almost zero, the size of the outdoor unit of the air conditioner is larger than when only one propeller fan is used. The pressure and air volume can be increased, and the operating point static pressure efficiency can be improved. As a result, the fan motor input can be reduced and the COP and period power consumption of the air conditioner can be reduced, or the reduction of the air volume can be suppressed and the noise can be reduced.
- FIG. 1 is a cross-sectional view of an outdoor unit of an air conditioner according to Embodiment 1 of the present invention.
- FIG. 2 is a plan view in the A direction of the windward propeller fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
- FIG. 3 is a plan view in the A direction of the leeward propeller fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
- Fig. 4 is a characteristic flow rate characteristic airflow ratio of a propeller fan of an outdoor unit of an air conditioner according to Embodiment 1 of the present invention.
- FIG. 5 is a performance diagram showing a developed blade row and a speed triangle of a cylindrical cut surface at a mean square radius position of the wind upper and lower propeller fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
- Fig. 6 is a static pressure / air flow characteristic diagram of a wind upper / lower propeller fan (double reversing fan) of an outdoor unit of an air conditioner according to Embodiment 1 of the present invention.
- FIG. 7 is a cross-sectional view of an outdoor unit of an air conditioner according to Embodiment 2 of the present invention.
- FIG. 8 is a meridional view of a wind up / down propeller fan of an outdoor unit of an air conditioner according to Embodiment 4 of the present invention.
- FIG. 9 is a radial cross-sectional view of a wind up / down propeller fan of an outdoor unit of an air conditioner according to Embodiment 4 of the present invention.
- FIG. 10 Wind up and down side propeller fan of the outdoor unit of the air conditioner according to Embodiment 5 of the present invention.
- FIG. 11 is a radial cross-sectional view of a wind up / down propeller fan of an outdoor unit of an air conditioner according to Embodiment 5 of the present invention.
- FIG. 12 is a plan view in the A direction of an upwind mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 6 of the present invention.
- FIG. 13 is a plan view in the A direction of the leeward mixed flow fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
- FIG. 14 is a meridional view of an up-down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 6 of the present invention.
- FIG. 15 is a meridional view of an up-down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 7 of the present invention.
- FIG. 16 is a radial cross-sectional view of a wind up / down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 7 of the present invention.
- FIG. 17 is a meridional view of an up-down mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 8 of the present invention.
- FIG. 18 is a radial cross-sectional view of a wind up / down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 8 of the present invention.
- FIG. 19 is a cross-sectional view of an outdoor unit of an air conditioner according to a conventional example.
- a first invention includes a compressor, a heat exchanger, and two propeller fans as fans for promoting heat exchange of the heat exchanger, and the two propeller fans are coaxial. They are provided close to each other and are configured so that the airflow directions are the same while rotating (reversely rotating) in opposite directions.
- the rotational energy behind the propeller fan on the windward side of the two propeller fans (waste energy associated with the rotational flow) is closely counter-rotated (rotated in the opposite direction to each other).
- the propeller fan on the leeward side can be recovered, and the rotational flow after the leeward propeller fan can be made almost zero.
- the size of the outdoor unit of the air conditioner is large, and the depth of one propeller fan (the depth is the same as the two propeller fans of the present invention)
- the static pressure efficiency at the operating point can be improved, and the static pressure and the air volume are increased, or the decrease in the air volume due to the blowing resistance such as dew and frost attached to the heat exchanger is suppressed.
- noise can be reduced.
- the fan motor input can be reduced and the COP, period power consumption, and noise of the air conditioner can be reduced.
- the second aspect of the invention is the outdoor unit of the air conditioner of the first aspect of the invention, in particular, the two propellers are each of which the wing shape is a chord shape and the bending direction is opposite, In other words, the plane shape of one propeller fan is the same or similar when reversed. As a result, only the hub is changed as the shape, and the design for demonstrating the performance as a double reversing fan becomes easy.
- the third invention is a propeller fan, particularly in the outdoor unit of the air conditioner of the first or second invention, wherein one fan motor and a reversing mechanism for reversing the rotation direction of the fan motor are transmitted.
- one propeller fan is driven by the fan motor, and the other propeller fan is driven by the reversing mechanism.
- the fourth aspect of the invention is, in particular, in the outdoor unit of the air conditioner of the third aspect of the invention, in order of the windward force, the heat exchanger, the fan motor, the windward propeller fan, the reversing mechanism, and the leeward propeller fan.
- the leeward propeller fan is driven by the fan motor, and the leeward propeller fan is driven by the reversing mechanism.
- the reversing mechanism of the third or fourth aspect is provided in the hub of the windward propeller fan. Or in the hub of the leeward propeller fan, or in the hubs of both the leeward and leeward propeller fans, the two propeller fans can be configured closer together.
- the sixth invention is such that, in the first or second invention, two fan motors are provided in each of the two propeller fans, and the two propeller fans are driven by the fan motors provided respectively.
- the rotation speed of the two propeller fans can be adjusted individually, and any setting can be made according to the operating conditions.
- the fan motor is an outer rotor type
- the fan motor is configured inside the hub of the propeller fan, so that the fan motor is provided. Since no space is required, it is possible to more effectively use the space that becomes the air path of the outdoor unit, and it is possible to make the air velocity distribution of the heat exchanger ⁇ uniform and improve noise reduction.
- the outdoor unit can be downsized.
- the rotational speed of each of the two counter-rotating propeller fans (co-rotating fan) on the same axis is changed.
- the rotation speed of the two propeller fans that rotate the speed triangles of the individual propeller fans differ, and the timing of the work time of the individual propeller fan blades shifts. Even if the time axis of work is taken, the peak of discrete noise due to harmonics that do not interfere with each other can be generated, and low noise can be achieved.
- the ninth invention is the ratio of the chord length L at the mean square radial position of the blade of the propeller fan to the representative actual length b in the radial direction of the blade in the first to eighth inventions.
- the aspect ratio bZL is bZ L ⁇ l. 1, and the outer peripheral chord length of the propeller fan is greater than or equal to the hub chord length.
- each propeller fan Since the outer chord length of each propeller fan is configured to be longer than the hub chord length, securing a large blade area at the blade tip sufficiently absorbs the aerodynamic load and performs work. Therefore, the fan efficiency of each propeller fan itself is improved and the noise is reduced. Furthermore, if the aspect ratio is set to bZL ⁇ l. 1, the air volume per noise can be increased.
- the two counter-rotating propellers (double reversing fans) that are coaxially rotated counterclockwise are the leading edges on the meridional plane (meridional plane).
- meridional plane meridional plane
- the rotational energy of the wake of the windward propeller fan (waste energy associated with the rotational flow) is recovered by the counter-rotating leeward propeller fan, and further the rotational flow of the wake of the leeward propeller fan.
- the static pressure and air volume can be increased compared to the case of using only a large size propeller fan and an air conditioner outdoor unit. Efficiency can be improved.
- the suction surface force of the two counter-rotating propeller fans on the same axis causes the tip vortex generated near the tip side of the suction surface of the propeller fan to be
- the concave part on the windward side of the blade cross-section of the directional cross section promotes the generation of the tip vortex and optimizes the flow state of the blades of each propeller fan. Can be improved.
- the blade tip vortex can be strengthened to generate a blade tip vortex quickly and strongly, and it can be quickly broken down. The fan noise and fan efficiency can be improved without interference.
- the two counter-rotating propellers (double reversing fans) that are coaxially rotated counterclockwise have a leading edge on the meridian plane (rotary projection).
- the tip side is concave from the midpoint of the wing
- the hub side is convex
- the cross-sectional shape of the wing in the radial cross section is concave to the windward side
- the hub side is convex.
- Each propeller fan The fan's outer chord length is longer than the hub chord length.
- the rotational energy of the wake of the windward propeller fan (waste energy associated with the rotational flow) is recovered by the counter-rotating leeward propeller fan, and further the rotational flow of the wake of the leeward propeller fan.
- the static pressure and air volume can be increased compared to the case of using only a large size propeller fan and an air conditioner outdoor unit. Efficiency can be improved.
- the suction surface force of the two counter-rotating propeller fans on the same axis causes the tip vortex generated near the tip side of the suction surface of the propeller fan to be
- the tip side of the blade cross-sectional shape of the directional cross section is concave with respect to the windward side, promoting the generation of this tip vortex
- the hub-side convex part of the blade cross-sectional shape of the above-mentioned radial cross-section attracts the flow that flows in the radial direction of the outer periphery of the blade of the propeller fan, so by promoting the generation of blade vortex and the radial flow, Since the flow state of each propeller fan blade can be optimized most, the operating point static pressure efficiency can be further improved.
- each propeller fan fan since the outer chord length of each propeller fan fan is larger than the hub chord length, the wing tip load can be strengthened to generate wing tip vortices quickly and strongly, and it can be quickly broken down. The fan noise and fan efficiency can be improved without interfering with the wings.
- a counter flow fan is used instead of a propeller fan instead of two counter-rotating fan (double reversing fan) forces that rotate on the same axis
- This mixed-flow fan is a mixed-flow fan in which each blade shape is designed to be approximately line-symmetric with respect to the same axial force, and the number of blades is one or more. It is formed in a frustum shape.
- the rotational energy of the wakeward-side mixed fan wake (useless energy associated with the rotational flow) is recovered by the counter-rotating leeward mixed-flow fan, and further after the leeward mixed-flow fan. Since the rotational flow of the air flow can be made almost zero, the static pressure and air volume can be increased compared to the case where only a large-size diagonal flow fan is used in the outdoor unit of the air conditioner. It is possible to improve the operating point static pressure efficiency. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan.
- FIG. 1 is a cross-sectional view of an outdoor unit of an air conditioner according to the first embodiment of the present invention.
- Fig. 2 is a plan view of the windward propeller fan in which the outdoor unit is also viewed in the direction A of Fig. 1.
- Fig. 3 is a plan view of the leeward propeller fan when the outdoor unit is viewed from the A direction.
- Figure 4 is an aspect ratio characteristic airflow characteristic chart of each propeller fan, showing the airflow per 41dB noise.
- an outdoor unit 1 includes a heat exchanger 2, a vertical compressor 3, a soundproof plate 4 that partitions the compressor room and the air passage, an upwind propeller fan 5, a downwind propeller fan 6, and a fan Motor 7 and fan
- the motor 7 includes a reversing mechanism 8 that houses a gear having a mechanism for reversing the rotation direction of the motor 7, an orifice 9, a front grill 10, and a fan motor base 11.
- the windward propeller fan 5 and the leeward propeller fan 6 generate a blowing action in the heat exchange 2 and act as a double reversing fan in a fan for promoting heat exchange.
- the blade 20 of the windward propeller fan 5 has a force of two blades, and is composed of a tip 21, a leading edge 22, a trailing edge 23, and a hub 24 that constitute the outer peripheral edge.
- An alternate long and short dash line B is a cylindrical cutting line of the blade 20 at the root mean square radius position of the windward propeller fan 5. Then, the chord length L at the mean square radial position of the blade of the prober fan and the representative actual length b in the radial direction of the blade.
- the wing 25 of the leeward propeller fan 6 has two blades and is composed of the tip 26, the leading edge 27, the trailing edge 28, and the hub 29 like the leeward propeller fan 5.
- the alternate long and short dash line B indicates the cylindrical cutting of the blade 20 at the mean square radius position of the leeward propeller fan 6.
- the flow of air is based on the fact that it flows in from the leading edges 22 and 27 and flows out from the trailing edges 23 and 28, respectively.
- the leading edges 22, 27 are moving forward (tilting forward) in the direction of rotation.
- each of the blades 20 and 25 is reverse to the chordal shape, and in the three-dimensional coordinate system, each is viewed from the same axial direction. It is designed and formed symmetrically.
- the shape of each of the two propeller fans 5 and 6 is the same or similar when the plane shape is reversed, and the blades have the same airflow direction when rotated in opposite directions. It is.
- the pub is changed as the shape, and the design for exhibiting the performance as the double reversing fan becomes easy.
- the leeward propeller fan 6 when changing the rotation speed of the two propeller fans, the leeward propeller fan 6 is often set to a lower rotation speed than the upwind propeller fan 5.
- the number of blades is two in Embodiment 1, but is not particularly limited.
- the leading edges 22 and 27 are formed by a spiral curve, and the leeward propeller fan 6 has a smaller diameter than the leeward propeller fan 5.
- the front edges 22 and 27 may be straight, and a triangular wing (triangular wing) may be attached in close contact with the straight front edge so as to have the same radius on the outer periphery.
- each propeller fan by configuring the outer chord length of each propeller fan to be longer than the hub chord length, it is possible to sufficiently absorb the aerodynamic load by performing a work by ensuring a large blade area at the blade tip, The fan efficiency of each propeller fan itself will be improved and the noise will be reduced. Furthermore, if the aspect ratio is set to bZL ⁇ l. 1, it is possible to increase the air volume per the same noise, as shown in Fig. 4.
- the configuration of the outdoor unit 1 includes a compressor 3, a heat exchanger 2, and two windward propeller fans 5 and a leeward propeller fan 6 that counter-rotate as fans for promoting heat exchange.
- a reversing mechanism 8 that counter-rotates the rotation direction is provided on the upper side, and a leeward propeller fan 6 that rotates counterclockwise on the same axis as the fan motor 7 is provided on the downstream side of the reversing mechanism 8.
- the reversing mechanism 8 is installed inside the hub 24 of the leeward propeller fan 5, or inside the hub 29 of the leeward propeller fan 6, or inside the hub 24 of the leeward propeller fan 5, and the leeward propeller fan 6
- the hub 29 may be housed in both the hubs 24 and 29, so that the outdoor unit 1 can be further saved in space.
- the fan motor 7 is an outer rotor type fan motor, and the outdoor unit 1 that can be housed in the hub 24 of the leeward propeller fan 5 or in the hub 29 of the leeward propeller fan 6 is further added. Space can be saved.
- the reversing mechanism 8 and the fan motor 7 can be used in a variety of combinations within the hub of the fan, and space can be saved by making effective use of them.
- the rotational energy of the leeward propeller fan 5 is recovered by the counter-rotating leeward propeller fan 6 and further rotated by the leeward propeller fan 6 Since the flow can be made almost zero, the static pressure and air volume can be increased compared to the case where the outdoor unit 1 is larger in size and only one propeller fan is used. It is possible to improve the static pressure efficiency. As a result, the input to the fan motor 7 can be reduced, and the COP and period power consumption of the air conditioner can be reduced.
- Fan motor 7 has a single force Windward propeller fan 5 Backward reversing mechanism 8 Combined with the gear shape and other features, the rotation direction of the shaft of fan motor 7 is set to be the counter-rotating direction to leeward propeller fan 6 Since there are only seven fan motors that can be transmitted and that are heavy, the number of components of the outdoor unit of the air conditioner can be reduced and the weight can be reduced. Since the leading edges 22 and 27 are moving forward, the tip load can be increased, the tip vortex can be generated quickly and strongly, and it can break down quickly without interfering with the rear wing. It becomes possible to improve the performance of fan noise and fan efficiency.
- FIG. Fig. 5 is a performance diagram showing the developed blade row and velocity triangle of the cylindrical cut surface at the mean square radius position of each propeller fan.
- Deployment of blade 20 Airflow flows at an absolute velocity into the blade row (the blade row that was cut and deployed with the B cylinder in Fig. 2).
- U the rotation speed and W is the relative speed.
- Absolute speed C Melide
- the circumferential component V is completely recovered in the open blade row 25, and the dynamic pressure Pd is converted to static pressure.
- fan motor 7 has m2 2
- the static pressure-air flow characteristics of two counter-rotating propeller fans are increased compared to the case of using only one single-stage propeller fan. Will do.
- the rotational speed of the windward and leeward propeller fans is set to 550 rpm, and the fan diameter is ⁇ 415 mm. This means that the fan static pressure efficiency of two counter-rotating propeller fans (double reversing fans) is improved. This makes it possible to reduce the COP and period power consumption of the air conditioner.
- Fig. 6 is a characteristic diagram of the static pressure and air flow rate of the double reversing fan of the outdoor unit of the present invention.
- the characteristic curve of the double reversing fan consisting of two counter-rotating propeller fans and the The characteristic curve of one (single stage) propeller fan is compared.
- the windward and leeward propellers are used.
- Experimental data showed that when using fans 5 and 6 (double reversing fan, fan diameter ⁇ 415 ⁇ ), the operating point static pressure efficiency was improved by 18%.
- the diameter of the leeward propeller fan 6 may be smaller than the diameter of the leeward propeller fan 5. In this way, the energy of the rotational flow behind the windward propeller fan 5 can be recovered without waste. Also, the diameter of the leeward propeller fan 6 is equal to the diameter of the leeward propeller fan 5. If the operating speed of the leeward propeller fan 6 is set to be even smaller, the energy of the rotatory flow of the leeward propeller fan 5 can be recovered without waste, and the meridian flow rate can be increased to> C. The air volume increases.
- chord lengths of the tips 21 and 26 on the outer periphery of the windward and leeward propeller fans 5 and 6 are larger than the chord lengths of the hubs 24 and 29 (however, at least the chord lengths of the tips 21 and 26 are Hub 24, 29 up to the same length as the side chord length), the wing tip load is increased, the wing tip vortex is generated quickly and strongly, and it can break down quickly without interfering with the rear wing. As a result, fan noise and fan efficiency can be improved.
- the leading edges 22, 27 are the force moving forward in the rotational direction.
- the up-and-down propeller fans 5, 6 are axisymmetric, and the leading edges 22, 27
- the effect of the double reversing fan can be exerted even when is moving backward in the rotation direction.
- the wind-up / down-side propeller fans 5 and 6 are at least line-symmetric and the directional relationship of the rotating blade row as shown in Fig. 5 (the bending direction of the blades 20 and 25 is reversed)
- the leading edge Even if either 22 or 27 can be a combination of forward and reverse in the rotational direction, the effect of the double reversing fan can be exhibited.
- the cross-sectional shape of the blade may be either a thin blade or a thick blade having an airfoil shape. However, if the blade is thick, separation can be reduced by controlling the boundary layer of the flow, and lower noise can be realized.
- FIG. 7 is a cross-sectional view of an outdoor unit of an air conditioner according to the second embodiment of the present invention.
- the outdoor unit 1 includes a heat exchanger 2, a vertical compressor 3, a soundproof plate 4 that cuts the compressor room and the air passage, an upwind propeller fan 5, a downwind propeller fan 6, and an upwind propeller fan.
- the fan motor 7a that drives the fan 5, the fan motor 7b that drives the leeward propeller fan 6, the orifice 9, the front grill 10, and the fan motor bases 11a and l ib.
- the windward propeller fan 5 and the leeward propeller fan 6 rotate on the same axis half of each other to produce a blowing action in the heat exchanger 2 and act as a heat exchange promoting blower (double reversing fan).
- the two fan motors 7a and 7b are outer rotor type fan motors, which are embedded in the respective hubs of the windward propeller fan 5 and the leeward propeller fan 6 and are configured integrally with the fan. [0052] These are, in order from the windward side ⁇ 2, the windward propeller fan 5 with the outer rotor fan motor 7a built in, and the leeward propeller fan with the other outer rotor fan motor 7b built-in. 6.
- the front grille 10 and the leeward propeller fan 5 and the leeward propeller fan 6 have a chord-shaped curved direction opposite to each other. As seen from the figure, it is almost line-symmetric and consists of two blades.
- the rotational energy of the leeward propeller fan 5 wake (wasteful energy associated with the rotational flow) is recovered by the counter-rotating leeward propeller fan 6 and further rotated by the leeward propeller fan 6 wake. Since the flow can be reduced to almost zero, the static pressure and airflow can be increased compared to the case of using only one propeller fan and the size of the outdoor unit 1 of the air conditioner. It is possible to improve the static pressure efficiency. As a result, the input to the fan motors 7a and 7b can be reduced, and the COP and period power consumption of the air conditioner can be reduced.
- the required air volume and static pressure are the same design as when only one large propeller fan is used in the outdoor unit 1 of the air conditioner.
- the blade load on two individual propeller fans 5 and 6 also called double reversing fans
- the input can be made lower than when only one fan motor is used.
- the two fan motors 7a and 7b are outer rotor types and are counter-rotating to each other, and are embedded in the hub portion of the two propeller fans 5 and 6, so that the propeller fans 5 and 6 and the outer rotor Since the fan motors 7a and 7b are combined, it is possible to save space for the outdoor unit of the air conditioner.
- the fan motors 7a and 7b are not limited to the outer rotor type fan motor, and a fan motor that rotates the fan motor shaft can be installed on the same axis outside the up / down propeller fan. As long as there is no problem, it does not matter.
- the heat exchanger 2 has a configuration in which the windward propeller fan 5 incorporating the outer rotor fan motor 7a from the windward side and the leeward propeller fan 6 incorporating the other outer rotor fan motor 7b are arranged in this order.
- the wind speed distribution of the heat exchanger 2 can be made uniform, and heat exchange can be further promoted. Further, wind noise caused by interference between the heat exchanger 2 and the windward propeller fan 5 can be prevented.
- a third embodiment of the present invention will be described with reference to FIGS.
- the reference numerals and configuration are omitted because they are described in the first and second embodiments.
- Two propeller fans 5 and 6 (2 counter rotating fans) on the same axis are set by changing the rotation speed of the two propeller fans 5 and 6 (double reversing fans).
- the present invention provides an outdoor unit for an air conditioner equipped with a double reversing fan.
- the ratio of the rotational speed of the windward propeller fan 5 and the rotational speed of the leeward propeller fan 6 can be set by the gear ratio of the reversing mechanism 8 that is a reversing mechanism.
- the propeller fans 5 and 6 are provided with the fan motors 7a and 7b, the respective rotational speeds can be freely set.
- the rotation speeds of the two propeller fans 5 and 6 that are counter-rotating can be changed, so that the speed triangles of the individual propeller fans 5 and 6 are different, and the individual propeller fans 5 and 6 have different speed triangles. Since the timing of the blades 20 and 25 is shifted, the peak of discrete noise is generated due to harmonics that do not interfere with each other even if the blades 20 and 25 work along the time axis. It can also be done with low noise.
- FIG. 8 shows the propeller of the counter rotating fan of the outdoor unit according to the fourth embodiment of the present invention. It is Ann's meridian view.
- FIG. 9 is a radial cross-sectional view of the propeller fan shown in FIG. 8, showing the upper side. Individual up-and-down propeller fans are standardized as 30.
- the propeller fan 30 includes two blades 31 and includes a leading edge 32, a trailing edge 33, a hub 34, and a tip 35.
- Two propeller fans 30 (co-rotating fan) that rotate counterclockwise on the same axis have a leading edge 32 on the meridian plane (rotational projection) that is concave with respect to the windward side, and each propeller fan 30 is viewed from the airflow direction.
- the blade 31 cross-sectional shape is concave with respect to the windward side in the radial cross section.
- An air conditioner outdoor unit provided with these two propeller fans 30 is provided.
- the rotational energy (waste energy associated with the rotational flow) of the leeward propeller fan 30 is recovered by the counter-rotating leeward propeller fan 30, and further the leeward propeller fan 30 wake Since the rotational flow of the air can be reduced to almost zero, the static pressure and air volume can be increased compared to the case where only one large propeller fan is used in the outdoor unit 1 of the air conditioner. It becomes possible to improve the point static pressure efficiency.
- the tip vortex generated near the tip side of the suction surface of the propeller fan The above-mentioned concave portion of the radial cross-section blade 31 on the windward side of the cross-sectional shape promotes the generation of the tip vortex and optimizes the flow state of the blade 31 of each propeller fan 30.
- the pressure efficiency can be further improved.
- the concave wing shape of the propeller fan 30 can achieve this effect more effectively if it is used for both forces that are effective even if it is used for either one of the fans.
- each propeller fan 30 is longer than the hub 34 chord length, the tip load is increased, the tip vortex is generated quickly and strongly, and the break down is performed quickly. Therefore, fan noise and fan efficiency can be improved without interfering with the rear wing.
- FIG. 10 is a meridional view of the propeller fan of the counter rotating fan of the outdoor unit in the fifth embodiment of the present invention.
- FIG. 11 is a radial sectional view of the propeller fan shown in FIG.
- Individual up-and-down propeller fans are standardized as 36.
- the propeller fan 36 includes two blades 37 and includes a front edge 38, a rear edge 39, a hub 40, and a tip 41.
- C—C is the midpoint of wing 37.
- Two propeller fans 36 double-reversing fan) that rotate counterclockwise on the same axis are the leading edge 38 on the meridian plane (rotational projection).
- the side of the blade 40 is convex
- the side of the hub 40 is convex
- the cross section of the blade 37 in the radial cross section is concave on the tip 41 side with respect to the windward side, and the hub 40 side is convex.
- An air conditioner outdoor unit provided with these two propeller fans 36 is provided.
- the rotational energy (waste energy associated with the rotational flow) of the leeward propeller fan 36 is recovered by the counter-rotating leeward propeller fan 36, and further the leeward propeller fan 36 wake Since the rotational flow of the air can be made almost zero, the static pressure and air volume can be increased compared to the case where only one large propeller fan is used in the outdoor unit 1 of the air conditioner. It becomes possible to improve the point static pressure efficiency.
- the tip vortex generated near the tip side of the suction surface of the propeller fan 36 The tip of the tip 41 side of the blade 37 in the radial cross-section is concave with respect to the windward side, which promotes the generation of the tip vortex. Blades with the above-mentioned radial cross-section 36 Hub with cross-sectional shape 40 side
- the convex part attracts the flow flowing radially from the outer peripheral side of the blade 37 of the propeller fan 36.
- the flow state of the blades 37 of the individual propeller fans 36 can be most optimized, so that the operating point static pressure efficiency can be further improved.
- the concave and convex wing shape of the propeller fan 36 is effective even if it is used for either one of the fans, but the effect can be exhibited more when it is used for both.
- each propeller fan 36 is larger than the hub chord length of the hub 40, the load on the blade tip is strengthened so that the blade tip vortex is generated quickly and strongly, and the break down is fast. Therefore, fan noise and fan efficiency can be improved without interfering with the rear wing.
- FIG. 12 is a plan view in the A direction of the upwind mixed flow fan of the outdoor unit according to the sixth embodiment of the present invention
- FIG. 13 is a plan view in the A direction of the downwind mixed flow fan
- FIG. Child FIG. Individual wind up and down propeller fans are unified as 42.
- the upwind mixed flow fan 42 includes two blades 43, a leading edge 44, a trailing edge 45, a tip 46, and a hub 47 that have advanced in the rotational direction.
- the leeward mixed flow fan is composed of two blades 49, a leading edge 50, a trailing edge 51, a tip 52, and a hub 53 that have advanced in the rotational direction. Two counter-rotating fan forces on the same axis are used to promote heat exchange, not a propeller fan, but a mixed-flow fan.
- Each blade 43, 49 has a chord-shaped curved direction, and the three-dimensional coordinate system
- the mixed flow fans 42 and 48 (double-reversing fan) are designed to be nearly line-symmetric with respect to the same axial force, and the number of blades 47 and 53 of the mixed flow fans 42 and 48 is It is formed in a substantially frustum shape.
- the present invention provides an air conditioner outdoor unit equipped with the two mixed flow fans 42 and 48.
- the windward mixed flow fan 42 rotates faster than the leeward mixed flow fan 48.
- Leading edges 44 and 50 are advanced in the direction of rotation. This leading edge 44, 50 is a force composed of a spiral curve.
- the trailing edge 45, 51 is a straight line, and a triangular wing (triangular wing) is attached to the outer circumference side in close contact with the straight leading edge.
- the radii of the blades 43 and 49 may be configured to be the same.
- the rotational energy of the wakeward mixed flow fan 42 wake (waste energy associated with the rotational flow) is recovered by the counterclockwise leeward mixed flow fan 48, and further, the leeward mixed flow fan 48 Since the rotational flow of the wake can be made almost zero, the static pressure and the air volume are increased compared to the case where only one fan with mixed flow is used for the air conditioner outdoor unit 1. It is possible to improve the operating point static pressure efficiency. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan. When a fan with a large fan diameter is used for the outdoor unit 1 of the air conditioner, the static pressure decreases, as is obvious from the similarity force between the fan diameter and the rotational speed of the blower.
- the outer side 46, 52 chord length of each mixed flow fan 42, 48 is larger than the hub 47, 53 chord length (However, at least the outer 46,52 chord length is the same length as the hub 47,53 chord length), the wing tip load is increased and the wing tip vortex is generated quickly and strongly. It is possible to break down, and it is possible to improve fan noise and fan efficiency without interfering with the rear wing.
- leading edges 44 and 50 are forces that advance in the rotational direction.
- the up-and-down mixed-flow fans 42 and 48 maintain point symmetry and the leading edges 44 , 50 can exert the effect of the double reversing fan even if it moves backward in the rotation direction.
- the wind-upward and lower-side mixed flow fans 42 and 48 are not at least line-symmetrical, and the directional relationship of the rotating blade row as shown in Fig. 5 (if Fig.
- either the front edge 44 or 50 of the up-and-down side mixed flow fan 42 or 48 can be a combination of forward and reverse with respect to the rotation direction. I can do it.
- FIG. 15 is a meridional view of each counter flow fan of the counter rotating fan of the present invention
- FIG. 16 is a radial sectional view of each counter flow fan of the counter rotating fan of the present invention.
- Individual wind-upper propeller fans are standardized as symbol 60.
- the blade 61 of the up-and-down side mixed flow fan 60 includes a leading edge 62, a trailing edge 63, a tip 64, and a hub 65.
- D—D is the midpoint of wing 61.
- the two counter-rotating fans on the same axis that promote rotation are not propeller fans but mixed-flow fans 60 (double reversing fans). They are designed almost symmetrically with the same axial force and have 2 blades.
- the mixed flow fan 60 is a mixed flow fan 60, and the hub shape 65 of the mixed flow fan 60 is formed in a substantially truncated cone shape, and the leading edge 62 on the meridian surface (rotational projection) of the mixed flow fan 60 is a blade against the windward side.
- the tip 64 side is concave
- the hub 65 side is convex
- the blade 61 cross section is concave on the tip 64 side with respect to the windward side
- the hub 65 side is It constitutes an air conditioner with two convex fans 60 that are convex.
- the rotational energy of the downstream of the upwind mixed-flow fan 60 (waste energy associated with the rotational flow) is recovered by the counter-rotating leeward mixed flow fan 60, and further, the downwind mixed flow fan 60 Since the rotational flow of the wake can be made almost zero, the outdoor unit 1 of the air conditioner Larger size ⁇ Static pressure and air volume can be increased compared to the case of using only one mixed flow fan, and the operating point static pressure efficiency can be improved. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan. When a fan with a large fan diameter is used for the outdoor unit 1 of the air conditioner, the static pressure decreases, as is obvious from the similar law of the fan diameter and rotation speed of the blower. Therefore, when a fan with a large fan diameter is inserted into the outdoor unit 1 of the air conditioner, the power of using a mixed flow fan with a high static pressure is optimal. This will improve the operating point static pressure efficiency.
- the suction surface force of the two counter-rotating counter-rotating fans 60 on the same axis is generated near the tip 64 side of the suction surface of the counter-flow fan 60 due to the leakage flowing toward the pressure surface.
- the tip vortex has a concave portion on the tip 64 side of the wing 61 in the radial cross section with respect to the windward side to promote the generation of the tip vortex.
- the above-mentioned radial cross-section blade 61 The cross-section of the hub 65 on the side of the cross section attracts the flow force in the radial direction of the blade of the mixed flow fan 60.
- the flow state of the blades of each mixed flow fan 60 can be optimized most, and the operating point static pressure efficiency can be further improved.
- the uneven wing shape of the mixed flow fan 60 can exert this effect more effectively when it is applied to both of the forces that are effective even when applied to either one of the fans.
- each mixed flow fan 60 is larger than the chord length of the hub 65! /, So the load on the wing tip is increased and the wing tip vortex is generated quickly and strongly. It is possible to break down and to improve fan noise and fan efficiency without interfering with the rear wing.
- FIG. 17 is a meridional view of an individual mixed flow fan of the counter rotating fan of the present invention
- FIG. 18 is a radial sectional view of an individual counter flow fan of the counter rotating fan of the present invention.
- the up-and-down mixed-flow fan is unified as 66.
- the blade 67 of the up-and-down mixed flow fan 66 includes a front edge 68, a rear edge 69, a tip 70, and a knob 71.
- the two counter-rotating fans on the same axis are not propeller fans but mixed flow fans 66 (double reversing fans). It is a mixed flow fan 66 that is formed in a truncated cone shape and is designed to be nearly line-symmetric when viewed from the same axial direction and has two blades.
- the rotational energy (waste energy associated with the rotational flow) of the leeward mixed-flow fan 66 is recovered by the counter-rotating leeward mixed flow fan 66, and further, the leeward mixed flow fan 66 Since the rotational flow of the wake can be made almost zero, the static pressure and the air volume can be increased compared to the case where only a single fan with a large size is used for the outdoor unit 1 of the air conditioner. It is possible to improve the operating point static pressure efficiency. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan.
- the static pressure decreases, as is obvious from the similar law of the fan diameter and rotation speed of the blower. Therefore, when a fan with a large fan diameter is inserted into the outdoor unit 1 of the air conditioner, it is optimal to use a mixed flow fan with a high static pressure. This will improve the operating point static pressure efficiency. Furthermore, the suction surface force of the two counter-rotating counter flow fans 66 on the same axis causes the tip vortices generated near the tip side 70 of the suction surface of the mixed flow fan 66 due to leakage leaking toward the pressure surface.
- the flow state of the blade 67 of each mixed flow fan 66 can be optimized.
- the operating point static pressure efficiency can be further improved.
- the concave blade shape of the mixed flow fan 66 can achieve this effect more effectively if it is used for both forces that are effective even if it is used for either one of the fans.
- chord length on the outer peripheral side of each mixed flow fan 66 is larger than the chord length on the hub 71 side, the load at the wing tip is strengthened so that the wing tip vortex is generated quickly and strongly, and the breakdown is quickly performed. Therefore, fan noise and fan efficiency can be improved without interfering with the rear wing.
- the outdoor unit of the air conditioner according to the present invention collects the rotational energy (wasteful energy associated with the rotational flow) downstream of the windward propeller fan with the leeward propeller fan that counter-rotates. Furthermore, the rotational flow behind the leeward propeller fan can be made almost zero. Therefore, compared to the case where only one large propeller fan is used for the outdoor unit of the air conditioner, the static pressure and the air volume can be increased, and the operating point static pressure efficiency can be improved. It becomes. As a result, it is possible to reduce the fan motor input and reduce the COP and period power consumption of the air conditioner, or suppress the reduction of the air volume against the blowing resistance and reduce the noise. Applicable to various air conditioners such as packaged air conditioners.
- this double reversing fan can be applied to consumer equipment, which is an industrial product that uses a fan. In other words, it can be deployed as a ventilation fan, fan, computer cooling fan, etc.
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Abstract
An outdoor unit (1) for an air conditioner, having improved COP and periodic electric power consumption of the air conditioner, which is achieved by reducing an input to a fan motor of the outdoor unit to enhance static pressure efficiency. The outdoor unit (1) has two propeller fans (5, 6) for promoting heat exchange and rotating in opposite directions to each other, a fan motor (7) for rotating the upwind propeller fan (5) of the two propeller fans, and a reversing mechanism (8) for reversing the rotation direction of the fan motor (7) and transmitting the reversed rotation. The downwind propeller fan (6) is provided coaxial with and on the downstream side of the upwind propeller fan (5) and is reversely rotated by the reversing mechanism (8). The upwind and downwind propeller fans (5, 6) have blade shapes whose chords are bent in the opposite directions and that are line symmetrically formed when viewed from the axis direction. The fans (5, 6) are rotated in the opposite directions from each other but produce airflow in the same direction.
Description
明 細 書 Specification
空気調和機の室外機 Air conditioner outdoor unit
技術分野 Technical field
[0001] 本発明は、空気調和機の室外機などに用いられる熱交換促進用の送風機に関 するもので、特に送風機のファン効率 (静圧効率)向上の技術に関するものである。 背景技術 TECHNICAL FIELD [0001] The present invention relates to a heat exchange accelerating blower used for an outdoor unit of an air conditioner, and more particularly to a technique for improving fan efficiency (static pressure efficiency) of the blower. Background
[0002] この種の空気調和機は、熱交換器と送風機とを有する室内機と、圧縮機と熱交換 器と送風機とを有する室外機とを配管で結んで冷凍サイクルを形成し、冷凍サイクル 内に充填した冷媒の熱搬送によって冷房運転又は暖房運転することによって室内の 空気調和を行っている。室外機において、送風機は熱交換器の熱交換促進を行うも のとしてファンとファンモータとを備えて構成される力 この送風機の風量は空気調和 機の能力を大きく左右するとともに、騒音まで含めた性能に大きな影響がある。 [0002] This type of air conditioner forms a refrigeration cycle by connecting an indoor unit having a heat exchanger and a blower and an outdoor unit having a compressor, a heat exchanger, and a blower by piping. Air conditioning is performed indoors by cooling operation or heating operation by heat transfer of the refrigerant filled inside. In the outdoor unit, the blower is configured to include a fan and a fan motor to promote heat exchange of the heat exchanger. The air volume of this blower greatly affects the performance of the air conditioner and includes noise. The performance is greatly affected.
[0003] 特に、暖房運転においては室外機の熱交換器に空気中の水分が凝縮して露とな つて付着し、それが熱交 を通過する気流を妨げるようになる。それがさらに低温 になると露が氷や霜となって目詰まりするような状態となるため、そのような状況でも 風量の低下を抑制し、騒音を低減するためには送風機のファン効率の向上は重要で ある。 [0003] In particular, in heating operation, moisture in the air condenses on the heat exchanger of the outdoor unit and adheres as dew, which interferes with the airflow passing through the heat exchange. At lower temperatures, the dew becomes clogged with ice and frost, so even in such a situation, the fan efficiency of the blower must be improved in order to suppress the decrease in air volume and reduce noise. is important.
[0004] 空気調和機の室外機などに用いられる熱交換促進用の送風機と、その動圧を回収 する効率を高めて騒音の低減を目的とした後置静翼に関する技術が開示されている (例えば、 JP2002— 81695A参照)。 [0004] A blower for promoting heat exchange used for an outdoor unit of an air conditioner, and a technology related to a rear stationary blade for the purpose of reducing noise by increasing the efficiency of recovering its dynamic pressure are disclosed ( For example, see JP2002-81695A).
[0005] 図 19は、従来の空気調和機の室外機の横断面図である。室外機 80は、本体外箱 84に圧縮機スペース 83、熱交換器 81、熱交換促進用のファンモータ 82と送風機 8 5、動圧を回収する後置静翼 86、オリフィス 87を備え、送風機 85とその動圧を回収 する後置静翼 86をファンモータ 82の同一軸心上に風上側力 配置して構成してい る。 FIG. 19 is a cross-sectional view of an outdoor unit of a conventional air conditioner. The outdoor unit 80 includes a compressor space 83, a heat exchanger 81, a fan motor 82 and a blower 85 for heat exchange promotion, a rear stationary blade 86 for recovering dynamic pressure, and an orifice 87 in a main body outer box 84. 85 and a rear stationary vane 86 that recovers the dynamic pressure are arranged on the same axis of the fan motor 82 as windward force.
発明の開示 Disclosure of the invention
発明が解決しょうとする課題
[0006] しかしながら、上記従来の構成では、送風機 85の絶対速度 Cの周方向成分 V Problems to be solved by the invention However, in the above conventional configuration, the circumferential component V of the absolute speed C of the blower 85
2 Θ を後置静翼 86で回収しても、静翼による回収では V を回収しきれず、動圧の静圧へ 2 Even if Θ is recovered by the rear stationary vane 86, V cannot be recovered by the stationary vane recovery.
Θ Θ
の変換には限界があった。即ちここで言う動圧は、 Pd=0. 5 * p * V 2 ( p:密度で There was a limit to the conversion. That is, the dynamic pressure here is Pd = 0.5 * p * V 2 (p:
Θ Θ
単位は kg ' sec2' m4であり、 Cと V の単位は m/sec)である。ちなみに、 Φ415ππη The unit is kg 'sec 2 ' m 4 and the unit of C and V is m / sec). By the way, Φ415ππη
2 Θ 2 Θ
の送風機 85に後置静翼 86を装着した場合、動作点静圧効率の向上は、比率で約 7 %程度であった。 When the rear stationary vane 86 was attached to the blower 85, the improvement of the operating point static pressure efficiency was about 7%.
[0007] 本発明は、前記従来の課題を解決するもので、送風機のファン効率 (静圧効率)を 向上して静圧と風量を増加させる、ある 、は送風抵抗に対しても風量の低下を抑制 し、騒音を低減することができる空気調和機の室外機を提供することを目的とする。 課題を解決するための手段 [0007] The present invention solves the above-described conventional problems, and improves the fan efficiency (static pressure efficiency) of the blower to increase the static pressure and the air volume. The purpose is to provide an outdoor unit for an air conditioner that can suppress noise and reduce noise. Means for solving the problem
[0008] 上記課題を解決するために、本発明の空気調和機の室外機は、圧縮機と、熱交換 器と、前記熱交^^の熱交換促進用のファンとして 2個のプロペラファンとを備え、前 記 2個のプロペラファンは同軸上に近接して設け、互いに反対方向に回転 (反回転) しながら気流方向は同一となるように構成したものである。 [0008] In order to solve the above problems, an outdoor unit of an air conditioner according to the present invention includes a compressor, a heat exchanger, and two propeller fans as fans for promoting heat exchange of the heat exchanger. The two propeller fans are provided close to each other on the same axis, and are configured such that the airflow directions are the same while rotating in the opposite directions (reverse rotation).
[0009] これによつて、 2個のプロペラファンのうち風上側となるプロペラファンの後流の回転 エネルギー(回転流に伴う無駄となるエネルギー)を、近接して反回転 (互いに反対 方向に回転)する風下側となるプロペラファンで回収し、更に風下側プロペラファン後 流の回転流をほぼ零とする事ができる。すなわち、空気調和機の室外機にサイズの 大き 、(奥行きが本発明のプロペラファン 2個分と同等程度の)プロペラファン一つの み使用する場合に比較して、動作点静圧効率を向上する事ができて、静圧と風量を 増加する、あるいは送風抵抗に対しても風量の低下を抑制し、騒音を低減する事が 可能となる。その結果ファンモータ入力を低減できて空気調和機の COP(Coefficient of performance)や期間消費電力、および騒音を低減する事が可能となる。 [0009] Accordingly, the rotational energy of the wake behind the propeller fan that is on the windward side of the two propeller fans (the energy that is wasted due to the rotational flow) is closely counter-rotated (rotated in the opposite direction to each other). The propeller fan on the leeward side can be recovered, and the rotational flow after the leeward propeller fan can be made almost zero. That is, the operating point static pressure efficiency is improved as compared with the case of using only one propeller fan (the depth is equivalent to two propeller fans of the present invention) for the outdoor unit of the air conditioner. It is possible to increase the static pressure and air flow, or to suppress the decrease of air flow against the air blowing resistance and reduce the noise. As a result, the fan motor input can be reduced, and the COP (Coefficient of performance), period power consumption, and noise of the air conditioner can be reduced.
発明の効果 The invention's effect
[0010] 本発明の空気調和機の室外機は、風上側プロペラファン後流の回転エネルギー( 回転流に伴う無駄となるエネルギー)を反回転する風下側プロペラファンで回収し、 更に風下側プロペラファン後流の回転流をほぼ零とする事ができるので、空気調和 機の室外機にサイズの大き 、プロペラファン一つのみ使用する場合に比較して、静
圧と風量を増加させる事が出来て、動作点静圧効率を向上させる事が可能となる。そ の結果ファンモータ入力を低減できて空気調和機の COPや期間消費電力を低減す る、あるいは送風抵抗に対しても風量の低下を抑制し、騒音を低減する事が可能とな る。 [0010] The outdoor unit of the air conditioner of the present invention collects the rotational energy (waste energy associated with the rotational flow) downstream of the windward propeller fan with a counter-rotating leeward propeller fan, and further leeward propeller fan. Since the rotational flow of the wake can be reduced to almost zero, the size of the outdoor unit of the air conditioner is larger than when only one propeller fan is used. The pressure and air volume can be increased, and the operating point static pressure efficiency can be improved. As a result, the fan motor input can be reduced and the COP and period power consumption of the air conditioner can be reduced, or the reduction of the air volume can be suppressed and the noise can be reduced.
[0011] そして、特に暖房運転において、室外機の熱交換器に空気中の水分が凝縮して露 となって付着し、それがさらに低温になると露が氷や霜となって目詰まりするような状 態となり、それが熱交換器を通過する気流を妨げるような状況になっても、風量の低 下を抑制し、騒音の増力 []も抑制するような、送風機の効率が良い空気調和機の室外 機を提供することができる。 [0011] In particular, in heating operation, moisture in the air condenses and adheres as dew to the heat exchanger of the outdoor unit, and dew becomes clogged as ice or frost when the temperature further decreases. The air conditioner is highly efficient and the air flow is reduced and the noise increase [] is suppressed even when the air flow through the heat exchanger is disturbed. An outdoor unit can be provided.
図面の簡単な説明 Brief Description of Drawings
[0012] [図 1]本発明の実施の形態 1における空気調和機の室外機の横断面図である。 FIG. 1 is a cross-sectional view of an outdoor unit of an air conditioner according to Embodiment 1 of the present invention.
[図 2]本発明の実施の形態 1における空気調和機の室外機の風上側プロペラファン の A方向平面図である。 FIG. 2 is a plan view in the A direction of the windward propeller fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
[図 3]本発明の実施の形態 1における空気調和機の室外機の風下側プロペラファン の A方向平面図である。 FIG. 3 is a plan view in the A direction of the leeward propeller fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
[図 4]本発明の実施の形態 1における空気調和機の室外機のプロペラファンのァスぺ タト比一風量特性図である。 [Fig. 4] Fig. 4 is a characteristic flow rate characteristic airflow ratio of a propeller fan of an outdoor unit of an air conditioner according to Embodiment 1 of the present invention.
[図 5]本発明の実施の形態 1における空気調和機の室外機の風上下側プロペラファ ンの自乗平均半径位置の円筒切断面の展開翼列と速度三角形を示す性能図である FIG. 5 is a performance diagram showing a developed blade row and a speed triangle of a cylindrical cut surface at a mean square radius position of the wind upper and lower propeller fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
[図 6]本発明の実施の形態 1における空気調和機の室外機の風上下側プロペラファ ン(2重反転ファン)の静圧 風量特性図である。 [Fig. 6] Fig. 6 is a static pressure / air flow characteristic diagram of a wind upper / lower propeller fan (double reversing fan) of an outdoor unit of an air conditioner according to Embodiment 1 of the present invention.
[図 7]本発明の実施の形態 2における空気調和機の室外機の横断面図である。 FIG. 7 is a cross-sectional view of an outdoor unit of an air conditioner according to Embodiment 2 of the present invention.
[図 8]本発明の実施の形態 4における空気調和機の室外機の風上下側プロペラファ ンの子午面図である。 FIG. 8 is a meridional view of a wind up / down propeller fan of an outdoor unit of an air conditioner according to Embodiment 4 of the present invention.
[図 9]本発明の実施の形態 4における空気調和機の室外機の風上下側プロペラファ ンの半径方向断面図である。 FIG. 9 is a radial cross-sectional view of a wind up / down propeller fan of an outdoor unit of an air conditioner according to Embodiment 4 of the present invention.
[図 10]本発明の実施の形態 5における空気調和機の室外機の風上下側プロペラファ
ンの子午面図である。 [Fig. 10] Wind up and down side propeller fan of the outdoor unit of the air conditioner according to Embodiment 5 of the present invention. FIG.
[図 11]本発明の実施の形態 5における空気調和機の室外機の風上下側プロペラファ ンの半径方向断面図である。 FIG. 11 is a radial cross-sectional view of a wind up / down propeller fan of an outdoor unit of an air conditioner according to Embodiment 5 of the present invention.
[図 12]本発明の実施の形態 6における空気調和機の室外機の風上側斜流ファンの A 方向平面図である。 FIG. 12 is a plan view in the A direction of an upwind mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 6 of the present invention.
[図 13]本発明の実施の形態 1における空気調和機の室外機の風下側斜流ファンの A 方向平面図である。 FIG. 13 is a plan view in the A direction of the leeward mixed flow fan of the outdoor unit of the air conditioner according to the first embodiment of the present invention.
[図 14]本発明の実施の形態 6における空気調和機の室外機の風上下側斜流ファン の子午面図である。 FIG. 14 is a meridional view of an up-down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 6 of the present invention.
[図 15]本発明の実施の形態 7における空気調和機の室外機の風上下側斜流ファン の子午面図である。 FIG. 15 is a meridional view of an up-down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 7 of the present invention.
[図 16]本発明の実施の形態 7における空気調和機の室外機の風上下側斜流ファン の半径方向断面図である。 FIG. 16 is a radial cross-sectional view of a wind up / down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 7 of the present invention.
[図 17]本発明の実施の形態 8における空気調和機の室外機の風上下側斜流ファン の子午面図である。 FIG. 17 is a meridional view of an up-down mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 8 of the present invention.
[図 18]本発明の実施の形態 8における空気調和機の室外機の風上下側斜流ファン の半径方向断面図である。 FIG. 18 is a radial cross-sectional view of a wind up / down side mixed flow fan of an outdoor unit of an air conditioner according to Embodiment 8 of the present invention.
[図 19]従来の実施例の空気調和機の室外機の横断面図である。 FIG. 19 is a cross-sectional view of an outdoor unit of an air conditioner according to a conventional example.
発明を実施するための最良の形態 BEST MODE FOR CARRYING OUT THE INVENTION
[0013] 第 1の発明は、圧縮機と、熱交換器と、前記熱交換器の熱交換促進用のファンとし て 2個のプロペラファンとを備え、前記 2個のプロペラファンは同軸上に近接して設け 、互いに反対方向に回転 (反回転)しながら気流方向は同一となるように構成したも のである。 [0013] A first invention includes a compressor, a heat exchanger, and two propeller fans as fans for promoting heat exchange of the heat exchanger, and the two propeller fans are coaxial. They are provided close to each other and are configured so that the airflow directions are the same while rotating (reversely rotating) in opposite directions.
[0014] これによつて、 2個のプロペラファンのうち風上側となるプロペラファンの後流の回転 エネルギー(回転流に伴う無駄となるエネルギー)を、近接して反回転 (互いに反対 方向に回転)する風下側となるプロペラファンで回収し、更に風下側プロペラファン後 流の回転流をほぼ零とする事ができる。すなわち、空気調和機の室外機にサイズの 大き 、(奥行きが本発明のプロペラファン 2個分と同等程度の)プロペラファン一つの
み使用する場合に比較して、動作点静圧効率を向上する事ができて、静圧と風量を 増加する、あるいは熱交換器に付着した露や霜などの送風抵抗による風量の低下を 抑制し、騒音を低減する事が可能となる。その結果ファンモータ入力を低減できて空 気調和機の COPや期間消費電力、および騒音を低減する事が可能となる。 [0014] Thus, the rotational energy behind the propeller fan on the windward side of the two propeller fans (waste energy associated with the rotational flow) is closely counter-rotated (rotated in the opposite direction to each other). The propeller fan on the leeward side can be recovered, and the rotational flow after the leeward propeller fan can be made almost zero. That is, the size of the outdoor unit of the air conditioner is large, and the depth of one propeller fan (the depth is the same as the two propeller fans of the present invention) Compared to the case of using only the operating point, the static pressure efficiency at the operating point can be improved, and the static pressure and the air volume are increased, or the decrease in the air volume due to the blowing resistance such as dew and frost attached to the heat exchanger is suppressed. In addition, noise can be reduced. As a result, the fan motor input can be reduced and the COP, period power consumption, and noise of the air conditioner can be reduced.
[0015] 第 2の発明は、特に第 1の発明の空気調和機の室外機において、 2個のプロペラフ アンを、各々の翼形状が弦形状の湾曲方向が逆であり、同一軸心方向から見て線対 称に形成したもので、換言すれば、一方のプロペラファンの平面形状は反転したとき に同一又は相似形である。これによつて、形状として変更するのはハブだけであると ともに、 2重反転ファンとしての性能を発揮させるための設計が容易となる。 [0015] The second aspect of the invention is the outdoor unit of the air conditioner of the first aspect of the invention, in particular, the two propellers are each of which the wing shape is a chord shape and the bending direction is opposite, In other words, the plane shape of one propeller fan is the same or similar when reversed. As a result, only the hub is changed as the shape, and the design for demonstrating the performance as a double reversing fan becomes easy.
[0016] 第 3の発明は、特に第 1又は 2の発明の空気調和機の室外機において、 1個のファ ンモータと、前記ファンモータの回転方向を反転して伝達する反転機構とをプロペラ ファンと同軸上に備え、 2個のプロペラファンのうち、一方のプロペラファンを前記ファ ンモータで駆動し、他方のプロペラファンを前記反転機構で駆動するようにしたもの である。 [0016] The third invention is a propeller fan, particularly in the outdoor unit of the air conditioner of the first or second invention, wherein one fan motor and a reversing mechanism for reversing the rotation direction of the fan motor are transmitted. Of the two propeller fans, one propeller fan is driven by the fan motor, and the other propeller fan is driven by the reversing mechanism.
[0017] これによつて、 1個のファンモータで 2個のプロペラファンを互いに反対方向に回転 するように駆動することが可能であり、重量のあるファンモータが一つなので空気調 和機の室外機の構成部品が少なぐ低コストで軽量に生産することができる。 [0017] With this, it is possible to drive two propeller fans to rotate in opposite directions with one fan motor, and since there is one heavy fan motor, the air conditioner's It can be produced at low cost and light weight with fewer components of the outdoor unit.
[0018] 第 4の発明は、特に第 3の発明の空気調和機の室外機において、風上側力 順番 に熱交換器、ファンモータ、風上側プロペラファン、反転機構、風下側プロペラファン となるように配設し、前記風上側プロペラファンを前記ファンモータで駆動し、前記風 下側プロペラファンを前記反転機構で駆動するようにしたものである。 [0018] The fourth aspect of the invention is, in particular, in the outdoor unit of the air conditioner of the third aspect of the invention, in order of the windward force, the heat exchanger, the fan motor, the windward propeller fan, the reversing mechanism, and the leeward propeller fan. The leeward propeller fan is driven by the fan motor, and the leeward propeller fan is driven by the reversing mechanism.
[0019] 上記構成によって、熱交換器より少しでも遠くに 2個のプロペラファンを配置して、 熱交^^とプロペラファンとの間に少しでも大きな空間を構成することができるので、 熱交換器の風速分布を均一にして、より熱交換促進を図ることができる。また、熱交 と風上側プロペラファンとの干渉による風切り音も発生しない。さらに、風下側プ 口ペラファンの下流にファンモータが存在しないので通風抵抗を少なくすることができ る。 [0019] With the above configuration, two propeller fans can be arranged as far as possible from the heat exchanger, and a large space can be formed between the heat exchanger ^^ and the propeller fan. It is possible to further promote heat exchange by making the wind speed distribution of the vessel uniform. In addition, there is no wind noise due to the interaction between the heat exchanger and the windward propeller fan. Furthermore, since there is no fan motor downstream of the leeward side blower fan fan, the draft resistance can be reduced.
[0020] 第 5の発明は、第 3又は第 4の発明の反転機構が、風上側プロペラファンのハブ内
部、もしくは風下側プロペラファンのハブ内部、あるいは風上側及び風下側プロペラ ファンの両方のハブ内部に収納されたもので、 2個のプロペラファン同士をより近接し て構成することが可能となる。 [0020] In a fifth aspect, the reversing mechanism of the third or fourth aspect is provided in the hub of the windward propeller fan. Or in the hub of the leeward propeller fan, or in the hubs of both the leeward and leeward propeller fans, the two propeller fans can be configured closer together.
[0021] 第 6の発明は、第 1又は 2の発明において、 2個のファンモータを 2個のプロペラファ ンそれぞれに備え、 2個のプロペラファンをそれぞれに設けたファンモータにより駆動 するようにしたもので、 2個のプロペラファンの回転数を個別に調整することができ、 運転状況に応じた任意の設定が可能となる。 [0021] The sixth invention is such that, in the first or second invention, two fan motors are provided in each of the two propeller fans, and the two propeller fans are driven by the fan motors provided respectively. As a result, the rotation speed of the two propeller fans can be adjusted individually, and any setting can be made according to the operating conditions.
[0022] 第 7の発明は、第 3〜第 6の発明にお 、て、ファンモータをアウターロータ式としたも ので、ファンモータをプロペラファンのハブ内部に構成することでファンモータのため のスペースが不要となるので、室外機の風路となる空間をより有効に利用することが 可能となって、熱交^^の風速分布の均一化や騒音低減の向上を図ることができる 。また、室外機を小型化することが可能となる。 [0022] In a seventh invention according to the third to sixth inventions, since the fan motor is an outer rotor type, the fan motor is configured inside the hub of the propeller fan, so that the fan motor is provided. Since no space is required, it is possible to more effectively use the space that becomes the air path of the outdoor unit, and it is possible to make the air velocity distribution of the heat exchanger ^ uniform and improve noise reduction. In addition, the outdoor unit can be downsized.
[0023] 第 8の発明は、第 1〜第 7の発明において、同軸上の反回転する 2個のプロペラファ ン(2重反転ファン)のそれぞれの回転数を変えて設定したもので、反回転する 2個の プロペラファンの回転数を変えることにより、個々のプロペラファンの速度三角形が異 なり、個々のプロペラファンの翼列が仕事をする時間のタイミングがずれるので、それ ぞれの翼列が仕事をする時間軸をとつても干渉することがなぐ高調による離散的騒 音のピークを発生する事も無ぐ低騒音にもできる。 [0023] In an eighth invention according to the first to seventh inventions, the rotational speed of each of the two counter-rotating propeller fans (co-rotating fan) on the same axis is changed. By changing the rotation speed of the two propeller fans that rotate, the speed triangles of the individual propeller fans differ, and the timing of the work time of the individual propeller fan blades shifts. Even if the time axis of work is taken, the peak of discrete noise due to harmonics that do not interfere with each other can be generated, and low noise can be achieved.
[0024] 第 9の発明は、第 1〜第 8の発明において、プロペラファンの翼の自乗平均半径位 置での翼弦長 Lと翼の半径方向の代表実長さ bとの比であるアスペクト比 bZLが bZ L≤l. 1であり、前記プロペラファンの外周側翼弦長がハブ側翼弦長以上としたもの である。 [0024] The ninth invention is the ratio of the chord length L at the mean square radial position of the blade of the propeller fan to the representative actual length b in the radial direction of the blade in the first to eighth inventions. The aspect ratio bZL is bZ L≤l. 1, and the outer peripheral chord length of the propeller fan is greater than or equal to the hub chord length.
[0025] 各々のプロペラファンの外周側弦長がハブ側弦長より長く構成されて ヽるので、翼 端での翼面積を大きく確保することが空力負荷を充分に吸収して仕事を行 、、各々 のプロペラファン自体のファン効率向上と低騒音化を達成することになる。更に、ァス ぺクト比 bZL≤l. 1に設定すると、騒音当たりの風量を多くすることができる。 [0025] Since the outer chord length of each propeller fan is configured to be longer than the hub chord length, securing a large blade area at the blade tip sufficiently absorbs the aerodynamic load and performs work. Therefore, the fan efficiency of each propeller fan itself is improved and the noise is reduced. Furthermore, if the aspect ratio is set to bZL≤l. 1, the air volume per noise can be increased.
[0026] 第 10の発明は、第 1〜第 9の発明において、同軸上の反回転する 2個のプロペラフ アン(2重反転ファン)が子午面(回転投影図、 Meridional plane)上の前縁が風上
側に対し凹状であり、半径方向断面で翼断面形状が風上側に対し凹状であり、個々 のプロペラファンの外周側弦長をノヽブ側弦長以上に構成したものである。 [0026] In a tenth aspect based on the first to ninth aspects, the two counter-rotating propellers (double reversing fans) that are coaxially rotated counterclockwise are the leading edges on the meridional plane (meridional plane). Upwind Concave with respect to the side, blade cross-sectional shape with a radial cross section is concave with respect to the windward side, and the outer chord length of each propeller fan is configured to be longer than the nose chord length.
[0027] 上記の構成によって、風上側プロペラファン後流の回転エネルギー(回転流に伴う 無駄となるエネルギー)を反回転する風下側プロペラファンで回収し、更に風下側プ 口ペラファン後流の回転流をほぼ零とする事ができるので、空気調和機の室外機に サイズの大き 、プロペラファン一つのみ使用する場合に比較して、静圧と風量を増加 させる事が出来て、動作点静圧効率を向上させる事が可能となる。更に、同軸上の 反回転する 2個のプロペラファンの負圧面力 圧力面に向力う洩れ流れを一因として 、プロペラファンの負圧面のチップ側付近に発生する翼端渦を、上記の半径方向断 面の翼断面形状の風上側に対し凹状部分が、この翼端渦の生成を促進させて、個 々のプロペラファンの翼の流動状態を最適化できるので、動作点静圧効率を更に向 上させる事ができる。また、個々のプロペラファンファンの外周側弦長がハブ側弦長 以上なので、翼端の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレー クダウンさせることができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向 上することが可能となる。 [0027] With the above configuration, the rotational energy of the wake of the windward propeller fan (waste energy associated with the rotational flow) is recovered by the counter-rotating leeward propeller fan, and further the rotational flow of the wake of the leeward propeller fan. The static pressure and air volume can be increased compared to the case of using only a large size propeller fan and an air conditioner outdoor unit. Efficiency can be improved. Furthermore, the suction surface force of the two counter-rotating propeller fans on the same axis causes the tip vortex generated near the tip side of the suction surface of the propeller fan to be The concave part on the windward side of the blade cross-section of the directional cross section promotes the generation of the tip vortex and optimizes the flow state of the blades of each propeller fan. Can be improved. Also, since the outer chord length of each propeller fan fan is longer than the hub chord length, the blade tip vortex can be strengthened to generate a blade tip vortex quickly and strongly, and it can be quickly broken down. The fan noise and fan efficiency can be improved without interference.
[0028] 第 11の発明は、第 1〜第 9の発明において、同軸上の反回転する 2個のプロペラフ アン (2重反転ファン)が子午面 (回転投影図)上の前縁が風上側に対し翼の中点付 近よりチップ側は凹状であり、ハブ側は凸状であり、半径方向断面で翼の断面形状 がチップ側が風上側に対し凹状であり、ハブ側が凸状であり、個々のプロペラファン ファンの外周側弦長がハブ側弦長以上に構成したものである。 [0028] In an eleventh aspect based on the first to ninth aspects, the two counter-rotating propellers (double reversing fans) that are coaxially rotated counterclockwise have a leading edge on the meridian plane (rotary projection). On the other hand, the tip side is concave from the midpoint of the wing, the hub side is convex, the cross-sectional shape of the wing in the radial cross section is concave to the windward side, and the hub side is convex. Each propeller fan The fan's outer chord length is longer than the hub chord length.
[0029] 上記の構成によって、風上側プロペラファン後流の回転エネルギー(回転流に伴う 無駄となるエネルギー)を反回転する風下側プロペラファンで回収し、更に風下側プ 口ペラファン後流の回転流をほぼ零とする事ができるので、空気調和機の室外機に サイズの大き 、プロペラファン一つのみ使用する場合に比較して、静圧と風量を増加 させる事が出来て、動作点静圧効率を向上させる事が可能となる。更に、同軸上の 反回転する 2個のプロペラファンの負圧面力 圧力面に向力う洩れ流れを一因として 、プロペラファンの負圧面のチップ側付近に発生する翼端渦を、上記の半径方向断 面の翼断面形状のチップ側が風上側に対し凹状部分が、この翼端渦の生成を促進
させる。上記の半径方向断面の翼断面形状のハブ側凸状部分がプロペラファンの翼 の外周側力 半径方向に流入してくる流れを誘引するので、翼渦の生成促進と半径 方向流の促進により、個々のプロペラファンの翼の流動状態を最も最適化できるので 、動作点静圧効率を更に向上させる事ができる。また、個々のプロペラファンファンの 外周側弦長がハブ側弦長より大きいので、翼端の負荷を強めて翼端渦を早く強く生 成させて、そして、早くブレークダウンさせることができ、後方翼に干渉せず、ファン騒 音やファン効率の性能を向上することが可能となる。 [0029] With the above configuration, the rotational energy of the wake of the windward propeller fan (waste energy associated with the rotational flow) is recovered by the counter-rotating leeward propeller fan, and further the rotational flow of the wake of the leeward propeller fan. The static pressure and air volume can be increased compared to the case of using only a large size propeller fan and an air conditioner outdoor unit. Efficiency can be improved. Furthermore, the suction surface force of the two counter-rotating propeller fans on the same axis causes the tip vortex generated near the tip side of the suction surface of the propeller fan to be The tip side of the blade cross-sectional shape of the directional cross section is concave with respect to the windward side, promoting the generation of this tip vortex Let The hub-side convex part of the blade cross-sectional shape of the above-mentioned radial cross-section attracts the flow that flows in the radial direction of the outer periphery of the blade of the propeller fan, so by promoting the generation of blade vortex and the radial flow, Since the flow state of each propeller fan blade can be optimized most, the operating point static pressure efficiency can be further improved. In addition, since the outer chord length of each propeller fan fan is larger than the hub chord length, the wing tip load can be strengthened to generate wing tip vortices quickly and strongly, and it can be quickly broken down. The fan noise and fan efficiency can be improved without interfering with the wings.
[0030] 第 12の発明は、第 1〜第 11の発明において、同軸上の反回転する 2個の熱交換 促進用のファン(2重反転ファン)力 プロペラファンを用いる代わりに斜流ファンを用 いるもので、この斜流ファンは各々の翼形状が同一軸心方向力も見てほぼ線対称に 設計され翼枚数が 1枚以上力 なる斜流ファンであり、斜流ファンのハブ形状は略円 錐台状に形成されたものである。 [0030] In a twelfth aspect of the invention according to the first to eleventh aspects of the present invention, a counter flow fan is used instead of a propeller fan instead of two counter-rotating fan (double reversing fan) forces that rotate on the same axis This mixed-flow fan is a mixed-flow fan in which each blade shape is designed to be approximately line-symmetric with respect to the same axial force, and the number of blades is one or more. It is formed in a frustum shape.
[0031] 上記の構成によって、風上側斜流ファン後流の回転エネルギー(回転流に伴う無 駄となるエネルギー)を反回転する風下側斜流ファンで回収し、更に風下側斜流ファ ン後流の回転流をほぼ零とする事ができるので、空気調和機室外機にサイズの大き ぃ斜流ファン一つのみ使用する場合に比較して、静圧と風量を増カロさせる事が出来 て、動作点静圧効率を向上させる事が可能となる。更に、基本的に斜流ファンはプロ ペラファンより静圧が高い。空気調和機の室外機にファン径の大きいファンを使用す る時に、送風機のファン径と回転数の相似則力も自明な様に、静圧は低下する。そこ で、空気調和機の室外機にファン径の大きいファンを投入する時には、静圧の高い 斜流ファンを用いるのが最適な構成となる。それは、動作点静圧効率を向上させる事 につながる。また、個々の斜流ファンファンの外周側弦長がハブ側弦長より大きいの で、翼端の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレークダウンさ せることができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向上すること が可能となる。 [0031] With the above-described configuration, the rotational energy of the wakeward-side mixed fan wake (useless energy associated with the rotational flow) is recovered by the counter-rotating leeward mixed-flow fan, and further after the leeward mixed-flow fan. Since the rotational flow of the air flow can be made almost zero, the static pressure and air volume can be increased compared to the case where only a large-size diagonal flow fan is used in the outdoor unit of the air conditioner. It is possible to improve the operating point static pressure efficiency. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan. When a fan with a large fan diameter is used for the outdoor unit of an air conditioner, the static pressure decreases, as is obvious from the similarity force between the fan diameter and the rotational speed of the blower. Therefore, when introducing a fan with a large fan diameter into the outdoor unit of an air conditioner, it is optimal to use a mixed flow fan with high static pressure. This leads to improved operating point static pressure efficiency. In addition, since the chord length on the outer peripheral side of each mixed flow fan fan is larger than the chord length on the hub side, it is possible to increase the load on the wing tip and generate a wing tip vortex quickly and strongly, and to break down quickly. Therefore, fan noise and fan efficiency can be improved without interfering with the rear wing.
[0032] 以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実 施の形態によって本発明が限定されるものではない。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.
[0033] (実施の形態 1)
図 1は、本発明の第 1の実施の形態における空気調和機の室外機の横断面図であ る。図 2は、同室外機を図 1の A方向力も見た風上側プロペラファンの平面図である。 図 3は、同室外機を A方向から見た風下側プロペラファンの平面図である。図 4は、各 プロペラファンのアスペクト比一風量特性図で、騒音 41dBあたりの風量を示す。 [Embodiment 1] FIG. 1 is a cross-sectional view of an outdoor unit of an air conditioner according to the first embodiment of the present invention. Fig. 2 is a plan view of the windward propeller fan in which the outdoor unit is also viewed in the direction A of Fig. 1. Fig. 3 is a plan view of the leeward propeller fan when the outdoor unit is viewed from the A direction. Figure 4 is an aspect ratio characteristic airflow characteristic chart of each propeller fan, showing the airflow per 41dB noise.
[0034] 図 1において、室外機 1は、熱交換器 2、縦型圧縮機 3、圧縮機室と送風路とを仕切 る防音板 4、風上側プロペラファン 5、風下側プロペラファン 6、ファンモータ 7、ファン モータ 7の回転方向を反転して伝達するメカニズムを有したギアなどを収納する反転 機構 8、オリフィス 9、前面グリル 10、ファンモータ台 11により構成される。風上側プロ ペラファン 5と風下側プロペラファン 6とは、熱交翻 2に送風作用を生じ熱交換促進 用の送風機で 2重反転ファンとして作用する。 In FIG. 1, an outdoor unit 1 includes a heat exchanger 2, a vertical compressor 3, a soundproof plate 4 that partitions the compressor room and the air passage, an upwind propeller fan 5, a downwind propeller fan 6, and a fan Motor 7 and fan The motor 7 includes a reversing mechanism 8 that houses a gear having a mechanism for reversing the rotation direction of the motor 7, an orifice 9, a front grill 10, and a fan motor base 11. The windward propeller fan 5 and the leeward propeller fan 6 generate a blowing action in the heat exchange 2 and act as a double reversing fan in a fan for promoting heat exchange.
[0035] 図 2において、風上側プロペラファン 5の翼 20は翼枚数 2枚力 なり、外周縁を構成 するチップ 21、前縁 22、後縁 23、ハブ 24により構成される。一点鎖線 Bは、風上側 プロペラファン 5の自乗平均半径位置での翼 20の円筒切断線である。そして、プロべ ラファンの翼の自乗平均半径位置での翼弦長 Lと翼の半径方向の代表実長さ bであ る。また、図 3において、風下側プロペラファン 6の翼 25は翼枚数が 2枚力もなり、風 上側プロペラファン 5と同様に、チップ 26、前縁 27、後縁 28、ハブ 29により構成され る。一点鎖線 Bは、風下側プロペラファン 6の自乗平均半径位置での翼 20の円筒切 In FIG. 2, the blade 20 of the windward propeller fan 5 has a force of two blades, and is composed of a tip 21, a leading edge 22, a trailing edge 23, and a hub 24 that constitute the outer peripheral edge. An alternate long and short dash line B is a cylindrical cutting line of the blade 20 at the root mean square radius position of the windward propeller fan 5. Then, the chord length L at the mean square radial position of the blade of the prober fan and the representative actual length b in the radial direction of the blade. In FIG. 3, the wing 25 of the leeward propeller fan 6 has two blades and is composed of the tip 26, the leading edge 27, the trailing edge 28, and the hub 29 like the leeward propeller fan 5. The alternate long and short dash line B indicates the cylindrical cutting of the blade 20 at the mean square radius position of the leeward propeller fan 6.
2 2
断線である。空気の流動は、それぞれの前縁 22, 27から流入し、後縁 23, 28から流 出するのを基本としている。前縁 22, 27は回転方向に前進 (前傾)している。 Disconnection. The flow of air is based on the fact that it flows in from the leading edges 22 and 27 and flows out from the trailing edges 23 and 28, respectively. The leading edges 22, 27 are moving forward (tilting forward) in the direction of rotation.
[0036] 風上側プロペラファン 5と風下側プロペラファン 6とは、各々の翼 20, 25の形状が弦 形状の湾曲方向が逆であり、 3次元座標系では各々同一軸心方向から見てほぼ線 対称に設計されて形成されたものである。言い換えれば、 2個のプロペラファン 5, 6 のそれぞれの形状は、平面形状は反転したときに同一又は相似形であり、翼の湾曲 はお互い反対方向に回転したときに気流方向が同一になるものである。これによつて 、形状として変更するのはパブだけであるとともに、 2重反転ファンとしての性能を発 揮させるための設計が容易となる。ちなみに、 2個のプロペラファンの回転数を変える 場合には、風上側プロペラファン 5より風下側プロペラファン 6の方が回転数を低く設 定することが多い。
[0037] なお、翼の枚数は、本実施の形態 1では 2枚としているが、特に限定するものではな い。また、図 1〜3に示すように、本実施の形態 1においては、前縁 22, 27を螺旋曲 線で構成し、風下側プロペラファン 6を風上側プロペラファン 5より小径としている。し 力しそれに限るものではない。また、前縁 22, 27を直線状として 3角状の翼(3角翼) を直線状前縁に密着して外周側に同一半径になるように取り付けた形状で構成して も良い。 [0036] In the windward propeller fan 5 and the leeward propeller fan 6, the shape of each of the blades 20 and 25 is reverse to the chordal shape, and in the three-dimensional coordinate system, each is viewed from the same axial direction. It is designed and formed symmetrically. In other words, the shape of each of the two propeller fans 5 and 6 is the same or similar when the plane shape is reversed, and the blades have the same airflow direction when rotated in opposite directions. It is. As a result, only the pub is changed as the shape, and the design for exhibiting the performance as the double reversing fan becomes easy. Incidentally, when changing the rotation speed of the two propeller fans, the leeward propeller fan 6 is often set to a lower rotation speed than the upwind propeller fan 5. [0037] The number of blades is two in Embodiment 1, but is not particularly limited. As shown in FIGS. 1 to 3, in the first embodiment, the leading edges 22 and 27 are formed by a spiral curve, and the leeward propeller fan 6 has a smaller diameter than the leeward propeller fan 5. However, it is not limited to that. Alternatively, the front edges 22 and 27 may be straight, and a triangular wing (triangular wing) may be attached in close contact with the straight front edge so as to have the same radius on the outer periphery.
[0038] また、各々のプロペラファンの外周側弦長がハブ側弦長より長く構成することにより 、翼端での翼面積を大きく確保することで空力負荷を充分に吸収して仕事を行 、、 各々のプロペラファン自体のファン効率向上と低騒音化を達成することになる。更に 、アスペクト比 bZL≤l. 1に設定すると、図 4に騒音 41dBあたりの風量特性を示す ように、同一騒音当たりの風量を多く出すことができる。 [0038] Also, by configuring the outer chord length of each propeller fan to be longer than the hub chord length, it is possible to sufficiently absorb the aerodynamic load by performing a work by ensuring a large blade area at the blade tip, The fan efficiency of each propeller fan itself will be improved and the noise will be reduced. Furthermore, if the aspect ratio is set to bZL≤l. 1, it is possible to increase the air volume per the same noise, as shown in Fig. 4.
[0039] 室外機 1の構成としては、圧縮機 3、熱交 2を備え、熱交換促進用のファンとし て反回転する 2個の風上側プロペラファン 5と風下側プロペラファン 6とを設け、風上 側プロペラファン 5の上流側で風上側プロペラファン 5を回転させるためのファンモー タ台 11に支持された 1個のファンモータ 7と、風上側プロペラファン 5の下流側でファ ンモータ 7の同軸上に回転方向を反回転させる反転機構 8を備え、反転機構 8の下 流側にファンモータ 7の同軸上に反回転する風下側プロペラファン 6を備えている。 [0039] The configuration of the outdoor unit 1 includes a compressor 3, a heat exchanger 2, and two windward propeller fans 5 and a leeward propeller fan 6 that counter-rotate as fans for promoting heat exchange. One fan motor 7 supported by the fan motor base 11 for rotating the windward side propeller fan 5 on the upstream side of the windward side propeller fan 5 and the fan motor 7 coaxially on the downstream side of the windward side propeller fan 5 A reversing mechanism 8 that counter-rotates the rotation direction is provided on the upper side, and a leeward propeller fan 6 that rotates counterclockwise on the same axis as the fan motor 7 is provided on the downstream side of the reversing mechanism 8.
[0040] このように並べた構成によって、熱交換器 2より少しでも遠くに 2個のプロペラファン 5, 6を配置して、熱交 2と風上側プロペラファン 5との間により大きな空間を構成 することにより、熱交 2の風速分布を均一にして、より熱交換促進を図ることがで きる。特に、熱交 2が図 1に示す U字形状であったり、図示しない L字形状であつ たりする時には、風速分布が悪くなりやすいのでより効果的である。また、熱交 2 と風上側プロペラファン 5との干渉による風切り音も防ぐことができる。さらに、風下側 プロペラファン 6の下流にファンモータ 7やファンモータ台 11が存在しないので、通風 抵抗を少なくして低騒音化を図ることができる。 [0040] With this arrangement, two propeller fans 5 and 6 are arranged as far as possible from the heat exchanger 2 to form a larger space between the heat exchanger 2 and the windward propeller fan 5. By doing so, the air velocity distribution of heat exchange 2 can be made uniform, and heat exchange can be further promoted. In particular, when the heat exchange 2 is U-shaped as shown in FIG. 1 or L-shaped (not shown), it is more effective because the wind speed distribution tends to deteriorate. Further, wind noise caused by interference between the heat exchanger 2 and the windward propeller fan 5 can be prevented. Furthermore, since the fan motor 7 and the fan motor base 11 do not exist downstream of the leeward propeller fan 6, it is possible to reduce the ventilation resistance and reduce noise.
[0041] そして、特に暖房運転において、室外機の熱交換器に空気中の水分が凝縮して露 となって付着し、それがさらに低温になると露が氷や霜となって目詰まりするような状 態となり、それが熱交換器を通過する気流を妨げるような状況になっても、風量の低
下を抑制し、騒音の増力 tlも抑制するような、送風機の効率が良い空気調和機の室外 機を提供することができる。 [0041] In particular, in heating operation, moisture in the air condenses and adheres to the heat exchanger of the outdoor unit, and dew becomes clogged as ice or frost when the temperature drops further. Even if the situation becomes such that it interferes with the airflow passing through the heat exchanger, the airflow is low. It is possible to provide an outdoor unit of an air conditioner with high efficiency of the blower that suppresses lowering and suppresses noise increase tl.
[0042] なお、反転機構 8を風上側プロペラファン 5のハブ 24の内部、または風下側プロべ ラファン 6のハブ 29の内部、あるいは風上側プロペラファン 5のハブ 24の内部と風下 側プロペラファン 6のハブ 29の両方のハブ 24, 29の内部に収納してもよく、そうすれ ば室外機 1をより省スペース化できる。同時に、ファンモータ 7をアウターロータ式のフ アンモータとして、風上側プロペラファン 5のハブ 24の内部、または風下側プロペラフ アン 6のハブ 29の内部に収納するようにしても良ぐ室外機 1をさらに省スペース化す ることができる。反転機構 8とファンモータ 7については、ファンのハブ内部の利用の 仕方として ヽろ ヽろな組み合わせが考えられ、それらを有効に活用することで省スぺ 一ス化を図ることができる。 [0042] The reversing mechanism 8 is installed inside the hub 24 of the leeward propeller fan 5, or inside the hub 29 of the leeward propeller fan 6, or inside the hub 24 of the leeward propeller fan 5, and the leeward propeller fan 6 The hub 29 may be housed in both the hubs 24 and 29, so that the outdoor unit 1 can be further saved in space. At the same time, the fan motor 7 is an outer rotor type fan motor, and the outdoor unit 1 that can be housed in the hub 24 of the leeward propeller fan 5 or in the hub 29 of the leeward propeller fan 6 is further added. Space can be saved. The reversing mechanism 8 and the fan motor 7 can be used in a variety of combinations within the hub of the fan, and space can be saved by making effective use of them.
[0043] 上記構成によって、風上側プロペラファン 5後流の回転エネルギー(回転流に伴う 無駄となるエネルギー)を反回転する風下側プロペラファン 6で回収し、更に風下側 プロペラファン 6後流の回転流をほぼ零とする事ができるので、空気調和機室外機 1 にサイズの大き 、プロペラファン 1個のみ使用する場合に比較して、静圧と風量を増 カロさせる事が出来て、動作点静圧効率を向上させる事が可能となる。その結果ファン モータ 7の入力を低減できて空気調和機の COPや期間消費電力を低減する事が可 能となる。ファンモータ 7は 1個である力 風上側プロペラファン 5後流の反転機構 8に 内蔵されたギア形状などの組み合わせにより、ファンモータ 7の軸の回転方向を風下 側プロペラファン 6に反回転方向として伝達する事が可能であり、重量があるファンモ ータ 7がーつなので空気調和機の室外機の構成部品が少なぐ低コストで軽量に生 産できる。前縁 22と 27は回転方向が前進しているので、翼端の負荷を高くできて翼 端渦を早く強く生成させて、そして、早くブレークダウンさせることができ、後方翼に干 渉せず、ファン騒音やファン効率の性能を向上することが可能となる。 [0043] With the above configuration, the rotational energy of the leeward propeller fan 5 is recovered by the counter-rotating leeward propeller fan 6 and further rotated by the leeward propeller fan 6 Since the flow can be made almost zero, the static pressure and air volume can be increased compared to the case where the outdoor unit 1 is larger in size and only one propeller fan is used. It is possible to improve the static pressure efficiency. As a result, the input to the fan motor 7 can be reduced, and the COP and period power consumption of the air conditioner can be reduced. Fan motor 7 has a single force Windward propeller fan 5 Backward reversing mechanism 8 Combined with the gear shape and other features, the rotation direction of the shaft of fan motor 7 is set to be the counter-rotating direction to leeward propeller fan 6 Since there are only seven fan motors that can be transmitted and that are heavy, the number of components of the outdoor unit of the air conditioner can be reduced and the weight can be reduced. Since the leading edges 22 and 27 are moving forward, the tip load can be increased, the tip vortex can be generated quickly and strongly, and it can break down quickly without interfering with the rear wing. It becomes possible to improve the performance of fan noise and fan efficiency.
[0044] 更に図 5を用いて、性能を詳しく説明する。図 5は、各プロペラファンの自乗平均半 径位置の円筒切断面の展開翼列と速度三角形を示した性能図である。翼 20の展開 翼列(図 2で B円筒で切断し展開した翼列)に、気流が絶対速度 で流入する。 U が回転速度、 Wが相対速度である。翼 25の展開翼列に気流が絶対速度 Cで流入
する。 Uが回転速度 (U =U )、 Wが出口の相対速度である。絶対速度 CのメリデFurther, the performance will be described in detail with reference to FIG. Fig. 5 is a performance diagram showing the developed blade row and velocity triangle of the cylindrical cut surface at the mean square radius position of each propeller fan. Deployment of blade 20 Airflow flows at an absolute velocity into the blade row (the blade row that was cut and deployed with the B cylinder in Fig. 2). U is the rotation speed and W is the relative speed. Airflow flows at an absolute speed C into the blade cascade of blade 25 To do. U is the rotational speed (U = U) and W is the relative speed of the exit. Absolute speed C Melide
2 1 2 2 2 イアン流速が C 、周方向成分が V である。展開翼列 25の出口の絶対速度が C m2 Θ 3、 回転速度が U (Uく U )、相対速度が Wであり、メリディアン流速が C である。展 2 1 2 2 2 Ian flow velocity is C and circumferential component is V. The absolute velocity at the outlet of the deployment blade row 25 is C m2 Θ 3, the rotational velocity is U (U く U), the relative velocity is W, and the Meridian flow velocity is C. Exhibition
3 3 2 3 m3 3 3 2 3 m3
開翼列 25にて周方向成分 V が完全回収されて、動圧 Pdは静圧に変換されるのでト The circumferential component V is completely recovered in the open blade row 25, and the dynamic pressure Pd is converted to static pressure.
Θ Θ
一タル静圧は増加する。 One tart static pressure increases.
[0045] Pd=0. 5 * p *V 2 ( ρは、密度で単位は、 kg/sec2 -m4) [0045] Pd = 0.5 * p * V 2 (ρ is density and unit is kg / sec 2 -m 4 )
Θ Θ
この C 1S 展開翼列 25 (図 5で B円筒で切断し展開した翼列)にファンモータ 7に m2 2 In this C 1S deployment blade row 25 (blade row cut by B cylinder in Fig. 5), fan motor 7 has m2 2
より角トルクを与えられて、増速されて絶対速度 Cとなり、回転流成分が非常に少な With more angular torque, the speed is increased to absolute speed C, and the rotational flow component is very small.
3 Three
い。それで、メリディアン流速 c は増加して、 Yes. So the Meridian flow velocity c increases and
m3 c m2 <c と成るので、メリディアン流速 m3 Since m3 c m2 <c, Meridian flow velocity m3
の積算である風量 q (m3Zmin)は増加する事になる。また、ここで相対速度 W >W The air volume q (m 3 Zmin), which is the integration of, increases. Also, here relative speed W> W
1 3 の関係を保っている。ここで、以上の各流速の単位は (mZsec)である。展開翼列 25 の後流 Cの回転流は殆ど零に近い。 1 3 is maintained. Here, the unit of each flow velocity is (mZsec). The rotational flow of the wake C in the deployment blade row 25 is almost zero.
3 Three
[0046] その結果、後述する図 6の様に、反回転する 2個のプロペラファン(2重反転ファン) の静圧—風量特性は、ただ 1個の単段のプロペラファンを用いる場合より増加する事 になる。ここでは仮に、風上側及び風下側プロペラファンの回転数は 550rpmに設定 し、ファン径は Φ 415mmである。これは、反回転する 2個のプロペラファン(2重反転 ファン)のファン静圧効率が向上する事を意味している。これにより、空気調和機の C OPや期間消費電力を低減する事が可能となる。 As a result, as shown in FIG. 6 to be described later, the static pressure-air flow characteristics of two counter-rotating propeller fans (double counter-rotating fan) are increased compared to the case of using only one single-stage propeller fan. Will do. Here, suppose that the rotational speed of the windward and leeward propeller fans is set to 550 rpm, and the fan diameter is Φ415 mm. This means that the fan static pressure efficiency of two counter-rotating propeller fans (double reversing fans) is improved. This makes it possible to reduce the COP and period power consumption of the air conditioner.
[0047] 図 6は、本発明の室外機の 2重反転ファンの静圧一風量特性図で、反回転する 2個 のプロペラファンからなる 2重反転ファンの特性曲線と、 2重反転ファンの内の 1個(単 段)のプロペラファンの特性曲線とを比較して示す。空気調和機の室外機 1に、本発 明の 2重反転ファンと同等の奥行きを有するサイズの大きいプロペラファン (ファン径 Φ415πιπι)を 1個のみ使う場合に比較して、風上側及び風下側プロペラファン 5, 6 ( 2重反転ファン、ファン径 Φ415πιπι)を使用する場合に、動作点静圧効率は比率で 18%向上する事が実験データより判明した。 [0047] Fig. 6 is a characteristic diagram of the static pressure and air flow rate of the double reversing fan of the outdoor unit of the present invention. The characteristic curve of the double reversing fan consisting of two counter-rotating propeller fans and the The characteristic curve of one (single stage) propeller fan is compared. Compared to the case where only one large propeller fan (fan diameter Φ415πιπι) with the same depth as the double reversing fan of the present invention is used for the outdoor unit 1 of the air conditioner, the windward and leeward propellers are used. Experimental data showed that when using fans 5 and 6 (double reversing fan, fan diameter Φ415πιπι), the operating point static pressure efficiency was improved by 18%.
[0048] そして、風下側プロペラファン 6の直径を、風上側プロペラファン 5の直径より小さく してもよい。その方が、風上側プロペラファン 5後流の回転流のエネルギーを無駄なく 回収できる。また、風下側プロペラファン 6の直径を、風上側プロペラファン 5の直径よ
り大きくしても風下側プロペラファン 6の作動回転数を更により小さく設定すれば、風 上側プロペラファン 5後流の回転流のエネルギーを無駄なく回収し、メリディアン流速 はじ >C となり増速できて風量が増える。 [0048] The diameter of the leeward propeller fan 6 may be smaller than the diameter of the leeward propeller fan 5. In this way, the energy of the rotational flow behind the windward propeller fan 5 can be recovered without waste. Also, the diameter of the leeward propeller fan 6 is equal to the diameter of the leeward propeller fan 5. If the operating speed of the leeward propeller fan 6 is set to be even smaller, the energy of the rotatory flow of the leeward propeller fan 5 can be recovered without waste, and the meridian flow rate can be increased to> C. The air volume increases.
[0049] また、風上側及び風下側プロペラファン 5, 6の外周縁のチップ 21, 26側弦長がハ ブ 24, 29側弦長より大きいので(但し、少なくともチップ 21, 26側弦長がハブ 24, 29 側弦長と同じ長さまでである)、翼端の負荷を強め、翼端渦を早く強く生成させて、そ して、早くブレークダウンさせることができ、後方翼に干渉せず、ファン騒音やファン効 率の性能を向上することが可能となる。 [0049] In addition, since the chord lengths of the tips 21 and 26 on the outer periphery of the windward and leeward propeller fans 5 and 6 are larger than the chord lengths of the hubs 24 and 29 (however, at least the chord lengths of the tips 21 and 26 are Hub 24, 29 up to the same length as the side chord length), the wing tip load is increased, the wing tip vortex is generated quickly and strongly, and it can break down quickly without interfering with the rear wing. As a result, fan noise and fan efficiency can be improved.
[0050] 更に、図には示していないが、前縁 22, 27は回転方向に前進している力 他の場 合として風上下側プロペラファン 5, 6が線対称で、前縁 22, 27が回転方向に後進し ていても 2重反転ファンの効果を発揮する事ができる。また、風上下側プロペラファン 5, 6が少なくとも線対称でなぐ更に図 5に示したような回転翼列の方向関係 (翼 20と 25の湾曲方向が逆)を保ってさえいれば、前縁 22, 27のどちらかが回転方向に前進 と後進の組み合わせでも良ぐこれらの場合でも 2重反転ファンの効果を発揮する事 ができる。また、翼の断面形状としては、薄翼又は翼型形状をした厚翼のいずれでも 良いが、厚翼であれば流れの境界層制御により剥離を低減でき、より低騒音を実現 できる。 [0050] Further, although not shown in the drawing, the leading edges 22, 27 are the force moving forward in the rotational direction. In other cases, the up-and-down propeller fans 5, 6 are axisymmetric, and the leading edges 22, 27 The effect of the double reversing fan can be exerted even when is moving backward in the rotation direction. As long as the wind-up / down-side propeller fans 5 and 6 are at least line-symmetric and the directional relationship of the rotating blade row as shown in Fig. 5 (the bending direction of the blades 20 and 25 is reversed), the leading edge Even if either 22 or 27 can be a combination of forward and reverse in the rotational direction, the effect of the double reversing fan can be exhibited. In addition, the cross-sectional shape of the blade may be either a thin blade or a thick blade having an airfoil shape. However, if the blade is thick, separation can be reduced by controlling the boundary layer of the flow, and lower noise can be realized.
[0051] (実施の形態 2) [0051] (Embodiment 2)
図 7は、本発明の第 2の実施の形態における空気調和機の室外機の横断面図であ る。図 7において、室外機 1は、熱交換器 2、縦型圧縮機 3、圧縮機室と送風路とを仕 切る防音板 4、風上側プロペラファン 5、風下側プロペラファン 6、風上側プロペラファ ン 5を駆動するファンモータ 7a、風下側プロペラファン 6を駆動するファンモータ 7b、 オリフィス 9、前面グリル 10、およびファンモータ台 11a, l ibにより構成される。風上 側プロペラファン 5と風下側プロペラファン 6は、同軸上で互いに半回転して熱交換 器 2に送風作用を生じ熱交換促進用の送風機 (2重反転ファン)として作用する。 2個 のファンモータ 7a, 7bはアウターロータ式ファンモータであり、風上側プロペラファン 5,風下側プロペラファン 6それぞれのハブ内部に埋め込まれ、ファンと一体に構成さ れている。
[0052] これらは、風上側から順番に熱交^^ 2、アウターロータ式ファンモータ 7aを内臓し た風上側プロペラファン 5、もう一つのアウターロータ式ファンモータ 7bを内蔵した風 下側プロペラファン 6、前面グリル 10となるように構成するとともに、風上側プロペラフ アン 5と風下側プロペラファン 6は、各々の翼形状が弦形状の湾曲方向が逆であり、 3 次元座標系では同一軸心方向から見てほぼ線対称に形成され、翼枚数が 2枚から なるものである。 FIG. 7 is a cross-sectional view of an outdoor unit of an air conditioner according to the second embodiment of the present invention. In FIG. 7, the outdoor unit 1 includes a heat exchanger 2, a vertical compressor 3, a soundproof plate 4 that cuts the compressor room and the air passage, an upwind propeller fan 5, a downwind propeller fan 6, and an upwind propeller fan. The fan motor 7a that drives the fan 5, the fan motor 7b that drives the leeward propeller fan 6, the orifice 9, the front grill 10, and the fan motor bases 11a and l ib. The windward propeller fan 5 and the leeward propeller fan 6 rotate on the same axis half of each other to produce a blowing action in the heat exchanger 2 and act as a heat exchange promoting blower (double reversing fan). The two fan motors 7a and 7b are outer rotor type fan motors, which are embedded in the respective hubs of the windward propeller fan 5 and the leeward propeller fan 6 and are configured integrally with the fan. [0052] These are, in order from the windward side ^^ 2, the windward propeller fan 5 with the outer rotor fan motor 7a built in, and the leeward propeller fan with the other outer rotor fan motor 7b built-in. 6. The front grille 10 and the leeward propeller fan 5 and the leeward propeller fan 6 have a chord-shaped curved direction opposite to each other. As seen from the figure, it is almost line-symmetric and consists of two blades.
[0053] 上記構成によって、風上側プロペラファン 5後流の回転エネルギー(回転流に伴う 無駄となるエネルギー)を反回転する風下側プロペラファン 6で回収し、更に風下側 プロペラファン 6後流の回転流をほぼ零とする事ができるので、空気調和機の室外機 1にサイズの大き 、プロペラファン 1個のみ使用する場合に比較して、静圧と風量を 増加させる事が出来て、動作点静圧効率を向上させる事が可能となる。その結果ファ ンモータ 7a, 7bの入力を低減できて空気調和機の COPや期間消費電力を低減する 事が可能となる。更に、 2個のファンモータ 7a, 7bを使用すると言っても、必要風量と 静圧は、空気調和機の室外機 1にサイズの大きいプロペラファン 1個のみ使用する場 合と同じ設計であるし、 2個の個々のプロペラファン 5, 6 (2重反転ファンとも言われる )にかかる翼負荷を低くできるので、結果的に 2個のファンモータ 7a, 7b入力を総合 しても、サイズの大きいプロペラファン 1個のみ使用する場合の 1個のファンモータの み使用する場合より低入力化できるものである。 [0053] With the above configuration, the rotational energy of the leeward propeller fan 5 wake (wasteful energy associated with the rotational flow) is recovered by the counter-rotating leeward propeller fan 6 and further rotated by the leeward propeller fan 6 wake. Since the flow can be reduced to almost zero, the static pressure and airflow can be increased compared to the case of using only one propeller fan and the size of the outdoor unit 1 of the air conditioner. It is possible to improve the static pressure efficiency. As a result, the input to the fan motors 7a and 7b can be reduced, and the COP and period power consumption of the air conditioner can be reduced. Furthermore, even if two fan motors 7a and 7b are used, the required air volume and static pressure are the same design as when only one large propeller fan is used in the outdoor unit 1 of the air conditioner. The blade load on two individual propeller fans 5 and 6 (also called double reversing fans) can be reduced, and as a result, even if the two fan motors 7a and 7b inputs are combined, the size is large. When only one propeller fan is used, the input can be made lower than when only one fan motor is used.
[0054] 更に、 2個のファンモータ 7a, 7bはアウターロータ式で互いに反回転し、 2個のプロ ペラファン 5, 6のハブ部内部に埋め込まれているので、プロペラファン 5, 6とアウター ロータ式ファンモータ 7a, 7bがー体ィ匕されているので、空気調和機の室外機の省ス ペースも実現できる。ここで、ファンモータ 7a, 7bは、アウターロータ式ファンモータで なぐ一般的な、ファンモータシャフトを回転させるファンモータを、風上下側プロペラ ファンの同軸上外部に設置しても、勿論、スペースをとるだけなので、特に支障がな ければかまわない。更に、風上側からアウターロータ式ファンモータ 7aを内臓した風 上側プロペラファン 5、もう一つのアウターロータ式ファンモータ 7bを内臓した風下側 プロペラファン 6の順序で配置する構成によって、熱交換器 2より最も遠くに 2個のプ 口ペラファン 5, 6を配置して熱交^^ 2と風上側プロペラファン 5との間に少しでも大
きな空間を構成し、熱交換器 2の風速分布を均一にして、より熱交換促進を図ること ができる。また、熱交換器 2と風上側プロペラファン 5との干渉による風切り音も防ぐこ とができる。さらに、風下側プロペラファン 6の下流にファンモータやファンモータ台が 存在しな!、ので、通風抵抗を少なくして低騒音化を図ることができる。 [0054] Furthermore, the two fan motors 7a and 7b are outer rotor types and are counter-rotating to each other, and are embedded in the hub portion of the two propeller fans 5 and 6, so that the propeller fans 5 and 6 and the outer rotor Since the fan motors 7a and 7b are combined, it is possible to save space for the outdoor unit of the air conditioner. Here, the fan motors 7a and 7b are not limited to the outer rotor type fan motor, and a fan motor that rotates the fan motor shaft can be installed on the same axis outside the up / down propeller fan. As long as there is no problem, it does not matter. Furthermore, the heat exchanger 2 has a configuration in which the windward propeller fan 5 incorporating the outer rotor fan motor 7a from the windward side and the leeward propeller fan 6 incorporating the other outer rotor fan motor 7b are arranged in this order. Arrange the two farthest propeller fans 5 and 6 at the farthest distance between the heat exchanger ^^ 2 and the windward propeller fan 5 Space can be formed, the wind speed distribution of the heat exchanger 2 can be made uniform, and heat exchange can be further promoted. Further, wind noise caused by interference between the heat exchanger 2 and the windward propeller fan 5 can be prevented. Furthermore, since there is no fan motor or fan motor base downstream of the leeward propeller fan 6, it is possible to reduce the ventilation resistance and reduce noise.
[0055] また、個々のプロペラファン 5, 6の外周側 21, 26弦長がハブ 24, 29側弦長より大 きいので、翼端の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレークダ ゥンさせることができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向上す ることが可能となる。 [0055] Also, since the outer and outer chord lengths of the individual propeller fans 5 and 6 are larger than the chord lengths of the hub 24 and 29, the wing tip load is increased and the wing tip vortex is generated quickly and strongly. And it is possible to break down quickly and to improve fan noise and fan efficiency without interfering with the rear wing.
[0056] (実施の形態 3) [Embodiment 3]
本発明の第三の実施の形態を、図 1と図 7を用いて説明する。符号と構成は、実施 の形態 1, 2にて説明しているので略する。 A third embodiment of the present invention will be described with reference to FIGS. The reference numerals and configuration are omitted because they are described in the first and second embodiments.
[0057] 同軸上の反回転する 2個のプロペラファン 5, 6 (2重反転ファン)の回転数を変えて 設定し、熱交換促進用のファンとして用いる 2個のプロペラファン 5, 6 (2重反転ファ ン)を備えた空気調和機の室外機を提供してなるものである。例えば、実施の形態 1 においては、反転機構である反転機構 8のギア比によって風上側プロペラファン 5の 回転数と、風下側プロペラファン 6の回転数の比率を設定することができる。また、実 施の形態 2においては、それぞれのプロペラファン 5, 6にファンモータ 7a, 7bが配設 されているので、それぞれの回転数は自由に設定することができる。 [0057] Two propeller fans 5 and 6 (2 counter rotating fans) on the same axis are set by changing the rotation speed of the two propeller fans 5 and 6 (double reversing fans). The present invention provides an outdoor unit for an air conditioner equipped with a double reversing fan. For example, in the first embodiment, the ratio of the rotational speed of the windward propeller fan 5 and the rotational speed of the leeward propeller fan 6 can be set by the gear ratio of the reversing mechanism 8 that is a reversing mechanism. In the second embodiment, since the propeller fans 5 and 6 are provided with the fan motors 7a and 7b, the respective rotational speeds can be freely set.
[0058] 上記の構成によって、反回転する 2個のプロペラファン 5, 6の回転数を変えることが できるので、個々のプロペラファン 5, 6の速度三角形が異なり、個々のプロペラファン 5, 6の翼列 20, 25が仕事をする時間のタイミングがずれるので、それぞれの翼列 20 , 25が仕事をする時間軸をとつても干渉することがなぐ高調による離散的騒音のピ ークを発生する事も無ぐ低騒音にもできる。そして、個々のプロペラファンファン 5, 6 の外周側 21, 26弦長がハブ 24, 29側弦長よりしておけば、翼端の負荷を強めて翼 端渦を早く強く生成させて、そして、早くブレークダウンさせることができ、後方翼に干 渉せず、ファン騒音やファン効率の性能を向上することが可能となる。 [0058] With the above configuration, the rotation speeds of the two propeller fans 5 and 6 that are counter-rotating can be changed, so that the speed triangles of the individual propeller fans 5 and 6 are different, and the individual propeller fans 5 and 6 have different speed triangles. Since the timing of the blades 20 and 25 is shifted, the peak of discrete noise is generated due to harmonics that do not interfere with each other even if the blades 20 and 25 work along the time axis. It can also be done with low noise. And if the outer peripheral side 21, 26 string length of each propeller fan fan 5, 6 is longer than the hub 24, 29 side chord length, the blade tip load is strengthened and the blade tip vortex is generated quickly and strongly, and Therefore, it is possible to break down quickly and improve fan noise and fan efficiency performance without interfering with the rear wing.
[0059] (実施の形態 4) [Embodiment 4]
図 8は、本発明の第 4の実施の形態における室外機の 2重反転ファンのプロペラフ
アンの子午面図である。図 9は、図 8に示すプロペラファンの半径方向断面図で、上 側を示す。個々の風上下側プロペラファンは、符号 30として統一する。 FIG. 8 shows the propeller of the counter rotating fan of the outdoor unit according to the fourth embodiment of the present invention. It is Ann's meridian view. FIG. 9 is a radial cross-sectional view of the propeller fan shown in FIG. 8, showing the upper side. Individual up-and-down propeller fans are standardized as 30.
[0060] 図 8と図 9において、プロペラファン 30は 2枚の翼 31からなり、前縁 32、後縁 33、ハ ブ 34、チップ 35により構成される。同軸上の反回転する 2個のプロペラファン 30 (2重 反転ファン)が子午面(回転投影図)上の前縁 32が風上側に対し凹状であり、個々の プロペラファン 30は気流方向から見て線対称に形成されており、半径方向断面で翼 31断面形状が風上側に対し凹状に形成されている。そして、これらの 2個のプロペラ ファン 30を備えた空気調和機の室外機を提供してなるものである。 8 and 9, the propeller fan 30 includes two blades 31 and includes a leading edge 32, a trailing edge 33, a hub 34, and a tip 35. Two propeller fans 30 (co-rotating fan) that rotate counterclockwise on the same axis have a leading edge 32 on the meridian plane (rotational projection) that is concave with respect to the windward side, and each propeller fan 30 is viewed from the airflow direction. The blade 31 cross-sectional shape is concave with respect to the windward side in the radial cross section. An air conditioner outdoor unit provided with these two propeller fans 30 is provided.
[0061] 上記の構成によって、風上側プロペラファン 30後流の回転エネルギー(回転流に 伴う無駄となるエネルギー)を反回転する風下側プロペラファン 30で回収し、更に風 下側プロペラファン 30後流の回転流をほぼ零とする事ができるので、空気調和機の 室外機 1にサイズの大きいプロペラファン一つのみ使用する場合に比較して、静圧と 風量を増加させる事が出来て、動作点静圧効率を向上させる事が可能となる。更に、 同軸上の反回転する 2個のプロペラファン 30の負圧面から圧力面に向力う洩れなが れを一因として、プロペラファンの負圧面のチップ側付近に発生する翼端渦を、上記 の半径方向断面の翼 31断面形状の風上側に対し凹状部分が、この翼端渦の生成を 促進させて、個々のプロペラファン 30の翼 31の流動状態を最適化できるので、動作 点静圧効率を更に向上させる事ができる。ここで、プロペラファン 30の凹型翼形状は 、どちらか一方のファンに採用しても効果がある力 両方に採用した方が、本効果を より発揮することができる。 [0061] With the above configuration, the rotational energy (waste energy associated with the rotational flow) of the leeward propeller fan 30 is recovered by the counter-rotating leeward propeller fan 30, and further the leeward propeller fan 30 wake Since the rotational flow of the air can be reduced to almost zero, the static pressure and air volume can be increased compared to the case where only one large propeller fan is used in the outdoor unit 1 of the air conditioner. It becomes possible to improve the point static pressure efficiency. In addition, due to leakage from the suction surface to the pressure surface of the two counter-rotating propeller fans 30 on the same axis, the tip vortex generated near the tip side of the suction surface of the propeller fan The above-mentioned concave portion of the radial cross-section blade 31 on the windward side of the cross-sectional shape promotes the generation of the tip vortex and optimizes the flow state of the blade 31 of each propeller fan 30. The pressure efficiency can be further improved. Here, the concave wing shape of the propeller fan 30 can achieve this effect more effectively if it is used for both forces that are effective even if it is used for either one of the fans.
[0062] また、個々のプロペラファン 30の外周側 35弦長がハブ 34側弦長より大きいので、 翼端の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレークダウンさせる ことができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向上することが可 能となる。 [0062] Also, since the outer chord 35 chord length of each propeller fan 30 is longer than the hub 34 chord length, the tip load is increased, the tip vortex is generated quickly and strongly, and the break down is performed quickly. Therefore, fan noise and fan efficiency can be improved without interfering with the rear wing.
[0063] (実施の形態 5) [0063] (Embodiment 5)
図 10は、本発明の第 5の実施の形態における室外機の 2重反転ファンのプロペラ ファンの子午面図である。図 11は、図 10に示すプロペラファンの半径方向断面図で 、上側を示す。個々の風上下側プロペラファンは、符号 36として統一する。
[0064] 図 10と図 11において、プロペラファン 36は、 2枚かの翼 37からなり、前縁 38、後縁 39、ハブ 40、チップ 41により構成される。 C— Cは翼 37の中点線である。同軸上の 反回転する 2個のプロペラファン 36 (2重反転ファン)が子午面(回転投影図)上の前 縁 38が風上側に対し翼 37の中点付近 (C— C)よりチップ 41側は凹状であり、ハブ 4 0側は凸状であり、半径方向断面で翼 37の断面形状がチップ 41側が風上側に対し 凹状であり、ハブ 40側が凸状に形成されている。そして、これらの 2個のプロペラファ ン 36を備えた空気調和機の室外機を提供してなるものである。 FIG. 10 is a meridional view of the propeller fan of the counter rotating fan of the outdoor unit in the fifth embodiment of the present invention. FIG. 11 is a radial sectional view of the propeller fan shown in FIG. Individual up-and-down propeller fans are standardized as 36. In FIG. 10 and FIG. 11, the propeller fan 36 includes two blades 37 and includes a front edge 38, a rear edge 39, a hub 40, and a tip 41. C—C is the midpoint of wing 37. Two propeller fans 36 (double-reversing fan) that rotate counterclockwise on the same axis are the leading edge 38 on the meridian plane (rotational projection). The side of the blade 40 is convex, the side of the hub 40 is convex, and the cross section of the blade 37 in the radial cross section is concave on the tip 41 side with respect to the windward side, and the hub 40 side is convex. An air conditioner outdoor unit provided with these two propeller fans 36 is provided.
[0065] 上記の構成によって、風上側プロペラファン 36後流の回転エネルギー(回転流に 伴う無駄となるエネルギー)を反回転する風下側プロペラファン 36で回収し、更に風 下側プロペラファン 36後流の回転流をほぼ零とする事ができるので、空気調和機の 室外機 1にサイズの大きいプロペラファン一つのみ使用する場合に比較して、静圧と 風量を増加させる事が出来て、動作点静圧効率を向上させる事が可能となる。更に、 同軸上の反回転する 2個のプロペラファン 36の負圧面から圧力面に向力う洩れなが れを一因として、プロペラファン 36の負圧面のチップ側付近に発生する翼端渦を、上 記の半径方向断面の翼 37断面形状のチップ 41側が風上側に対し凹状部分が、こ の翼端渦の生成を促進させる。上記の半径方向断面の翼 36断面形状のハブ 40側 凸状部分がプロペラファン 36の翼 37の外周側から半径方向に流入してくる流れを誘 引するので、翼渦の生成促進と半径方向流の促進により、個々のプロペラファン 36 の翼 37の流動状態を最も最適化できるので、動作点静圧効率を更に向上させる事 ができる。ここで、プロペラファン 36の凹凸形翼形状は、どちらか一方のファンに採用 しても効果があるが、両方に採用した方が、本効果をより発揮することができる。 [0065] With the above configuration, the rotational energy (waste energy associated with the rotational flow) of the leeward propeller fan 36 is recovered by the counter-rotating leeward propeller fan 36, and further the leeward propeller fan 36 wake Since the rotational flow of the air can be made almost zero, the static pressure and air volume can be increased compared to the case where only one large propeller fan is used in the outdoor unit 1 of the air conditioner. It becomes possible to improve the point static pressure efficiency. Furthermore, due to leakage from the suction surface to the pressure surface of the two propeller fans 36 rotating on the same axis, the tip vortex generated near the tip side of the suction surface of the propeller fan 36 The tip of the tip 41 side of the blade 37 in the radial cross-section is concave with respect to the windward side, which promotes the generation of the tip vortex. Blades with the above-mentioned radial cross-section 36 Hub with cross-sectional shape 40 side The convex part attracts the flow flowing radially from the outer peripheral side of the blade 37 of the propeller fan 36. By facilitating the flow, the flow state of the blades 37 of the individual propeller fans 36 can be most optimized, so that the operating point static pressure efficiency can be further improved. Here, the concave and convex wing shape of the propeller fan 36 is effective even if it is used for either one of the fans, but the effect can be exhibited more when it is used for both.
[0066] また、個々のプロペラファン 36の外周側 41弦長がハブ 40側弦長より大きいので、 翼端の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレークダウンさせる ことができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向上することが可 能となる。 [0066] Also, since the outer chord length 41 string length of each propeller fan 36 is larger than the hub chord length of the hub 40, the load on the blade tip is strengthened so that the blade tip vortex is generated quickly and strongly, and the break down is fast. Therefore, fan noise and fan efficiency can be improved without interfering with the rear wing.
[0067] (実施の形態 6) [Embodiment 6]
図 12は、本発明の第 6の実施の形態における室外機の風上側斜流ファンの A方向 平面図、図 13は風下側斜流ファンの A方向平面図、図 14は風上下斜流ファンの子
午面図である。個々の風上下側プロペラファンは、符号 42として統一する。 FIG. 12 is a plan view in the A direction of the upwind mixed flow fan of the outdoor unit according to the sixth embodiment of the present invention, FIG. 13 is a plan view in the A direction of the downwind mixed flow fan, and FIG. Child FIG. Individual wind up and down propeller fans are unified as 42.
[0068] 図 12において、風上側斜流ファン 42は、 2枚の翼 43、回転方向に前進した前縁 4 4、後縁 45、チップ 46、ハブ 47により構成される。図 13において、風下側斜流ファン は、 2枚の翼 49、回転方向に前進した前縁 50、後縁 51、チップ 52、ハブ 53により構 成される。同軸上の反回転する 2個の熱交換促進用のファン力 プロペラファンでなく 斜流ファンであり、各々の翼 43, 49形状が弦形状の湾曲方向が逆であり、 3次元座 標系では同一軸心方向力 見てほぼ線対称に設計され、翼枚数が 2枚からなる斜流 ファン 42, 48 (2重反転ファン)であり、斜流ファン 42, 48のノヽブ 47, 53形状は略円 錐台状に形成されている。そして、この 2個の斜流ファン 42, 48を備えた空気調和機 の室外機を提供してなるものである。ここで、風上側斜流ファン 42は風下側斜流ファ ン 48より、回転速度は速い。前縁 44と 50は回転方向に前進している。この前縁 44, 50は螺旋曲線で構成されている力 後縁 45, 51は直線状で、 3角状の翼(3角翼)を 直線状前縁に密着して外周側に取り付け、そして尚、翼 43, 49の半径を同一になる ように構成しても良い。 In FIG. 12, the upwind mixed flow fan 42 includes two blades 43, a leading edge 44, a trailing edge 45, a tip 46, and a hub 47 that have advanced in the rotational direction. In FIG. 13, the leeward mixed flow fan is composed of two blades 49, a leading edge 50, a trailing edge 51, a tip 52, and a hub 53 that have advanced in the rotational direction. Two counter-rotating fan forces on the same axis are used to promote heat exchange, not a propeller fan, but a mixed-flow fan. Each blade 43, 49 has a chord-shaped curved direction, and the three-dimensional coordinate system The mixed flow fans 42 and 48 (double-reversing fan) are designed to be nearly line-symmetric with respect to the same axial force, and the number of blades 47 and 53 of the mixed flow fans 42 and 48 is It is formed in a substantially frustum shape. The present invention provides an air conditioner outdoor unit equipped with the two mixed flow fans 42 and 48. Here, the windward mixed flow fan 42 rotates faster than the leeward mixed flow fan 48. Leading edges 44 and 50 are advanced in the direction of rotation. This leading edge 44, 50 is a force composed of a spiral curve. The trailing edge 45, 51 is a straight line, and a triangular wing (triangular wing) is attached to the outer circumference side in close contact with the straight leading edge. The radii of the blades 43 and 49 may be configured to be the same.
[0069] 上記の構成によって、風上側斜流ファン 42後流の回転エネルギー(回転流に伴う 無駄となるエネルギー)を反回転する風下側斜流ファン 48で回収し、更に風下側斜 流ファン 48後流の回転流をほぼ零とする事ができるので、空気調和機室外機 1にサ ィズの大き ヽ斜流ファン一つのみ使用する場合に比較して、静圧と風量を増加させ る事が出来て、動作点静圧効率を向上させる事が可能となる。更に、基本的に斜流 ファンはプロペラファンより静圧が高い。空気調和機室外機 1にファン径の大きいファ ンを使用する時に、送風機のファン径と回転数の相似則力も自明な様に、静圧は低 下する。そこで、空気調和機の室外機 1にファン径の大きいファンを投入する時には 、静圧の高い斜流ファンを用いるのが最適な構成となる。それは、動作点静圧効率を 向上させる事につながる。前縁 44と 50は回転方向に前進しているので、翼端の負荷 を高くできて、より強い翼端渦を生成させることができる。翼端渦は早く強く生成させ て、そして、早くブレークダウンさせるのが、後方翼に干渉せず、ファン騒音,ファン効 率の性能が良い。 [0069] With the above configuration, the rotational energy of the wakeward mixed flow fan 42 wake (waste energy associated with the rotational flow) is recovered by the counterclockwise leeward mixed flow fan 48, and further, the leeward mixed flow fan 48 Since the rotational flow of the wake can be made almost zero, the static pressure and the air volume are increased compared to the case where only one fan with mixed flow is used for the air conditioner outdoor unit 1. It is possible to improve the operating point static pressure efficiency. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan. When a fan with a large fan diameter is used for the outdoor unit 1 of the air conditioner, the static pressure decreases, as is obvious from the similarity force between the fan diameter and the rotational speed of the blower. Therefore, when a fan with a large fan diameter is inserted into the outdoor unit 1 of the air conditioner, it is optimal to use a mixed flow fan with a high static pressure. This leads to improved operating point static pressure efficiency. The leading edges 44 and 50 are advanced in the direction of rotation, so the tip load can be increased and a stronger tip vortex can be generated. If the tip vortex is generated quickly and strongly, and it breaks down quickly, it will not interfere with the rear wing, and fan noise and fan efficiency will be good.
[0070] また、個々の斜流ファン 42, 48の外周側 46, 52弦長がハブ 47, 53側弦長より大き
いので (但し、少なくとも外周側 46, 52弦長がハブ 47, 53側弦長と同じ長さまでであ る)、翼端の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレークダウンさ せることができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向上すること が可能となる。 [0070] Also, the outer side 46, 52 chord length of each mixed flow fan 42, 48 is larger than the hub 47, 53 chord length (However, at least the outer 46,52 chord length is the same length as the hub 47,53 chord length), the wing tip load is increased and the wing tip vortex is generated quickly and strongly. It is possible to break down, and it is possible to improve fan noise and fan efficiency without interfering with the rear wing.
[0071] 更に、図には示していないが、前縁 44, 50は回転方向に前進している力 他の場 合として風上下側斜流ファン 42, 48が点対称性を保ち前縁 44, 50が回転方向に後 進していても 2重反転ファンの効果を発揮する事ができる。また、風上下側斜流ファン 42, 48が少なくとも線対称ではなぐ更に図 5に示したような回転翼列の方向関係( 図 5を転用するなら、翼 20と 25の湾曲方向が逆)を保ってさえいれば、風上下側斜 流ファン 42, 48の前縁 44, 50のどちらかが回転方向に対し前進と後進の組み合わ せでも良ぐこれらの場合でも 2重反転ファンの効果を発揮する事ができる。 [0071] Further, although not shown in the drawing, the leading edges 44 and 50 are forces that advance in the rotational direction. In other cases, the up-and-down mixed-flow fans 42 and 48 maintain point symmetry and the leading edges 44 , 50 can exert the effect of the double reversing fan even if it moves backward in the rotation direction. In addition, the wind-upward and lower-side mixed flow fans 42 and 48 are not at least line-symmetrical, and the directional relationship of the rotating blade row as shown in Fig. 5 (if Fig. 5 is diverted, the bending direction of blades 20 and 25 is reversed) As long as it is maintained, either the front edge 44 or 50 of the up-and-down side mixed flow fan 42 or 48 can be a combination of forward and reverse with respect to the rotation direction. I can do it.
[0072] (実施の形態 7) [Embodiment 7]
本発明の第 7の実施の形態を、図 15と図 16を用いて説明する。図 15は本発明の 2 重反転ファンの個々の斜流ファンの子午面図、図 16は、本発明の 2重反転ファンの 個々の斜流ファンの半径方向断面図である。個々の風上下側プロペラファンは、符 号 60として統一する。 A seventh embodiment of the present invention will be described with reference to FIG. 15 and FIG. FIG. 15 is a meridional view of each counter flow fan of the counter rotating fan of the present invention, and FIG. 16 is a radial sectional view of each counter flow fan of the counter rotating fan of the present invention. Individual wind-upper propeller fans are standardized as symbol 60.
[0073] 図 15において、風上下側斜流ファン 60の翼 61は、前縁 62、後縁 63、チップ 64、 ハブ 65により構成される。 D— Dは翼 61の中点線である。同軸上の反回転する 2個 の熱交換促進用のファンがプロペラファンでなく斜流ファン 60 (2重反転ファン)であ り、同一軸心方向力 見てほぼ対称に設計され翼枚数が 2枚力 なる斜流ファン 60 であり、斜流ファン 60のハブ形状 65は略円錐台状に形成され、斜流ファン 60の子午 面(回転投影図)上の前縁 62が風上側に対し翼の中点 (D— D)付近よりチップ 64側 は凹状であり、ハブ 65側は凸状であり、半径方向断面で翼 61断面形状がチップ 64 側が風上側に対し凹状であり、ハブ 65側が凸状である 2個の斜流ファン 60を備えた 空気調和機を構成している。 In FIG. 15, the blade 61 of the up-and-down side mixed flow fan 60 includes a leading edge 62, a trailing edge 63, a tip 64, and a hub 65. D—D is the midpoint of wing 61. The two counter-rotating fans on the same axis that promote rotation are not propeller fans but mixed-flow fans 60 (double reversing fans). They are designed almost symmetrically with the same axial force and have 2 blades. The mixed flow fan 60 is a mixed flow fan 60, and the hub shape 65 of the mixed flow fan 60 is formed in a substantially truncated cone shape, and the leading edge 62 on the meridian surface (rotational projection) of the mixed flow fan 60 is a blade against the windward side. From the middle point (D-D), the tip 64 side is concave, the hub 65 side is convex, and in the radial cross section, the blade 61 cross section is concave on the tip 64 side with respect to the windward side, and the hub 65 side is It constitutes an air conditioner with two convex fans 60 that are convex.
[0074] 上記の構成によって、風上側斜流ファン 60後流の回転エネルギー(回転流に伴う 無駄となるエネルギー)を反回転する風下側斜流ファン 60で回収し、更に風下側斜 流ファン 60後流の回転流をほぼ零とする事ができるので、空気調和機の室外機 1に
サイズの大き ヽ斜流ファン一つのみ使用する場合に比較して、静圧と風量を増加さ せる事が出来て、動作点静圧効率を向上させる事が可能となる。更に、基本的に斜 流ファンはプロペラファンより静圧が高 、。空気調和機の室外機 1にファン径の大き いファンを使用する時に、送風機のファン径と回転数の相似則から自明な様に、静圧 は低下する。そこで、空気調和機の室外機 1にファン径の大きいファンを投入する時 には、静圧の高い斜流ファンを用いるの力 最適な構成となる。それは、動作点静圧 効率を向上させる事になる。 [0074] With the above-described configuration, the rotational energy of the downstream of the upwind mixed-flow fan 60 (waste energy associated with the rotational flow) is recovered by the counter-rotating leeward mixed flow fan 60, and further, the downwind mixed flow fan 60 Since the rotational flow of the wake can be made almost zero, the outdoor unit 1 of the air conditioner Larger size 静 Static pressure and air volume can be increased compared to the case of using only one mixed flow fan, and the operating point static pressure efficiency can be improved. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan. When a fan with a large fan diameter is used for the outdoor unit 1 of the air conditioner, the static pressure decreases, as is obvious from the similar law of the fan diameter and rotation speed of the blower. Therefore, when a fan with a large fan diameter is inserted into the outdoor unit 1 of the air conditioner, the power of using a mixed flow fan with a high static pressure is optimal. This will improve the operating point static pressure efficiency.
[0075] 更に、同軸上の反回転する 2個の斜流ファン 60の負圧面力 圧力面に向力う洩れ ながれを一因として、斜流ファン 60の負圧面のチップ 64側付近に発生する翼端渦を 、上記の半径方向断面の翼 61断面形状のチップ 64側が風上側に対し凹状部分が、 この翼端渦の生成を促進させる。上記の半径方向断面の翼 61断面形状のハブ 65 側凸状部分が斜流ファン 60の翼の外周側力 半径方向に流入してくる流れを誘引 するので、翼端渦と半径方向流の促進により、個々の斜流ファン 60の翼の流動状態 を最も最適化できるので、動作点静圧効率を更に向上させる事ができる。ここで、斜 流ファン 60の凹凸形翼形状は、どちらか一方のファンに採用しても効果がある力 両 方に採用した方が、本効果をより発揮することができる。 [0075] Further, the suction surface force of the two counter-rotating counter-rotating fans 60 on the same axis is generated near the tip 64 side of the suction surface of the counter-flow fan 60 due to the leakage flowing toward the pressure surface. The tip vortex has a concave portion on the tip 64 side of the wing 61 in the radial cross section with respect to the windward side to promote the generation of the tip vortex. The above-mentioned radial cross-section blade 61 The cross-section of the hub 65 on the side of the cross section attracts the flow force in the radial direction of the blade of the mixed flow fan 60. As a result, the flow state of the blades of each mixed flow fan 60 can be optimized most, and the operating point static pressure efficiency can be further improved. Here, the uneven wing shape of the mixed flow fan 60 can exert this effect more effectively when it is applied to both of the forces that are effective even when applied to either one of the fans.
[0076] また、個々の斜流ファン 60の外周側 64弦長がハブ 65側弦長よりおおき!/、ので、翼 端の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレークダウンさせるこ とができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向上することが可能 となる。 [0076] In addition, the 64 chord length of the outer peripheral side of each mixed flow fan 60 is larger than the chord length of the hub 65! /, So the load on the wing tip is increased and the wing tip vortex is generated quickly and strongly. It is possible to break down and to improve fan noise and fan efficiency without interfering with the rear wing.
[0077] (実施の形態 8) [0077] (Embodiment 8)
本発明の第 8の実施の形態を、図 17と図 18にて説明する。図 17は、本発明の 2重 反転ファンの個々の斜流ファンの子午面図、図 18は本発明の 2重反転ファンの個々 の斜流ファンの半径方向断面図である。ここで、風上下側斜流ファンは、符号 66とし て統一する。 An eighth embodiment of the present invention will be described with reference to FIGS. FIG. 17 is a meridional view of an individual mixed flow fan of the counter rotating fan of the present invention, and FIG. 18 is a radial sectional view of an individual counter flow fan of the counter rotating fan of the present invention. Here, the up-and-down mixed-flow fan is unified as 66.
[0078] 図 17において、風上下斜流ファン 66の翼 67は、前縁 68、後縁 69、チップ 70、ノヽ ブ 71により構成される。同軸上の反回転する 2個の熱交換促進用のファンがプロペラ ファンでなく斜流ファン 66 (2重反転ファン)であり、斜流ファン 66のハブ 71形状は略
円錐台状に形成され、同一軸心方向から見てほぼ線対称に設計され翼枚数が 2枚 力もなる斜流ファン 66であり、斜流ファン 66の子午面(回転投影図)上の前縁 68が 風上側に対し凹状であり、半径方向断面で翼 67の断面形状が風上側に対し凹状で ある 2個の斜流ファン 66を備えた空気調和機の室外機 1を構成してなるものである。 In FIG. 17, the blade 67 of the up-and-down mixed flow fan 66 includes a front edge 68, a rear edge 69, a tip 70, and a knob 71. The two counter-rotating fans on the same axis are not propeller fans but mixed flow fans 66 (double reversing fans). It is a mixed flow fan 66 that is formed in a truncated cone shape and is designed to be nearly line-symmetric when viewed from the same axial direction and has two blades. The leading edge of the mixed flow fan 66 on the meridian plane (rotary projection) An air conditioner outdoor unit 1 having two mixed flow fans 66 in which 68 is concave with respect to the windward side and the cross-sectional shape of the blade 67 is concave with respect to the windward side in the radial cross section It is.
[0079] 上記構成によって、風上側斜流ファン 66後流の回転エネルギー(回転流に伴う無 駄となるエネルギー)を反回転する風下側斜流ファン 66で回収し、更に風下側斜流 ファン 66後流の回転流をほぼ零とする事ができるので、空気調和機の室外機 1にサ ィズの大き ヽ斜流ファン一つのみ使用する場合に比較して、静圧と風量を増加させ る事が出来て、動作点静圧効率を向上させる事が可能となる。更に、基本的に斜流 ファンはプロペラファンより静圧が高 、。空気調和機の室外機 1にファン径の大き 、フ アンを使用する時に、送風機のファン径と回転数の相似則から自明な様に、静圧は 低下する。そこで、空気調和機の室外機 1にファン径の大きいファンを投入する時に は、静圧の高い斜流ファンを用いるのが、最適な構成となる。それは、動作点静圧効 率を向上させる事になる。更に、同軸上の反回転する 2個の斜流ファン 66の負圧面 力 圧力面に向力う洩れながれを一因として、斜流ファン 66の負圧面のチップ側 70 付近に発生する翼端渦を、上記の半径方向断面の翼 67断面形状の風上側に対し 凹状部分が、この翼端渦の生成を促進させて、個々の斜流ファン 66の翼 67の流動 状態を最適化できるので、動作点静圧効率を更に向上させる事ができる。ここで、斜 流ファン 66の凹型翼形状は、どちらか一方のファンに採用しても効果がある力 両方 に採用した方が、本効果をより発揮することができる。 [0079] With the above configuration, the rotational energy (waste energy associated with the rotational flow) of the leeward mixed-flow fan 66 is recovered by the counter-rotating leeward mixed flow fan 66, and further, the leeward mixed flow fan 66 Since the rotational flow of the wake can be made almost zero, the static pressure and the air volume can be increased compared to the case where only a single fan with a large size is used for the outdoor unit 1 of the air conditioner. It is possible to improve the operating point static pressure efficiency. Furthermore, the mixed flow fan basically has a higher static pressure than the propeller fan. When using a fan with a large fan diameter for the outdoor unit 1 of the air conditioner, the static pressure decreases, as is obvious from the similar law of the fan diameter and rotation speed of the blower. Therefore, when a fan with a large fan diameter is inserted into the outdoor unit 1 of the air conditioner, it is optimal to use a mixed flow fan with a high static pressure. This will improve the operating point static pressure efficiency. Furthermore, the suction surface force of the two counter-rotating counter flow fans 66 on the same axis causes the tip vortices generated near the tip side 70 of the suction surface of the mixed flow fan 66 due to leakage leaking toward the pressure surface. Since the concave part of the above-mentioned radial cross section of the blade 67 in the radial cross section promotes the generation of the tip vortex, the flow state of the blade 67 of each mixed flow fan 66 can be optimized. The operating point static pressure efficiency can be further improved. Here, the concave blade shape of the mixed flow fan 66 can achieve this effect more effectively if it is used for both forces that are effective even if it is used for either one of the fans.
[0080] また、個々の斜流ファン 66の外周側 70弦長がハブ 71側弦長より大きいので、翼端 の負荷を強めて翼端渦を早く強く生成させて、そして、早くブレークダウンさせること ができ、後方翼に干渉せず、ファン騒音やファン効率の性能を向上することが可能と なる。 [0080] Since the chord length on the outer peripheral side of each mixed flow fan 66 is larger than the chord length on the hub 71 side, the load at the wing tip is strengthened so that the wing tip vortex is generated quickly and strongly, and the breakdown is quickly performed. Therefore, fan noise and fan efficiency can be improved without interfering with the rear wing.
産業上の利用可能性 Industrial applicability
[0081] 以上のように本発明にかかる、空気調和機の室外機は、風上側プロペラファン後流 の回転エネルギー(回転流に伴う無駄となるエネルギー)を反回転する風下側プロべ ラファンで回収し、更に風下側プロペラファン後流の回転流をほぼ零とする事ができ
るので、空気調和機の室外機にサイズの大きいプロペラファン一つのみ使用する場 合に比較して、静圧と風量を増加させる事が出来て、動作点静圧効率を向上させる 事が可能となる。その結果ファンモータ入力を低減できて空気調和機の COPや期間 消費電力を低減し、あるいは送風抵抗に対しても風量の低下を抑制し、騒音を低減 する事が可能となり、ルームエアコンや店舗用パッケージエアコンなど、各種の空気 調和機に適用できる。 [0081] As described above, the outdoor unit of the air conditioner according to the present invention collects the rotational energy (wasteful energy associated with the rotational flow) downstream of the windward propeller fan with the leeward propeller fan that counter-rotates. Furthermore, the rotational flow behind the leeward propeller fan can be made almost zero. Therefore, compared to the case where only one large propeller fan is used for the outdoor unit of the air conditioner, the static pressure and the air volume can be increased, and the operating point static pressure efficiency can be improved. It becomes. As a result, it is possible to reduce the fan motor input and reduce the COP and period power consumption of the air conditioner, or suppress the reduction of the air volume against the blowing resistance and reduce the noise. Applicable to various air conditioners such as packaged air conditioners.
また、この 2重反転ファンは、ファンを用いる工業製品である民生用の機器に展開 可能である。即ち、換気扇、扇風機、コンピュータ冷却ファンなどとしても展開可能で ある。
In addition, this double reversing fan can be applied to consumer equipment, which is an industrial product that uses a fan. In other words, it can be deployed as a ventilation fan, fan, computer cooling fan, etc.
Claims
[1] 圧縮機と、熱交換器と、前記熱交換器の熱交換促進用のファンとして 2個のプロペラ ファンとを備え、前記 2個のプロペラファンは同軸上に近接して設け、互いに反対方 向に回転しながら気流方向は同一となるように構成したことを特徴とする空気調和機 の室外機。 [1] A compressor, a heat exchanger, and two propeller fans as fans for promoting heat exchange of the heat exchanger are provided, the two propeller fans being provided close to each other on the same axis and opposite to each other An outdoor unit of an air conditioner characterized in that the airflow direction is the same while rotating in the direction.
[2] 2個のプロペラファンは、各々の翼形状が弦形状の湾曲方向が逆であり、同一軸心 方向から見て線対称に形成したことを特徴とする請求項 1記載の空気調和機の室外 機。 [2] The air conditioner according to claim 1, wherein each of the two propeller fans is formed in a symmetric shape when viewed from the same axial center direction, wherein each blade shape has a chordal shape with opposite bending directions. Outdoor unit.
[3] 1個のファンモータと、前記ファンモータの回転方向を反転して伝達する反転機構と をプロペラファンと同軸上に備え、 2個のプロペラファンのうち、一方のプロペラファン を前記ファンモータで駆動し、他方のプロペラファンを前記反転機構で駆動するよう にしたことを特徴とする請求項 1又は 2記載の空気調和機の室外機。 [3] One fan motor and a reversing mechanism for reversing and transmitting the rotation direction of the fan motor are provided coaxially with the propeller fan, and one of the two propeller fans is the fan motor. 3. The outdoor unit for an air conditioner according to claim 1, wherein the other propeller fan is driven by the reversing mechanism.
[4] 風上側から順番に熱交換器、ファンモータ、風上側プロペラファン、反転機構、風下 側プロペラファンとなるように配設し、前記風上側プロペラファンを前記ファンモータ で駆動し、前記風下側プロペラファンを前記反転機構で駆動するように構成したこと を特徴とする請求項 3記載の空気調和機の室外機。 [4] The heat exchanger, the fan motor, the windward propeller fan, the reversing mechanism, and the leeward propeller fan are arranged in order from the windward side, the windward propeller fan is driven by the fan motor, and the windward side 4. The outdoor unit for an air conditioner according to claim 3, wherein a side propeller fan is configured to be driven by the reversing mechanism.
[5] 反転機構は、風上側プロペラファンのハブ内部、もしくは風下側プロペラファンのハ ブ内部、あるいは風上側及び風下側プロペラファンの両方のハブ内部に収納したこ とを特徴とする請求項 3又は 4記載の空気調和機の室外機。 [5] The reversing mechanism is housed inside the hub of the windward propeller fan, inside the hub of the leeward propeller fan, or inside the hub of both the windward and leeward propeller fans. Or the outdoor unit of the air conditioner of 4.
[6] 2個のファンモータを 2個のプロペラファンそれぞれに備え、前記 2個のプロペラファ ンをそれぞれに設けた前記ファンモータにより駆動することを特徴とする請求項 1又 は 2記載の空気調和機の室外機。 [6] The air according to claim 1 or 2, wherein two fan motors are provided in each of the two propeller fans, and the two propeller fans are driven by the fan motors provided respectively. Harmonic outdoor unit.
[7] ファンモータをアウターロータ式としたことを特徴とする請求項 3〜6のうち 、ずれか一 項記載の空気調和機の室外機。 [7] The air conditioner outdoor unit according to any one of claims 3 to 6, wherein the fan motor is an outer rotor type.
[8] 同軸上の反回転する 2個のプロペラファンの回転数を変えて設定したことを特徴とす る請求項 1〜7のうちいずれか一項記載の空気調和機の室外機。 [8] The outdoor unit for an air conditioner according to any one of claims 1 to 7, wherein the number of rotations of the two counter-rotating propeller fans on the same axis is changed.
[9] プロペラファンの翼の自乗平均半径位置での翼弦長 Lと翼の半径方向の代表実長さ bとの比であるアスペクト比 bZLが bZL≤l. 1であり、前記プロペラファンの外周側
翼弦長がハブ側翼弦長以上であることを特徴とする請求項 1〜8のうちいずれか一項 記載の空気調和機の室外機。 [9] The aspect ratio bZL, which is the ratio of the chord length L at the mean square radial position of the blade of the propeller fan to the representative actual length b in the radial direction of the blade, is bZL≤l. Outer peripheral side The air conditioner outdoor unit according to any one of claims 1 to 8, wherein the chord length is equal to or greater than the hub chord length.
[10] プロペラファンの子午面上の前縁が風上側に対し凹状であり、半径方向断面で翼断 面形状が風上側に対し凹状であり、前記プロペラファンの外周側弦長がハブ側弦長 以上であることを特徴とする請求項 1〜9のうちいずれか一項記載の空気調和機の室 外機。 [10] The front edge on the meridian surface of the propeller fan is concave with respect to the windward side, the blade cross-sectional shape is concave with respect to the windward side in the radial section, and the outer chord length of the propeller fan is the hub chord The outdoor unit for an air conditioner according to any one of claims 1 to 9, wherein the outdoor unit is not less than a length.
[11] プロペラファンの子午面上の前縁が風上側に対して翼の中点付近よりチップ側は凹 状であるとともにハブ側は凸状であり、半径方向断面で翼の断面形状が、チップ側が 風上側に対し凹状であるとともにハブ側が凸状であり、前記プロペラファンの外周側 翼弦長がハブ側翼弦長以上であることを特徴とする請求項 1〜9のうちいずれか一項 記載の空気調和機の室外機。 [11] The leading edge of the propeller fan on the meridian plane is concave on the tip side and near the midpoint of the blade with respect to the windward side, and the hub side is convex. The tip side is concave with respect to the windward side and the hub side is convex, and the outer peripheral side chord length of the propeller fan is equal to or greater than the hub side chord length. The outdoor unit of the air conditioner described.
[12] 熱交換促進用としてプロペラファンを用いる代わりに、ハブ形状が略円錐台形状に形 成された斜流ファンを用いたことを特徴とする請求項 1〜: L 1のうちいずれか一項記載 の空気調和機の室外機。
[12] The mixed flow fan according to any one of claims 1 to 1, characterized in that, instead of using a propeller fan for heat exchange promotion, a mixed flow fan having a substantially circular truncated cone shape is used. The outdoor unit of the air conditioner described in the paragraph.
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- 2007-02-22 JP JP2007041900A patent/JP5003198B2/en not_active Expired - Fee Related
- 2007-06-18 CN CN2007800007475A patent/CN101331362B/en not_active Expired - Fee Related
- 2007-06-18 WO PCT/JP2007/062211 patent/WO2007148645A1/en active Application Filing
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JPH0942184A (en) * | 1995-07-26 | 1997-02-10 | Hitachi Ltd | Mixed flow type fluid machine |
JPH11294389A (en) * | 1998-04-14 | 1999-10-26 | Matsushita Electric Ind Co Ltd | Mixed flow air blower impeller |
JP2000136798A (en) * | 1998-11-02 | 2000-05-16 | Kajima Corp | Noise reducing method and device of two-stage axial blower |
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Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2010104360A2 (en) | 2009-03-12 | 2010-09-16 | Lg Electronics Inc. | Outdoor unit for air conditioner |
EP2406501A2 (en) * | 2009-03-12 | 2012-01-18 | LG Electronics Inc. | Outdoor unit for air conditioner |
EP2406501A4 (en) * | 2009-03-12 | 2012-10-03 | Lg Electronics Inc | Outdoor unit for air conditioner |
US9416982B2 (en) | 2009-03-12 | 2016-08-16 | Lg Electronics Inc. | Outdoor unit for air conditioner |
EP2354685A3 (en) * | 2010-01-21 | 2012-12-05 | LG Electronics, Inc. | Ventilating device and outdoor unit having the same |
WO2013055036A1 (en) | 2011-10-13 | 2013-04-18 | Lg Electronics Inc. | Air conditioner |
EP2766666A4 (en) * | 2011-10-13 | 2015-07-08 | Lg Electronics Inc | Air conditioner |
US9494358B2 (en) | 2011-10-13 | 2016-11-15 | Lg Electronics Inc. | Air conditioner |
EP3182025A1 (en) * | 2015-12-14 | 2017-06-21 | Lg Electronics Inc. | Orifice for air conditioner |
US10054355B2 (en) | 2015-12-14 | 2018-08-21 | Lg Electronics Inc. | Orifice for air conditioner |
EP3708842A4 (en) * | 2019-01-30 | 2020-09-16 | GD Midea Air-Conditioning Equipment Co., Ltd. | Fan and air conditioner indoor unit having same |
Also Published As
Publication number | Publication date |
---|---|
CN101331362B (en) | 2011-06-22 |
JP5003198B2 (en) | 2012-08-15 |
CN101331362A (en) | 2008-12-24 |
JP2008025983A (en) | 2008-02-07 |
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