JP2017218109A - Vehicular freezer device and freezer vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicular freezer device and a freezer vehicle that are capable of setting temperature in a cargo chamber to a uniform low-temperature state in a relatively short time while avoiding enlargement of the device.SOLUTION: A vehicular freezer device 1 includes: a housing 1a mounted to a cargo chamber 3; an evaporator 13 disposed in the housing 1a to cool air inside the cargo chamber 3; an air duct disposed in the housing 1a, and directed from the evaporator 13 toward the cargo chamber 3; and a fan arranged in the air duct to blow the air cooled by the evaporator 13 into the cargo chamber 3. The fan is a crossflow fan 16, and at a lateral part of the crossflow fan 16, a partition plate 25 is disposed to partition an air duct R1. The partition plate 25 is arranged at a position which is 0.075 to 0.125 times a diameter of the crossflow fan 16 from a reference plane W in a narrowing direction of the air duct R1, using a horizontal plane including an axis O1 of the crossflow fan 16 as the reference plane W.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a vehicle refrigeration apparatus and a refrigeration vehicle.

  Conventionally, a vehicle refrigeration apparatus mounted on a vehicle blows cold air into a cargo compartment using a turbo fan or a propeller fan (see, for example, Patent Document 1). In general, a refrigeration apparatus for a vehicle is installed on a front wall or the like that constitutes a luggage compartment, obliquely behind a roof of a driver seat. The front wall is provided with an inlet for cold air, and cold air from a turbo fan or a propeller fan provided in the vehicle refrigeration apparatus is introduced into the cargo compartment through the inlet. As a result, the luggage in the luggage compartment is cooled.

By the way, a turbofan used in a vehicular refrigeration system is advantageous in that it can easily give strength to its wings, can stably exhibit the performance of the fan itself, and can obtain a relatively large air volume. Have.
Further, the propeller fan used in the vehicle refrigeration apparatus has the advantages that the structure is simple and the price is reasonable, the air volume is relatively large, and the noise is relatively small.

Japanese Patent Laid-Open No. 2002-254977

  However, in a vehicular refrigeration apparatus having a turbofan, the blowing direction of cold air tends to be shifted to the left or right side of the cargo compartment, and it is difficult to blow cool air straight toward the rear of the cargo compartment. For example, after the cold air blown to the left side of the cargo compartment hits the left wall of the cargo compartment, it bounces off to the right wall on the opposite side, and tends to zigzag between the left and right walls toward the rear of the cargo compartment. For this reason, there is a problem that an area that is not cooled by the cold air is generated in the cargo compartment, and that the cold air is difficult to reach to the rear part of the cargo compartment, and that it takes time to make the temperature of the cargo compartment a uniform low temperature. In particular, when there is a door at the rear part of the cargo compartment, it takes time to return the temperature of the rear part of the cargo compartment raised by opening and closing the door to a low temperature state.

  Moreover, in the vehicular refrigeration apparatus having a propeller fan, vortices are easily generated in the cold air, and it is difficult to uniformly blow the cold air into the luggage compartment. Further, since the fan air volume is reduced at the center of the fan and it is difficult to secure the reach distance of the cold air, the cold air cannot be uniformly blown to the rear part of the cargo compartment. Therefore, even in the vehicle refrigeration apparatus having the propeller fan, there is a problem that it takes time to bring the temperature of the luggage compartment to a uniform low temperature state. In order to secure the air volume, it is necessary to use a propeller fan having a relatively large diameter, which causes a problem that the apparatus is enlarged.

  The present invention has been made to solve the above-described problem, and a vehicle refrigeration apparatus capable of bringing the temperature of a cargo compartment to a uniform low temperature state in a relatively short time while avoiding an increase in size of the apparatus, and It is an object to provide a refrigeration vehicle.

  As a result of intensive investigations to achieve the above object, the present inventor has used a cross flow fan as a fan for blowing cool air into the cargo compartment, and has arranged a partition plate at an appropriate position on the side of the cross flow fan. By partitioning the air path, it has been found that cold air can be blown straight into the cargo compartment even though the air path is relatively short, and the present invention has been completed.

The vehicular refrigeration apparatus of the present invention made to solve the above problems includes a housing that is attached to a luggage compartment. An evaporator for cooling the air in the cargo compartment is provided in the casing. An air passage from the evaporator toward the cargo compartment is provided in the casing. A fan that blows air cooled through the evaporator into the cargo compartment is disposed in the air passage. The fan is a cross flow fan, and a partition plate for partitioning the air passage is provided on a side of the cross flow fan. The partition plate is 0.075 to 0.125 times the diameter of the cross flow fan in the direction of narrowing the air passage from the reference surface with a horizontal surface including the axis of the cross flow fan as a reference surface. Placed in position.
Here, the horizontal surface refers to a surface that is parallel to the road surface when the vehicle is stopped on a reference road surface, for example, on a leveled road surface.

In this vehicular refrigeration apparatus, the cold air from the cross flow fan is partitioned by the partition plate and proceeds straight toward the cargo compartment, so that the cold air can be blown straight toward the rear of the cargo compartment. Thereby, it is easy to spread cold air over the entire cargo compartment, and the temperature of the cargo compartment can be made to be a uniform low temperature in a relatively short time.
In addition, since a crossflow fan is used, space can be saved (smaller and thinner) compared to the case where a turbo fan or propeller fan is used to obtain the same air volume, avoiding an increase in the size of the device. be able to. Furthermore, the cross-flow fan has a high static pressure and has a stable air volume for blowing air to the highly airtight cargo compartment, and is suitable for making the temperature of the cargo compartment a uniform low temperature in a relatively short time. is there.

  In the vehicle refrigeration apparatus described above, the horizontal distance between the cross flow fan and the end of the partition plate may be 0.1 times or less the diameter of the cross flow fan. By configuring in this way, the cold air from the cross flow fan is partitioned by the partition plate and proceeds straight toward the cargo compartment, so that it is possible to blow the cold air straight toward the rear of the cargo compartment. .

  Further, in the above-described vehicle refrigeration apparatus, an electric compressor that compresses the refrigerant, a condenser that condenses the refrigerant discharged from the electric compressor by exchanging heat with outside air, and a refrigerant cooled by the condenser. And a decompression means for decompressing. In this case, it is preferable that the electric compressor, the condenser, and the pressure reducing means are provided in the casing. By setting it as such a structure, it can be set as the integrated (refrigerant sealed) vehicle refrigeration apparatus provided with all the main structures in a housing | casing. Therefore, it is not necessary to draw out the refrigerant pipe outside the apparatus, and the attachment of the vehicle refrigeration apparatus to the vehicle is enhanced. In addition, since the refrigerant piping is accommodated in the apparatus, the piping route of the refrigerant piping is shortened, the amount of refrigerant used is reduced, and the cooling performance is improved.

  Further, in the above-described vehicular refrigeration apparatus, the cross flow fan may be formed by connecting a plurality of short axis cross flow fan assemblies that are formed short in the axial direction in the axial direction. By comprising in this way, the cross flow fan can be lengthened easily. By increasing the length, the area where the cold air is blown out can be increased, so that a crossflow fan with a high airflow can be easily created. Further, an expensive molding die as in the case of integrally molding a long cross flow fan is not required, and the cost can be reduced. In addition, by changing the number to be connected, it is possible to deal with vehicle refrigeration apparatuses of various sizes, and it is possible to increase product variations.

  Moreover, the refrigeration vehicle of this invention is a refrigeration vehicle provided with the cargo compartment and the said vehicle refrigeration apparatus installed in the said cargo compartment. The cargo compartment is divided into at least two spaces, and the vehicular refrigeration apparatus is installed corresponding to each of the spaces.

  In this refrigeration vehicle, each space of the luggage compartment can be cooled by each refrigeration device for vehicles. Moreover, it is possible to set each space of a luggage compartment to a different temperature. In particular, since the main components including the electric compressor are integrally housed in the housing of the vehicle refrigeration apparatus of the present invention, the vehicle refrigeration apparatus can be placed at any position simply by extending the power supply wiring or the like. Can be installed. Moreover, since it can cool for every cargo compartment, cooling efficiency is also good.

  The refrigerated vehicle may include a 12V or 24V generator, and the vehicle refrigeration apparatus may be driven by using the generator and a storage battery as a power source. By comprising in this way, the refrigeration apparatus for vehicles can be operated using the existing generator.

  ADVANTAGE OF THE INVENTION According to this invention, the refrigeration apparatus for vehicles and the refrigeration vehicle which can make the temperature of a cargo compartment into a uniform low temperature state for a comparatively short time, avoiding the enlargement of an apparatus are obtained.

It is the perspective view which looked at the refrigeration vehicle carrying the refrigeration apparatus for vehicles concerning one embodiment of the present invention from the front left side. It is explanatory drawing which showed the internal structure of the freezing apparatus for vehicles from the one side. It is explanatory drawing which showed the internal structure of the freezing apparatus for vehicles from the other side. It is explanatory drawing which showed the internal structure of the freezing apparatus for vehicles from the upper side. It is explanatory drawing which showed the internal structure of the freezing apparatus for vehicles from the rear side. It is the rear view which looked at the freezing apparatus for vehicles from the inside of the luggage compartment. It is explanatory drawing which shows the relationship between a crossflow fan and the air path partitioned off with a partition plate. It is explanatory drawing which shows the refrigerating cycle of the refrigeration apparatus for vehicles. It is the block diagram which showed the drive system for driving the refrigeration apparatus for vehicles. It is the schematic diagram which showed the flow of the cold wind which blows off from the refrigeration apparatus for vehicles, (a) is a top view, (b) is a side view. (A) (b) is explanatory drawing which shows the refrigeration vehicle provided with several luggage compartments. It is explanatory drawing which showed the measuring point which concerns on an evaluation test. It is the graph which showed typically the range which satisfies evaluation criteria.

  Hereinafter, embodiments of a refrigeration apparatus for a vehicle and a refrigeration vehicle according to the present invention will be described with reference to the drawings. Hereinafter, a case where the vehicle refrigeration apparatus is applied to a truck type vehicle as a refrigeration vehicle will be described as an example. However, the type of the vehicle to which the present invention is applied is not limited. In the following description, when referring to “front and rear”, “left and right”, and “up and down”, the directions shown in FIGS.

  As shown in FIG. 1, the vehicle refrigeration apparatus 1 is attached to a cargo compartment 3 of a truck-type vehicle including a cabin 2 and a cargo compartment 3. The instrument panel in the cabin 2 is provided with a controller 4 for performing on / off operation of the vehicle refrigeration apparatus 1 and temperature adjustment. The truck-type vehicle body is provided with a refrigerator generator 5. The luggage compartment 3 accommodates luggage such as frozen food. A door 3d (not shown) for loading or unloading the luggage is provided at the rear of the luggage compartment 3. The controller 4 includes a display, an operation switch, an operation lever, and the like. On the display, the operating state of the refrigeration apparatus 1 for the vehicle is displayed, the display relating to the charging state of the refrigerating battery 6 (see FIG. 9) to be described later, the temperature display in the cargo compartment 3, information relating to the vehicle, for example, fuel consumption, etc. It is also possible to display travel information.

The vehicular refrigeration apparatus 1 is attached to a front wall 3a of a luggage compartment 3 that is located above and behind the cabin 2 by brackets 1j (see FIGS. 2 to 5). That is, the vehicle refrigeration apparatus 1 is attached to a position that efficiently receives the traveling wind during vehicle traveling. As shown in FIGS. 2 to 3, the vehicular refrigeration apparatus 1 includes an electric compressor 11, a condenser 12, an evaporator 13, an accumulator 14, a condenser fan 15, and a condenser fan motor in one housing 1 a. 15a, the cross flow fan 16, the cross flow fan motor 16a, and other constituent elements constituting the refrigerator are provided. That is, the vehicular refrigeration apparatus 1 is an integrated (refrigerant-enclosed) apparatus that includes all the main components in the housing 1a.
Note that the vehicular refrigeration apparatus 1 does not protrude into the cargo compartment 3, can secure the volume of the cargo compartment 3, and can improve the loading efficiency.

The inside of the housing 1a is partitioned into a front chamber 1c and a rear chamber 1d through a partition wall 1b as shown in FIGS. The front chamber 1c has a substantially trapezoidal shape in a side view, and a front chamber lower plate 1c1 constituting the lower surface is inclined so as to descend from the front portion toward the rear portion.
As shown in FIG. 4, the front chamber 1c is divided into a left chamber 1f and a right chamber 1g by a vertical wall 1e.

  As shown in FIG. 2, an electric compressor 11 and an accumulator 14 are mainly accommodated in the left chamber 1f. The electric compressor 11 is a device that draws in refrigerant, compresses it, and discharges it. The electric compressor 11 is disposed using a portion having a large height on the rear side of the left chamber 1f. The electric compressor 11 has a dryer 11a (see FIG. 4). The accumulator 14 is a gas-liquid separator that separates the refrigerant flowing from the evaporator 13 into a liquid phase refrigerant and a gas phase refrigerant. The accumulator 14 is smaller in capacity and height than the electric compressor 11, and is arranged using a portion having a small height on the front side of the left chamber 1f. The refrigerant pipe arranged in the left chamber 1f is provided with an expansion valve 17, a high pressure sensor 18a, a low pressure sensor 18b, a high pressure charge port 19a, and a low pressure charge port 19b. The expansion valve 17 functions as a decompression unit that decompresses the refrigerant cooled by the condenser 12.

  As shown in FIG. 3, a condenser 12 and a condenser fan 15 are mainly accommodated in the right chamber 1g. The condenser 12 condenses the refrigerant discharged from the electric compressor 11 (see FIG. 2) by exchanging heat with the outside air. The condenser fan 15 is a propeller fan driven by a condenser fan motor 15a.

  As shown in FIG. 3, an air intake 1c2 is formed in the front chamber lower plate 1c1 in front of the right chamber 1g. In the right chamber 1g, an inclined air guide plate 1c3 that rises from the front to the rear is provided. The air guide plate 1c3 serves to guide the air taken into the right chamber 1g through the intake port 1c2 to the upper condenser 12. A control box 20 is provided on the front side of the partition wall 1b on the rear inner side of the air guide plate 1c3. The control box 20 accommodates a control board (not shown) and electrical components that control the driving of the electric compressor 11, the driving of the condenser fan motor 15a, and the driving of the cross flow fan motor 16a. The control box 20 performs refrigeration control for controlling the electric compressor 11, the cross flow fan motor 16a, and the like in order to maintain, for example, −10 ° C. to −20 ° C.

  In the right chamber 1g, the condenser 12 is mounted horizontally. In addition, the condenser 12 is not restricted to what was attached horizontally, You may make it incline and attach.

  The condenser fan 15 is disposed above the condenser 12. The condenser fan motor 15a is supported by a bracket or the like (not shown) attached to the top plate 1c4 of the right chamber 1g. The condenser fan 15 discharges the air heat-exchanged by the condenser 12 to the outside of the housing 1a through the opening 1c5 of the top plate 1c4. Note that a net 1c6 for preventing entry of foreign matter is attached to the opening 1c5. A wing 1c7 that guides the traveling wind upward is attached to the upper front end of the right chamber 1g.

  As shown in FIGS. 2 and 3, the rear chamber 1 d has a vertically long square shape in a side view. A heat insulating material 21 is attached to the inner surface of the rear chamber 1d. The heat insulating material 21 includes the inner surface of the upper plate 1d4, the rear surface of the partition wall 1b, the inner surface of the lower plate 1d3, excluding the inner surface of the rear plate 1d5 of the rear chamber 1d, as shown in FIG. And the inner surface of the right side plate 1d8.

  As shown in FIG. 2, the evaporator 13 is a heat exchanger that evaporates the refrigerant from the expansion valve 17 and cools the air blown by the cross flow fan 16 by the latent heat of evaporation during evaporation. The evaporator 13 is positioned substantially at the center in the vertical direction in the rear chamber 1d, and is attached substantially horizontally by the support member 13a. A suction port space S <b> 1 is formed below the evaporator 13. As shown in FIG. 6, the suction port space S1 communicates with a suction port 23 (see FIG. 6) formed in the rear plate 1d5. The rear plate 1d5 is exposed in the cargo compartment 3 through the front wall 3a of the cargo compartment 3, so that the air in the cargo compartment 3 flows into the inlet port space S1 through the inlet port 23 by the operation of the cross flow fan 16. It has become. A drain pan 22 is disposed in the lower portion of the suction port space S1. The drain water accumulated in the drain pan 22 is discharged to the outside through the drain hose 22a (see FIG. 2).

As shown in FIGS. 2 and 3, the cross flow fan 16 is disposed above the evaporator 13 on the downstream side in the air flow direction of the evaporator 13. The cross flow fan 16 serves to blow out the air cooled through the evaporator 13 from the air outlet 26 provided in the rear plate 1d5 toward the cargo compartment 3.
As shown in FIG. 4, the cross flow fan 16 is formed to be long in the left-right direction along the left-right direction (longitudinal direction) of the evaporator 13. In the present embodiment, the long crossflow fan 16 is configured by connecting six short-axis crossflow fan assemblies 160 formed short in the axial direction in the axial direction. Each cross flow fan assembly 160 is a resin molded product. The cross flow fan 16 can be easily elongated by connecting adjacent facing portions of the cross flow fan assembly 160 using an adhesive or the like. The length in the axial direction of the cross flow fan assembly 160 and the number to be connected can be appropriately set in consideration of the size and capacity of the evaporator 13.
The left end portion of the cross flow fan 16 is supported by the drive shaft of the cross flow fan motor 16a. The cross flow fan motor 16a is supported by the support member 16b. A shaft member 16 c is attached to the right end portion of the cross flow fan 16. The shaft member 16 is supported by the right support member 16b via a bearing 16c1.

  As shown in FIG. 2, the cross flow fan 16 is disposed in the middle of the air path R <b> 1 from the evaporator 13 toward the cargo compartment 3 (the air outlet 26). The air path R <b> 1 is formed by a casing 24 arranged along the circumferential direction of the cross flow fan 16. A partition plate 25 that forms (partitions) an air passage R1 on the downstream side of the crossflow fan 16 is disposed behind the crossflow fan 16 on the rear side.

As shown in FIGS. 2 to 4, the partition plate 25 is a flat plate. The partition plate 25 is attached to the front surface (inner surface) of the rear plate 1d5. Moreover, the left and right ends of the partition plate 25 are fixed to the left and right support members 16b as shown in FIG. The partition plate 25 may be formed integrally with the rear plate 1d5.
As shown in FIG. 7, the partition plate 25 has a horizontal plane including the axis O <b> 1 of the crossflow fan 16 as a reference plane W, and a position that is in a direction narrowing the air passage R <b> 1 from the reference plane W (above the reference plane W). Is located).

  The installation position of the partition plate 25 (height H1 from the reference plane W) is 0 in diameter of the cross-flow fan 16 from the viewpoint of blowing cold air straight (backward in the horizontal direction) from the outlet 26 into the cargo compartment 3. The position (height H1) is preferably in the range of .075 times to 0.125 times. More preferably, the partition plate 25 is installed at a position (height H1) in a minute range around 0.1 times the diameter of the cross flow fan 16. In a range smaller than 0.075 times the diameter of the cross flow fan 16, the blowing direction of the cold air is downward in the direction of rotation of the cross flow fan 16 (the direction of arrow Y1 in FIG. Is not blown out straight. Moreover, in the range larger than 0.125 times the diameter of the cross flow fan 16, the air volume of the cool air blown into the cargo compartment 3 cannot be secured (the function as the partition plate 25 can be secured). It is difficult to ensure the reach distance of the cold air toward the rear part of the luggage compartment 3.

  The horizontal distance (gap) L1 between the outer periphery of the crossflow fan 16 and the front end of the partition plate 25 is set to 0. 0 of the diameter of the crossflow fan 16 from the viewpoint of securing the amount of cold air blown into the cargo compartment 3. It is preferable that it is 1 time or less. In a range larger than 0.1 times the diameter of the cross flow fan 16, it is not possible to ensure the amount of cold air blown into the cargo compartment 3 (the function as the partition plate 25 cannot be ensured). It is difficult to ensure the reach distance of the cold air toward the rear part of the cargo compartment 3.

  Further, the length L2 of the partition plate 25 (horizontal distance from the outer periphery of the cross flow fan 16 to the rear end portion of the partition plate 25) is from the viewpoint of blowing cool air straight from the air outlet 26 into the luggage compartment 3. A range of 0.15 to 0.35 times the diameter of the cross flow fan 16 is preferable. More preferably, the size (length L2) is 0.25 times the diameter of the cross flow fan 16. In a range smaller than 0.15 times the diameter of the cross flow fan 16, it is difficult to blow cool air straight out from the outlet 26 into the cargo compartment 3, and the reach of the cold air toward the rear of the cargo compartment 3 is secured. Difficult to do. Moreover, in the range larger than 0.35 times the diameter of the cross flow fan 16, since the length of the air path R1 (blower) becomes long, it is not preferable from a viewpoint of product size reduction.

  The height (opening height) H2 of the air passage R1 partitioned by the casing 24 and the partition plate 25 is a cross flow from the viewpoint of blowing cool air straight from the air outlet 26 into the cargo compartment 3 while securing the air volume. The size is preferably in the range of 0.5 to 0.7 times the diameter of the fan 16. More preferably, the size (height H2) is 0.6 times the diameter of the cross flow fan 16. In a range smaller than 0.5 times the diameter of the cross flow fan 16 and a range larger than 0.7 times the diameter of the cross flow fan 16, it is possible to secure the amount of cool air blown into the cargo compartment 3. Therefore, it is difficult to ensure the reach distance of the cold air toward the rear part of the cargo compartment 3.

  Further, the height H3 of the air passage R1 partitioned by the casing 24 and the outer periphery of the cross flow fan 16 is set to 0. 0 of the diameter of the cross flow fan 16 from the viewpoint of securing the air volume of the cool air blown out from the air outlet 26. The size is preferably in the range of 1 to 0.3 times. More preferably, the size (height H3) is 0.2 times the diameter of the cross flow fan 16. In a range smaller than 0.1 times the diameter of the cross flow fan 16 and a range larger than 0.3 times the diameter of the cross flow fan 16, it is possible to secure the amount of cold air blown into the cargo compartment 3. Therefore, it is difficult to ensure the reach distance of the cold air toward the rear part of the cargo compartment 3.

Next, the refrigeration cycle of the vehicle refrigeration apparatus 1 of the present embodiment will be described with reference to FIG.
As shown in FIG. 8, the vehicular refrigeration apparatus 1 configures a refrigeration cycle in which a cooling operation can be performed by connecting a front chamber 1 c and a rear chamber 1 d of a housing 1 a through refrigerant pipes 18 and 19. The refrigeration cycle is filled with a refrigerant as a working fluid for transferring heat. As the refrigerant, R404A, R407C, or the like is used as an HFC (hydrofluorocarbon) mixed refrigerant having a large global warming potential.

  When the vehicle refrigeration apparatus 1 is operated, as indicated by an arrow, the high-temperature and high-pressure gas refrigerant compressed by the electric compressor 11 in the front chamber 1c flows into the condenser 12 to exchange heat with the outside air (air). Condensates and becomes a high-pressure liquid refrigerant. The liquid refrigerant is depressurized by the action of the expansion valve 17, enters a low-temperature low-pressure gas-liquid two-phase state, and flows through the refrigerant pipe 18 to the evaporator 13 in the rear chamber 1d. In the evaporator 13, the refrigerant evaporates by exchanging heat with the air taken in from the cargo compartment 3 by the cross flow fan 16. The refrigerant evaporated in the evaporator 13 returns from the rear chamber 1d to the front chamber 1c through the refrigerant pipe 19, is stored in the accumulator 14, and is compressed again by the electric compressor 11.

As shown in FIGS. 2 and 3, a hot water coil 30 is attached to the evaporator 13. Water warmed by the heat of the engine E of the vehicle is supplied to the hot water coil 30. The supply of water to the hot water coil 30 is performed not only when the frost attached to the evaporator 13 is defrosted but also when the cargo compartment 3 is heated. By heating the luggage compartment 3, it is possible to suitably cope with physical distribution in cold regions.
Note that the hot water coil 30 is not necessarily mounted, and the defrosting operation may be performed by other methods. For example, an electric coil (not shown) that is driven by a storage battery 6 for a refrigerator, which will be described later, may be attached to the evaporator 13 to perform a defrosting operation. Further, an electromagnetic valve for refrigerant path branching (not shown) may be provided in the refrigerant pipe that leads to the discharge port of the electric compressor 11, and a bypass refrigerant pipe that leads to the inlet side of the evaporator 13 may be provided in this electromagnetic valve. In this case, the high-temperature and high-pressure refrigerant can flow directly into the evaporator 13 by operating the solenoid valve, and the evaporator 13 can be defrosted. The operation control of the electromagnetic valve can be performed by the control box 20 based on a sensor installed in the evaporator 13 or the like. Further, instead of the hot water coil 30, the above-described electric coil or the like may be used, or a refrigeration cycle capable of heating operation (heating operation) may be configured using a four-way switching valve or the like to perform heating. Good.

Next, the power supply of the vehicle refrigeration apparatus 1 will be described. FIG. 9 is a block diagram showing a drive system for driving the vehicle refrigeration apparatus.
As shown in FIG. 9, the vehicle refrigeration apparatus 1 (illustrated as the electric compressor 11 in FIG. 9) charges 12 V or 24 V power generated by the chiller generator 5 to the refrigeration battery 6, It is driven by the electric power of the storage battery 6 for the refrigerator. The vehicle refrigeration apparatus 1 is subjected to on / off control and temperature control control based on the setting of the controller 4 interposed between the refrigeration battery 6 and the storage battery 6. In addition, you may comprise so that the vehicle refrigeration apparatus 1 may be directly driven with the generator 5 for refrigerators, without passing through the storage battery 6 for refrigerators.

The generator 5 for refrigerators is driven by the engine E of the vehicle to generate 12V or 24V. The generator 5 for refrigerators is a product different from the generator 7 for vehicles, and the electric power generated with the generator 7 for vehicles is charged to the vehicle storage battery 8, and is provided as a vehicle power supply.
In addition, you may comprise so that the electric power generated with the vehicle-mounted generator 7 may be charged to the storage battery 6 for refrigerators via a transformer. Further, the vehicle refrigeration apparatus 1 may be directly driven by the electric power generated by the chiller generator 5 or the in-vehicle generator 7 without using the refrigeration battery 6.
Alternatively, the vehicle refrigeration apparatus 1 may be driven by receiving power from a 200 V power source or an external facility (such as a logistics facility or a parking facility). In this case, the cargo compartment 3 of the refrigerated vehicle can be used as a storage (such as a product storage in a busy season).

  FIGS. 10A and 10B schematically show the state of the cold air blown out from the vehicle refrigeration apparatus 1 of the present embodiment. As shown in these drawings, the cold air blown out by the cross flow fan 16 travels substantially straight along the ceiling wall 3 b of the luggage compartment 3 to the rear of the luggage compartment 3. Since the cold air is heavier than the air in the cargo compartment 3, as shown in FIG. 10B, part of the cold air flows from the vicinity of the ceiling wall 3b toward the floor 3c in the process of being blown out straight and going to the rear. By this action, the inside of the cargo compartment 3 is suitably cooled while the cold air reaches the rear part.

  The cold air that has reached the rear part of the cargo compartment 3 hits the rear wall 3d (door) and flows to the floor 3c, then flows along the floor 3c to the front wall 3a, and is sucked into the vehicular refrigeration apparatus 1. In this way, the cold air blown out from the vehicular refrigeration apparatus 1 reaches the interior of the cargo compartment 3 and effectively cools the entire interior of the cargo compartment 3.

In the vehicle refrigeration apparatus 1 of the present embodiment described above, the cold air from the cross flow fan 16 is partitioned by the partition plate 25 and proceeds straight toward the interior of the cargo compartment 3. It becomes possible to blow cool air straight. Thereby, it is easy to distribute cold air to the whole cargo compartment 3, and it becomes possible to make the temperature of the cargo compartment 3 into a uniform low temperature state in a relatively short time.
In addition, since the cross flow fan 16 is used, it is possible to save space (smaller and thinner) compared to the case where a turbo fan or propeller fan is used to obtain the same air volume, and avoids an increase in the size of the device. can do. Further, the cross flow fan 16 has a high static pressure and a stable air volume for blowing air to the highly airtight cargo room 3, and makes the temperature of the cargo room 3 uniform and low in a relatively short time. It is suitable for.

  Further, the horizontal distance L1 between the cross flow fan 16 and the front end portion of the partition plate 25 is set to 0.1 times or less the diameter of the cross flow fan 16, so that the cool air from the cross flow fan 16 is partitioned by the partition plate 25. And proceed straight into the cargo compartment 3. For this reason, it becomes possible to blow cool air straight toward the rear part of the cargo compartment 3.

  In addition, since the vehicular refrigeration apparatus 1 is an integrated type (with the refrigerant enclosed) that includes all the main components such as the electric compressor 11 in the housing 1a, it is not necessary to draw out refrigerant piping outside the apparatus. Easy to attach to vehicles. In addition, since the refrigerant piping is accommodated in the apparatus, the piping route of the refrigerant piping is shortened, the amount of refrigerant used is reduced, and the cooling performance is improved.

  Further, since the cross flow fan 16 is formed by connecting a plurality of cross flow fan assemblies 160 in the axial direction, the cross flow fan 16 can be easily elongated. By increasing the length, the area where the cold air is blown out can be increased, so that the crossflow fan 16 having a high airflow can be easily created. Further, an expensive mold as in the case of integrally molding the long cross flow fan 16 is not required, and the cost can be reduced. Moreover, by changing the number to connect, it can respond to the vehicle refrigeration apparatus 1 of various magnitude | sizes, and can increase the variation of a product.

  Further, the refrigeration vehicle includes a 12V or 24V refrigeration generator 5 and the vehicle refrigeration apparatus 1 is driven by using the refrigeration generator 5 and the refrigeration storage battery 6 as power sources. The refrigeration apparatus 1 for a vehicle can be operated using an existing generator without using a generator based on a simple design. Therefore, the installation property of the vehicle refrigeration apparatus 1 with respect to the refrigeration vehicle is high.

FIGS. 11A and 11B are explanatory views showing a refrigerated vehicle having a plurality of luggage compartments. In the refrigerated vehicle shown in FIG. 11A, the cargo compartment 3 is divided into left and right cargo compartments 301 and 302 (two left and right spaces) by a partition 300. A total of two vehicular refrigeration apparatuses 1 are provided corresponding to the cargo compartments 301 and 302.
In the refrigerated vehicle shown in FIG. 11B, the cargo compartment 3 is divided into front and rear cargo compartments 303 and 304 (two front and rear spaces) by a partition 305. The front luggage compartment 303 has the same vehicle refrigeration apparatus 1 as in the above embodiment. The front luggage compartment 303 is provided with a door 3e on the side wall. The rear luggage compartment 304 is provided with a vehicle refrigeration apparatus 1A on the upper rear side. This vehicle refrigeration apparatus 1A has substantially the same configuration as the vehicle refrigeration apparatus 1 of the above-described embodiment, except that a suction port and an air outlet (not shown) are opened downward, and includes a cross-flow fan 16. I have.

In the refrigeration vehicle as described above, each space of the cargo compartment 3 can be cooled by the refrigeration apparatuses 1 and 1A for the vehicles. Moreover, it is possible to set each space of the luggage compartment 3 to a different temperature. In particular, since the main components including the electric compressor 11 are integrally accommodated in the housing 1a, the vehicle refrigeration apparatus 1 and 1A are for the vehicle at any position simply by extending the power supply wiring or the like. Refrigeration apparatuses 1 and 1A can be installed. Moreover, since it can cool for every cargo compartment 3, cooling efficiency is also good.
The cargo compartment 3 may be divided into three or more spaces and each space may be cooled by the respective vehicle refrigeration apparatuses 1 and 1A (for example, corresponding to three temperature zone logistics). .

Evaluation Test An evaluation test performed in connection with the present invention will be described. In the evaluation test, as described in the embodiment, the suction space S1 that communicates with the upstream side of the evaporator 13 in the rear chamber 1d via the suction port 23 is formed, and the cross flow fan is formed in the casing 24 on the downstream side. 16 was installed using the vehicle refrigeration apparatus 1 in which the air path R1 was formed by the partition plate 25. As an evaluation method, the horizontal position including the axis O1 of the crossflow fan 16 is moved from the lower side to the upper side of the reference plane W to move the installation position of the partition plate 25 that partitions the air path R1, and the suction port space S1 at each position. The wind speed value and the wind speed value of the cargo compartment 3 were measured.

Evaluation Items and Evaluation Criteria (1) Whether the average of wind speed values measured in the inlet space S1 is 3.5 m / s or more.
(2) The air volume is calculated based on the wind speed value in the suction port space S1, and whether the calculated air volume is 1000 m ³ / h or more.
(3) Whether the wind speed value is 5.0 m / s or more at a point of 6 m from the outlet 26 toward the rear of the cargo compartment 3.
The above items were evaluated, and the case where all items were satisfied was considered good.

Test conditions (1) Three points P1 to P3 in the front-rear direction in the suction port space S1 are set (see FIG. 12), and the points A1 are equally spaced in the axial direction of the crossflow fan 16 for each point P1 to P3. Wind speed values were measured for 7 points (see Fig. 4) of ~ G. The point P1 is a position 20 mm forward from the suction port 23. Point P2 is an intermediate position between point P1 and point P3. The point P3 is a position 100 mm rearward from the rear surface of the partition wall 1b.
(2) The input voltage of the cross flow fan motor 16a was DC27V (JIS), rated 27V57W, and the rotational speed was 2800 rpm.
(3) As the cross flow fan 16, a cross flow fan 16 formed by adhering a cross flow fan assembly 160 having a diameter of 80 mm and a length of 100 mm to a length of 600 mm was used.
(4) The dimensions of the suction port 23 were 120 mm in height and 680 mm in length.
(5) The air volume was calculated by the following formula.
Air volume m ³ / s = average wind speed value × suction port height × suction port length × second (1h: 3600)

As the evaluation test 1, the diameter of the cross flow fan 16 is set to 0 in the direction in which the air passage R1 expands (downward) with the position of the partition plate 25 as a reference plane W including the horizontal plane including the axis O1 of the cross flow fan 16. The position was set to be 1 time. At this time, the voltage of the cross flow fan motor 16a was 27V, the current was 2.65A, and the rotation speed was 2966 rpm.
In the evaluation test 1, the cold air blown out from the air outlet 26 faced downward, and the cold air was not blown straight into the cargo compartment 3. The amount and speed of the cold air blown out from the outlet 26 did not reach the numerical values listed in the evaluation items.

As the evaluation test 2, the position of the partition plate 25 was set on the reference plane W including the axis O1 of the cross flow fan 16. At this time, the voltage of the cross flow fan motor 16a was 27 V, the current was 2.7 A, and the rotation speed was 2980 rpm.
In the evaluation test 2, similarly to the evaluation test 1, the cold air blown out from the air outlet 26 turned downward, and the cold air was not blown straight into the cargo compartment 3. The amount and speed of the cold air blown out from the outlet 26 did not reach the numerical values listed in the evaluation items.

As the evaluation test 3, the position of the partition plate 25 is set to 0.05 in the diameter of the cross flow fan 16 in the direction in which the air path R1 above the reference plane W including the axis O1 of the cross flow fan 16 is narrowed (upward). The position was set to double. At this time, the voltage of the cross flow fan motor 16a was 27 V, the current was 2.75 A, and the rotation speed was 2990 rpm.
The results of Evaluation Test 3 are shown in Table 1. In the evaluation test 3, the wind speed value increased at each of the points P1 to P3 (points A to G), but the average wind speed value was 3.2 m ³ / s, which did not satisfy the evaluation criterion (1). It was. Moreover, the airflow value was 940 m ³ / h, and the evaluation criterion (2) was not satisfied.

As the evaluation test 4, the position of the partition plate 25 is set to 0.1 in the diameter of the cross flow fan 16 in the direction in which the air path R1 above the reference plane W including the axis O1 of the cross flow fan 16 narrows (upward). The position was set to double. At this time, the voltage of the cross flow fan motor 16a was 27V, the current was 2.5A, and the rotation speed was 2850 rpm.
The results of Evaluation Test 4 are shown in Table 2. In the evaluation test 4, the wind speed value increased at each of the points P1 to P3 (points A to G), and the evaluation criteria (1) and (2) were satisfied. Moreover, in the cargo compartment 3, it became 0.55 m / s in the 6-m point from the blower outlet 26, and satisfy | filled evaluation criteria (3).

As the evaluation test 5, the position of the partition plate 25 is set to 0.133 of the diameter of the cross flow fan 16 in the direction in which the air path R1 above the reference plane W including the axis O1 of the cross flow fan 16 is narrowed (upward). The position was set to double. At this time, the voltage of the cross flow fan motor 16a was 27V, the current was 2.5A, and the rotation speed was 2880 rpm.
The results of evaluation test 5 are shown in Table 3. In the evaluation test 5, an increase in the wind speed value was observed at each of the points P1 to P3 (points A to G), but the average wind speed value was 3.27 m ³ / s, which did not satisfy the above evaluation criterion (1). It was. Moreover, the airflow value was 961 m ³ / h, and the evaluation criterion (2) was not satisfied.

  From the above evaluation tests 1 to 5, it can be seen that the evaluation test 4 satisfies the above evaluation criteria (1) to (3). When the wind speed value was measured by shifting the position of the partition plate 25 up and down based on the evaluation test 4, in the direction in which the air path R1 above the reference plane W narrows (upward), as shown in FIG. It was found that the evaluation criteria (1) to (3) are satisfied when the partition plate 25 is arranged at a position that is 0.075 to 0.125 times the diameter of the cross flow fan 16.

DESCRIPTION OF SYMBOLS 1 Refrigeration apparatus for vehicles 1A Refrigeration apparatus for vehicles 1a Case 1b Partition wall 3 Cargo compartment 3e Door 4 Controller 5 Generator for generator (generator)
6 Storage battery for refrigerating machine (storage battery)
DESCRIPTION OF SYMBOLS 11 Electric compressor 12 Condenser 13 Evaporator 16 Cross flow fan 17 Expansion valve 23 Suction port 25 Partition plate 26 Outlet 160 Cross flow fan assembly 301,302 Cargo compartment 303,304 Cargo compartment L1 Horizontal distance L2 Horizontal distance O1 Axis P1 point P2 point P3 point R1 air path S1 inlet space W reference plane

Claims (6)

A housing attached to the luggage compartment;
An evaporator provided in the housing for cooling air in the cargo compartment;
An air passage that is provided in the housing and is directed from the evaporator toward the cargo compartment;
A fan that is arranged in the air path and blows air cooled through the evaporator into the cargo compartment,
The fan is a cross flow fan,
On the side of the cross flow fan, a partition plate that partitions the air path is provided,
The partition plate is 0.075 to 0.125 times the diameter of the cross flow fan in the direction of narrowing the air passage from the reference surface with a horizontal surface including the axis of the cross flow fan as a reference surface. A refrigeration apparatus for a vehicle, which is disposed at a position.   2. The vehicular refrigeration apparatus according to claim 1, wherein a horizontal distance between the cross flow fan and an end of the partition plate is 0.1 times or less a diameter of the cross flow fan. An electric compressor that compresses the refrigerant;
A condenser that condenses the refrigerant discharged from the electric compressor by exchanging heat with outside air; and
Decompressing means for decompressing the refrigerant cooled by the condenser, and
The vehicular refrigeration apparatus according to claim 1, wherein the electric compressor, the condenser, and the pressure reducing unit are provided in the casing.   4. The cross flow fan according to claim 1, wherein the cross flow fan is formed by connecting a plurality of short-axis cross flow fan assemblies that are formed short in the axial direction in the axial direction. 5. The vehicle refrigeration apparatus described. A refrigeration vehicle comprising a cargo compartment and the vehicle refrigeration apparatus according to claim 3 or 4 installed in the cargo compartment,
The refrigeration vehicle, wherein the cargo compartment is partitioned into at least two spaces, and the refrigeration apparatus for vehicles is installed corresponding to each of the spaces. A generator for 12V or 24V, and a storage battery charged by the generator,
The refrigeration vehicle according to claim 5, wherein the vehicular refrigeration apparatus is driven by using the generator and a storage battery as a power source.

Images