US20020026805A1 - Refrigerated transport vehicle - Google Patents
Refrigerated transport vehicle Download PDFInfo
- Publication number
- US20020026805A1 US20020026805A1 US09/987,521 US98752101A US2002026805A1 US 20020026805 A1 US20020026805 A1 US 20020026805A1 US 98752101 A US98752101 A US 98752101A US 2002026805 A1 US2002026805 A1 US 2002026805A1
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- US
- United States
- Prior art keywords
- evaporator
- chamber
- refrigerated transport
- transport vehicle
- freezing chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000007710 freezing Methods 0.000 claims abstract description 51
- 230000008014 freezing Effects 0.000 claims abstract description 51
- 239000002826 coolant Substances 0.000 claims abstract description 39
- 238000001816 cooling Methods 0.000 claims abstract description 14
- 238000007599 discharging Methods 0.000 claims abstract description 7
- 239000007788 liquid Substances 0.000 claims abstract description 5
- 238000001704 evaporation Methods 0.000 claims abstract description 4
- 230000005494 condensation Effects 0.000 claims abstract description 3
- 238000009833 condensation Methods 0.000 claims abstract description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 24
- 230000007423 decrease Effects 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 239000011152 fibreglass Substances 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 229920003002 synthetic resin Polymers 0.000 description 2
- 239000000057 synthetic resin Substances 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 239000002990 reinforced plastic Substances 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
- B60P3/00—Vehicles adapted to transport, to carry or to comprise special loads or objects
- B60P3/20—Refrigerated goods vehicles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3232—Cooling devices using compression particularly adapted for load transporting vehicles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3233—Cooling devices characterised by condensed liquid drainage means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
- F25D19/003—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors with respect to movable containers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/14—Collecting or removing condensed and defrost water; Drip trays
Definitions
- the present invention relates to a refrigerated transport vehicle provided with a refrigerator for land transportation.
- FIGS. 3 and 4 Conventional refrigerated transport vehicles are shown in FIGS. 3 and 4.
- the refrigerated transport vehicle provides with a cooling system comprising an evaporator unit 10 a or 10 , a condenser unit 20 a or 20 , a compressor 5 , and coolant pipes.
- FIG. 3 shows a refrigerated transport vehicle in which the evaporator unit 10 a is arranged inside of the adiabatic freezing chamber 90 , and the condenser unit 20 a is arranged outside of the adiabatic freezing chamber 90 and above the vehicle 1 .
- FIG. 4 shows a refrigerated transport vehicle in which the evaporator unit 10 is arranged outside of the adiabatic freezing chamber 90 and above the vehicle 1 , and the condenser unit 20 is arranged on the bottom of the chassis 2 of the vehicle.
- FIG. 5 shows that the evaporator 10 equipped with the adiabatic freezing chamber 90 as shown in FIG. 4.
- an opening 91 for fixing the evaporator unit 10 to the adiabatic freezing chamber 90 is formed in the upper front wall of the adiabatic freezing chamber 90 in the travelling direction.
- the adiabatic evaporator chamber 30 is fixed to the adiabatic freezing chamber 90 so as to cover the opening 91 .
- Metal fixtures 30 d are used to fast fix the adiabatic evaporator chamber 30 to the adiabatic freezing chamber 90 .
- the evaporator unit 10 is equipped in the upper inside wall of the adiabatic evaporator chamber 30 , and maintains the inside of the adiabatic freezing chamber 90 cool.
- Metal fixtures 30 c are used to fast fix the evaporator unit 10 to the adiabatic evaporator chamber 30 .
- the outer and inner walls 30 a of the adiabatic evaporator chamber 30 are made of reinforced plastics such as fiber-glass reinforced plastic (FRP) for light weight.
- FRP fiber-glass reinforced plastic
- Foamed synthetic resin 30 b is filled between the outer and inner walls 30 a to provide thermal insulation.
- the evaporation unit 10 comprises a packing 11 , an evaporator 12 , a propeller type blower 13 , an expansion valve 14 , an accumulator 15 , a drain water pool 16 , and a drain water pipe 17 .
- the drain water generated by the evaporator 12 is accumulated in the drain water pool 16 .
- the drain water pool 16 is connected to the drain water pipe 17 .
- the drain water pipe 17 passes through the adiabatic evaporator chamber 30 , and discharges the drain water accumulated in the drain water pool 16 to the outside of the adiabatic freezing chamber 90 .
- FIGS. 5 and 6 The relationship between the evaporator unit 10 , the condenser unit 20 , and the compressor 5 of the cooling system will be explained with FIGS. 5 and 6.
- the compressor 5 provided in the engine room of the vehicle 1 is driven by the engine 6 for the driving the vehicle, via a conduction belt 7 .
- a coolant vapor of high temperature and high pressure is generated by the compressor 5 , passes through the coolant pipe 40 , and reaches the condenser 21 of the condenser unit 20 , while it is pressurized. Then the coolant vapor is cooled and condensed by contact with the outside air introduced by the propeller type fan 22 for the condenser.
- the coolant flows out of the condenser 21 , passes through the receiver 23 , the dryer 24 , and the coolant pipe 41 between the condenser unit 20 and evaporator unit 10 , and reaches the expansion valve 14 of the evaporator unit 10 . Then the coolant adiabatically expands by passing through the expansion valve 14 , and heat exchanges with air circulated between the adiabatic freezing chamber 90 and the evaporator 12 by the propeller type blower 13 , while the coolant passes through the pipe for heat exchange. Thereby, the circulating air is cooled.
- the cooled circulating air is blown out as an airflow indicated by A from the air outlet 11 a of the evaporator unit 10 to the inside of the adiabatic freezing chamber 90 by the propeller type blower 13 as shown in FIG. 5.
- the airflow A cools the inside of the adiabatic freezing chamber 90 .
- the coolant gasified in the evaporator 12 passes through the accumulator 15 , and the coolant pipe 42 , and returns to the compressor 5 as shown in FIG. 6.
- the conventional refrigerated transport vehicle shown in FIG. 3 comprises the evaporator unit 10 a in the adiabatic freezing chamber 90 ; therefore, the carrying capacity of the adiabatic freezing chamber 90 decreases.
- the conventional refrigerated transport vehicle shown in FIG. 4 comprises the condenser unit 20 arranged on the bottom of the chassis 2 of the vehicle; therefore a mudguard is necessary for the condenser unit 20 . When a mudguard is provided, it is impossible to sufficiently employ the airflow generated by driving to cool the condenser 21 .
- the condenser unit 20 or 20 a and the evaporator unit 10 or 10 a are separated in the conventional refrigerated transport vehicle; therefore, it is necessary to separately provide these units to the adiabatic freezing chamber 90 . Consequently, much time is needed to fit these units. Therefore, a small and light weight cooling system has been desired.
- the refrigerated transport vehicle of the present invention comprises
- an adiabatic freezing chamber which is provided on the vehicle body and comprises an opening
- an adiabatic evaporator chamber fixed to an outer surface of the freezing chamber so as to cover the opening and to communicate inner spaces of the freezing chamber and the evaporator chamber;
- an evaporator unit provided in the inner space of the evaporator chamber for evaporating a coolant liquid and cooling the inner spaces of the freezing chamber and the evaporator chamber;
- a condenser unit provided on the outer surface of the evaporator chamber for condensing a coolant vapor and discharging heat of condensation of the coolant vapor;
- a circulation system for circulating the coolant between the evaporator unit and the condenser unit.
- FIG. 1 shows a preferred embodiment of the evaporator unit and the condenser unit provided to the refrigerated transport vehicle of the present invention.
- FIG. 2 shows a preferred embodiment of the refrigerated transport vehicle of the present invention.
- FIG. 3 shows a conventional refrigerated transport vehicle.
- FIG. 4 shows another conventional refrigerated transport vehicle.
- FIG. 5 shows the evaporator equipped with the adiabatic freezing chamber shown in FIG. 4.
- FIG. 6 shows the relationship between the evaporator unit, the condenser unit, and the compressor of the cooling system.
- FIGS. 1 and 2 the preferred embodiment of the refrigerated transport vehicle according to the present invention will be explained.
- FIG. 2 shows the refrigerated transport vehicle provided with the cooling system.
- the cooling system comprises the evaporator unit 110 , the condenser unit 120 , the compressor 105 , and the coolant pipes 140 , 141 , and 142 .
- the compressor 105 is arranged in the engine room of the vehicle.
- the evaporator unit 110 and the condenser unit 120 are provided to the upper part of the front wall of the adiabatic freezing chamber 190 in the travelling direction of the vehicle.
- the coolant pipe 140 is provided between the compressor 105 and the condenser unit 120 , the coolant pipe 141 is provided between the condenser unit 120 and the evaporator unit 110 , and the coolant pipe 142 is provided between the evaporator unit 110 and the compressor 105 .
- the freezing chamber 190 is simple shaped, such as a quadrate shape.
- the adiabatic evaporator chamber 160 comprises the outer wall 160 a and the foamed synthetic resin layer 160 b adhered to the outer wall 160 a.
- the adiabatic evaporator chamber 160 is box shaped, and the opening for communicating the inner spaces of the freezing chamber 190 and the evaporator chamber 160 is formed in one side. That is, the adiabatic evaporator chamber 160 comprises the side walls and the front wall in the travelling direction, the ceiling wall flat extending from the top edge of the front wall, and the bottom wall.
- the bottom wall comprises the front slope face downwardly extending from the bottom edge of the front wall and the back slope face upwardly extending from the rear end of the front slope face.
- the opening is formed at the opposite side to the front wall.
- the adiabatic evaporator chamber 160 is attached to the adiabatic freezing chamber 190 with bolts so that the opening of the evaporator chamber 160 covers the opening 191 formed in the upper part of the front wall of the adiabatic freezing chamber 190 in the travelling direction.
- the evaporator chamber 160 can be detached from the freezing chamber 190 by loosening the bolts.
- the adiabatic evaporator chamber 160 comprises the dike portion 171 substantially upwardly extending from the rear end of the back slope face of the bottom wall.
- the drain water receiver 172 is formed in the bottom of the adiabatic evaporator chamber 160 . Therefore, it is unnecessary to separately provide a drain water receiver.
- the drain water is accumulated in the space between the side walls, the bottom wall, and the dike portion 171 .
- the opening 173 for discharging the drain water is formed in the bottom of the drain water receiver 172 .
- the drain pipe 1 17 is connected to the opening 173 for discharging the drain water, whereby the drain water is discharged from the evaporator chamber 160 .
- the evaporator unit 110 is provided in the inner space of the adiabatic evaporator chamber 160 while the evaporator unit 110 does not protrude toward the inside of the adiabatic freezing chamber 190 .
- the condenser unit 120 is provided on the front wall of the adiabatic evaporator chamber 160 in the traveling direction. The evaporator unit 110 and the condenser unit 120 are associated with each other.
- the evaporator unit 110 comprises the evaporator 112 and the blower 113 for the evaporator.
- the blower 113 for the evaporator generates the airflow indicated by B for the heat exchange between the coolant and the air inside of the evaporator 112 .
- a turbo blower which blows air perpendicularly to the inflow direction of the air is suitable for the blower 113 . That is, the turbo blower which takes air from the bottom side thereof, and flat blows out the air to the inner space of the freezing chamber 190 is preferable for the blower 113 .
- the condenser unit 120 comprises the condenser 121 and the blower 122 which generates the airflow indicated by C for the heat exchange between the coolant inside of the condenser 121 and the open air.
- the propeller blower is suitable for the blower 122 .
- the turbo blower when it is not necessary to generate the airflow C blowing both upwardly and downwardly, it is possible to use the turbo blower as the blower 122 .
- FIGS. 1 and 2 The relationship between the evaporator unit 110 , the condenser unit 120 , and the compressor 105 of the cooling system will be explained referring to FIGS. 1 and 2.
- the compressor 105 provided in the engine room of the vehicle is driven by the engine 6 (not shown in FIGS. 1 and 2) for the driving the vehicle.
- a gas coolant at high temperature and high pressure is generated by the compressor 105 , passes through the coolant pipe 140 , and reaches the condenser 121 of the condenser unit 120 , while it is pressurized. Then the gas coolant is cooled and condensed by contact with the outside air introduced by the propeller type fan 122 for the condenser.
- the coolant liquid flows out of the condenser 121 , passes through the coolant pipe 141 between the condenser unit 120 and evaporator unit 110 , and reaches the expansion valve (not shown in FIGS. 1 and 2) of the evaporator unit 110 . Then the coolant liquid adiabatically expands by passing through the expansion valve, and heat exchanges with air circulated between the adiabatic freezing chamber 190 and the evaporator 112 by the blower 113 for the evaporator, while the coolant passes through the pipe for heat exchange.
- the circulating air is cooled
- the air is easily circulated from the inside of the adiabatic freezing chamber 190 to the evaporator 112 , because the air rises along the front slope face.
- the cooled circulating air is blown out as an airflow indicated by B from the air outlet of the evaporator unit 110 to the inside of the adiabatic freezing chamber 190 by the blower 113 for the evaporator as shown in FIG. 1.
- the airflow B cools the inside of the adiabatic freezing chamber 190 .
- the coolant gasified in the evaporator 112 passes through the coolant pipe 142 , and returns to the compressor 105 .
- the evaporator chamber 160 , the evaporator unit 110 and the condenser unit 120 are assembled as a unit in the refrigerated transport vehicles of the present invention. Therefore, the coolant pipe between the evaporator unit 110 and the condenser unit 120 can be short; whereby the vehicle of the present invention can be light in weight, compared with the refrigerated transport vehicles in which the condenser unit is provided on the bottom of the chassis of the vehicle.
- the manufacturing cost of the refrigerated transport vehicles of the present invention is decreased, because the number of the assembling processes is small.
- the bottom of the adiabatic evaporator chamber 160 functions as a drain water receiver in the refrigerated transport vehicles of the present invention. Therefore, it is not necessary to specially provide the drain water receiver. The weight of the refrigerated transport vehicles of the present invention is decreased. Moreover, it is possible to decrease the manufacturing cost of the refrigerated transport vehicle, because the special element for the drain water receiver is not necessary.
- blowers which blow air perpendicularly to the inflow direction of the air such as a turbo blower
- blower 113 for the evaporator
- the condenser unit 120 When the condenser unit 120 is provided in the upper front wall of the adiabatic freezing chamber 190 in the travelling direction, a mudguard is not necessary. Therefore, it is possible to decrease the weight and the manufacturing cost of the refrigerated transport vehicle, compared with the refrigerated transport vehicles in which the condenser unit is provided on the bottom of the chassis of the vehicle. In addition, it is possible to sufficiently employ the airflow generated by driving to cool the condenser; therefore, the efficiency of the condenser can be improved without a decrease in the carrying capacity.
Abstract
One object of the present invention is to provide a refrigerated transport vehicle which comprises a small and light weight cooling system easily fitted to the vehicle; in order to accomplish the above object, the refrigerated transport vehicle comprising a vehicle body; an adiabatic freezing chamber which is provided on the vehicle body and comprises an opening; an adiabatic evaporator chamber fixed to an outer surface of the freezing chamber so as to cover the opening and to communicate inner spaces of the freezing chamber and the evaporator chamber; an evaporator unit provided in the inner space of the evaporator chamber for evaporating a coolant liquid and cooling the inner spaces of the freezing chamber and the evaporator chamber; a condenser unit provided on the outer surface of the evaporator chamber for condensing a coolant vapor and discharging heat of condensation of the coolant vapor; and a circulation system for circulating the coolant between the evaporator unit and the condenser unit.
Description
- 1. Field of the Invention
- The present invention relates to a refrigerated transport vehicle provided with a refrigerator for land transportation.
- This application is based on Japanese Patent Application No. Hei 11-16260, the contents of which are incorporated herein by reference.
- 2. Description of the Related Art
- Conventional refrigerated transport vehicles are shown in FIGS. 3 and 4. In order to refrigerate an
adiabatic freezing chamber 90 provided on vehicle 1, the refrigerated transport vehicle provides with a cooling system comprising anevaporator unit condenser unit compressor 5, and coolant pipes. FIG. 3 shows a refrigerated transport vehicle in which theevaporator unit 10 a is arranged inside of theadiabatic freezing chamber 90, and thecondenser unit 20 a is arranged outside of theadiabatic freezing chamber 90 and above the vehicle 1. FIG. 4 shows a refrigerated transport vehicle in which theevaporator unit 10 is arranged outside of theadiabatic freezing chamber 90 and above the vehicle 1, and thecondenser unit 20 is arranged on the bottom of thechassis 2 of the vehicle. - FIG. 5 shows that the
evaporator 10 equipped with theadiabatic freezing chamber 90 as shown in FIG. 4. As shown in FIG. 5, anopening 91 for fixing theevaporator unit 10 to theadiabatic freezing chamber 90 is formed in the upper front wall of theadiabatic freezing chamber 90 in the travelling direction. Theadiabatic evaporator chamber 30 is fixed to theadiabatic freezing chamber 90 so as to cover the opening 91.Metal fixtures 30 d are used to fast fix theadiabatic evaporator chamber 30 to theadiabatic freezing chamber 90. Theevaporator unit 10 is equipped in the upper inside wall of theadiabatic evaporator chamber 30, and maintains the inside of theadiabatic freezing chamber 90 cool.Metal fixtures 30 c are used to fast fix theevaporator unit 10 to theadiabatic evaporator chamber 30. The outer andinner walls 30 a of theadiabatic evaporator chamber 30 are made of reinforced plastics such as fiber-glass reinforced plastic (FRP) for light weight. Foamedsynthetic resin 30 b is filled between the outer andinner walls 30 a to provide thermal insulation. - As shown in FIGS. 5 and 6, the
evaporation unit 10 comprises apacking 11, anevaporator 12, apropeller type blower 13, an expansion valve 14, anaccumulator 15, adrain water pool 16, and adrain water pipe 17. The drain water generated by theevaporator 12 is accumulated in thedrain water pool 16. Thedrain water pool 16 is connected to thedrain water pipe 17. Thedrain water pipe 17 passes through theadiabatic evaporator chamber 30, and discharges the drain water accumulated in thedrain water pool 16 to the outside of theadiabatic freezing chamber 90. - The relationship between the
evaporator unit 10, thecondenser unit 20, and thecompressor 5 of the cooling system will be explained with FIGS. 5 and 6. Thecompressor 5 provided in the engine room of the vehicle 1 is driven by theengine 6 for the driving the vehicle, via aconduction belt 7. When thecompressor 5 is driven, a coolant vapor of high temperature and high pressure is generated by thecompressor 5, passes through thecoolant pipe 40, and reaches thecondenser 21 of thecondenser unit 20, while it is pressurized. Then the coolant vapor is cooled and condensed by contact with the outside air introduced by thepropeller type fan 22 for the condenser. The coolant flows out of thecondenser 21, passes through thereceiver 23, thedryer 24, and thecoolant pipe 41 between thecondenser unit 20 andevaporator unit 10, and reaches the expansion valve 14 of theevaporator unit 10. Then the coolant adiabatically expands by passing through the expansion valve 14, and heat exchanges with air circulated between theadiabatic freezing chamber 90 and theevaporator 12 by thepropeller type blower 13, while the coolant passes through the pipe for heat exchange. Thereby, the circulating air is cooled. The cooled circulating air is blown out as an airflow indicated by A from theair outlet 11 a of theevaporator unit 10 to the inside of theadiabatic freezing chamber 90 by thepropeller type blower 13 as shown in FIG. 5. The airflow A cools the inside of theadiabatic freezing chamber 90. The coolant gasified in theevaporator 12 passes through theaccumulator 15, and thecoolant pipe 42, and returns to thecompressor 5 as shown in FIG. 6. - As explained above, the conventional refrigerated transport vehicle shown in FIG. 3 comprises the
evaporator unit 10 a in theadiabatic freezing chamber 90; therefore, the carrying capacity of theadiabatic freezing chamber 90 decreases. The conventional refrigerated transport vehicle shown in FIG. 4 comprises thecondenser unit 20 arranged on the bottom of thechassis 2 of the vehicle; therefore a mudguard is necessary for thecondenser unit 20. When a mudguard is provided, it is impossible to sufficiently employ the airflow generated by driving to cool thecondenser 21. In addition, thecondenser unit evaporator unit adiabatic freezing chamber 90. Consequently, much time is needed to fit these units. Therefore, a small and light weight cooling system has been desired. - It is therefore an object of the present invention to provide a refrigerated transport vehicle comprising a cooling system which is easily fit to the vehicle, whereby it is possible to decrease its manufacturing cost. Another object of the present invention is to provide a refrigerated transport vehicle comprising a small and light weight cooling system. Another object of the present invention is to provide a refrigerated transport vehicle in which the carrying capacity of the
adiabatic freezing chamber 90 is not decreased, and the thermal efficiency is excellent. - In order to accomplish the above object, the refrigerated transport vehicle of the present invention comprises
- a vehicle body;
- an adiabatic freezing chamber which is provided on the vehicle body and comprises an opening;
- an adiabatic evaporator chamber fixed to an outer surface of the freezing chamber so as to cover the opening and to communicate inner spaces of the freezing chamber and the evaporator chamber;
- an evaporator unit provided in the inner space of the evaporator chamber for evaporating a coolant liquid and cooling the inner spaces of the freezing chamber and the evaporator chamber;
- a condenser unit provided on the outer surface of the evaporator chamber for condensing a coolant vapor and discharging heat of condensation of the coolant vapor; and
- a circulation system for circulating the coolant between the evaporator unit and the condenser unit.
- FIG. 1 shows a preferred embodiment of the evaporator unit and the condenser unit provided to the refrigerated transport vehicle of the present invention.
- FIG. 2 shows a preferred embodiment of the refrigerated transport vehicle of the present invention.
- FIG. 3 shows a conventional refrigerated transport vehicle.
- FIG. 4 shows another conventional refrigerated transport vehicle.
- FIG. 5 shows the evaporator equipped with the adiabatic freezing chamber shown in FIG. 4.
- FIG. 6 shows the relationship between the evaporator unit, the condenser unit, and the compressor of the cooling system.
- Referring to FIGS. 1 and 2, the preferred embodiment of the refrigerated transport vehicle according to the present invention will be explained.
- FIG. 2 shows the refrigerated transport vehicle provided with the cooling system. The cooling system comprises the
evaporator unit 110, thecondenser unit 120, thecompressor 105, and thecoolant pipes compressor 105 is arranged in the engine room of the vehicle. Theevaporator unit 110 and thecondenser unit 120 are provided to the upper part of the front wall of theadiabatic freezing chamber 190 in the travelling direction of the vehicle. In order to flow the coolant through the cooling system, thecoolant pipe 140 is provided between thecompressor 105 and thecondenser unit 120, thecoolant pipe 141 is provided between thecondenser unit 120 and theevaporator unit 110, and thecoolant pipe 142 is provided between theevaporator unit 110 and thecompressor 105. It is preferable that the freezingchamber 190 is simple shaped, such as a quadrate shape. - As shown in FIG. 1, the
adiabatic evaporator chamber 160 comprises theouter wall 160 a and the foamedsynthetic resin layer 160 b adhered to theouter wall 160 a. Theadiabatic evaporator chamber 160 is box shaped, and the opening for communicating the inner spaces of the freezingchamber 190 and theevaporator chamber 160 is formed in one side. That is, theadiabatic evaporator chamber 160 comprises the side walls and the front wall in the travelling direction, the ceiling wall flat extending from the top edge of the front wall, and the bottom wall. Furthermore, it is preferable that the bottom wall comprises the front slope face downwardly extending from the bottom edge of the front wall and the back slope face upwardly extending from the rear end of the front slope face. That is, the front slope face and the back slope face are crossed so as to form a V-shape. The opening is formed at the opposite side to the front wall. Theadiabatic evaporator chamber 160 is attached to the adiabatic freezingchamber 190 with bolts so that the opening of theevaporator chamber 160 covers theopening 191 formed in the upper part of the front wall of the adiabatic freezingchamber 190 in the travelling direction. Theevaporator chamber 160 can be detached from the freezingchamber 190 by loosening the bolts. - Moreover, the
adiabatic evaporator chamber 160 comprises thedike portion 171 substantially upwardly extending from the rear end of the back slope face of the bottom wall. Thereby, thedrain water receiver 172 is formed in the bottom of theadiabatic evaporator chamber 160. Therefore, it is unnecessary to separately provide a drain water receiver. The drain water is accumulated in the space between the side walls, the bottom wall, and thedike portion 171. In addition, theopening 173 for discharging the drain water is formed in the bottom of thedrain water receiver 172. The drain pipe 1 17 is connected to theopening 173 for discharging the drain water, whereby the drain water is discharged from theevaporator chamber 160. - The
evaporator unit 110 is provided in the inner space of theadiabatic evaporator chamber 160 while theevaporator unit 110 does not protrude toward the inside of the adiabatic freezingchamber 190. Thecondenser unit 120 is provided on the front wall of theadiabatic evaporator chamber 160 in the traveling direction. Theevaporator unit 110 and thecondenser unit 120 are associated with each other. - The
evaporator unit 110 comprises theevaporator 112 and theblower 113 for the evaporator. Theblower 113 for the evaporator generates the airflow indicated by B for the heat exchange between the coolant and the air inside of theevaporator 112. A turbo blower which blows air perpendicularly to the inflow direction of the air is suitable for theblower 113. That is, the turbo blower which takes air from the bottom side thereof, and flat blows out the air to the inner space of the freezingchamber 190 is preferable for theblower 113. - The
condenser unit 120 comprises thecondenser 121 and theblower 122 which generates the airflow indicated by C for the heat exchange between the coolant inside of thecondenser 121 and the open air. The propeller blower is suitable for theblower 122. Moreover, when it is not necessary to generate the airflow C blowing both upwardly and downwardly, it is possible to use the turbo blower as theblower 122. - The relationship between the
evaporator unit 110, thecondenser unit 120, and thecompressor 105 of the cooling system will be explained referring to FIGS. 1 and 2. Thecompressor 105 provided in the engine room of the vehicle is driven by the engine 6 (not shown in FIGS. 1 and 2) for the driving the vehicle. When thecompressor 105 is driven, a gas coolant at high temperature and high pressure is generated by thecompressor 105, passes through thecoolant pipe 140, and reaches thecondenser 121 of thecondenser unit 120, while it is pressurized. Then the gas coolant is cooled and condensed by contact with the outside air introduced by thepropeller type fan 122 for the condenser. The coolant liquid flows out of thecondenser 121, passes through thecoolant pipe 141 between thecondenser unit 120 andevaporator unit 110, and reaches the expansion valve (not shown in FIGS. 1 and 2) of theevaporator unit 110. Then the coolant liquid adiabatically expands by passing through the expansion valve, and heat exchanges with air circulated between the adiabatic freezingchamber 190 and theevaporator 112 by theblower 113 for the evaporator, while the coolant passes through the pipe for heat exchange. Thereby, the circulating air is cooled When theadiabatic evaporator chamber 160 comprises the front slope face upwardly extending from bottom of theadiabatic evaporator chamber 160, the air is easily circulated from the inside of the adiabatic freezingchamber 190 to theevaporator 112, because the air rises along the front slope face. The cooled circulating air is blown out as an airflow indicated by B from the air outlet of theevaporator unit 110 to the inside of the adiabatic freezingchamber 190 by theblower 113 for the evaporator as shown in FIG. 1. The airflow B cools the inside of the adiabatic freezingchamber 190. The coolant gasified in the evaporator 112 passes through thecoolant pipe 142, and returns to thecompressor 105. - As explained above, the
evaporator chamber 160, theevaporator unit 110 and thecondenser unit 120 are assembled as a unit in the refrigerated transport vehicles of the present invention. Therefore, the coolant pipe between theevaporator unit 110 and thecondenser unit 120 can be short; whereby the vehicle of the present invention can be light in weight, compared with the refrigerated transport vehicles in which the condenser unit is provided on the bottom of the chassis of the vehicle. In addition, it is possible to provide theevaporator unit 110 and thecondenser unit 120 on the adiabatic freezingchamber 190 as a unit; therefore, the arrangement of theevaporator unit 110 and thecondenser unit 120 to the adiabatic freezingchamber 190 is simple. The manufacturing cost of the refrigerated transport vehicles of the present invention is decreased, because the number of the assembling processes is small. - In addition, the bottom of the
adiabatic evaporator chamber 160 functions as a drain water receiver in the refrigerated transport vehicles of the present invention. Therefore, it is not necessary to specially provide the drain water receiver. The weight of the refrigerated transport vehicles of the present invention is decreased. Moreover, it is possible to decrease the manufacturing cost of the refrigerated transport vehicle, because the special element for the drain water receiver is not necessary. - When the blowers which blow air perpendicularly to the inflow direction of the air such as a turbo blower is used as the
blower 113 for the evaporator, it is possible to make theevaporator unit 110 compact. - When the
condenser unit 120 is provided in the upper front wall of the adiabatic freezingchamber 190 in the travelling direction, a mudguard is not necessary. Therefore, it is possible to decrease the weight and the manufacturing cost of the refrigerated transport vehicle, compared with the refrigerated transport vehicles in which the condenser unit is provided on the bottom of the chassis of the vehicle. In addition, it is possible to sufficiently employ the airflow generated by driving to cool the condenser; therefore, the efficiency of the condenser can be improved without a decrease in the carrying capacity. - The refrigerated transport vehicle in which the
condenser unit 120 is provided in the upper front wall of the adiabatic freezingchamber 190 in the travelling direction is explained above. However, it is possible to provide thecondenser unit 120 on the top or the bottom wall of theadiabatic evaporator chamber 160. However, the total height of the refrigerated transport vehicle increases in these cases; therefore, it is suitable to provide thecondenser unit 120 in the upper front wall of the adiabatic freezingchamber 190 in the travelling direction.
Claims (8)
1. A refrigerated transport vehicle comprising
a vehicle body;
an adiabatic freezing chamber which is provided on the vehicle body and comprises an opening;
an adiabatic evaporator chamber fixed to an outer surface of the freezing chamber so as to cover the opening and to communicate inner spaces of the freezing chamber and the evaporator chamber;
an evaporator unit provided in the inner space of the evaporator chamber for evaporating a coolant liquid and cooling the inner spaces of the freezing chamber and the evaporator chamber;
a condenser unit provided on the outer surface of the evaporator chamber for condensing a coolant vapor and discharging heat of condensation of the coolant vapor; and
a circulation system for circulating the coolant between the evaporator unit and the condenser unit.
2. A refrigerated transport vehicle according to claim 1 , wherein a drain water receiver is formed at the bottom of the evaporator chamber.
3. A refrigerated transport vehicle according to claim 1 , wherein said evaporator unit comprises a blower which takes air from the bottom side thereof, and flat blows out the air to the inner space of the freezing chamber.
4. A refrigerated transport vehicle according to claim 1 , wherein said evaporator chamber is provided in the upper front wall of the freezing chamber in the travelling direction of the vehicle.
5. A refrigerated transport vehicle according to claim 1 , wherein said evaporator chamber comprises the bottom wall comprising a front slope face and a back slope face, the front slope face and the back slope face are crossed so as to form a V-shape, and a drain water receiver is formed at the cross portion.
6. A refrigerated transport vehicle according to claim 5 , wherein a dike portion substantially upwardly extending from the rear end of the back slope face is provided.
7. A refrigerated transport vehicle according to claim 6 , wherein an opening for discharging the drain water is formed in the bottom of the drain water receiver, and a drain pipe is connected to the opening for discharging the drain water.
8. A refrigerated transport vehicle according to claim 1 , wherein said condenser unit, the evaporator unit, and the freezing chamber are substantially linearly arranged in the travelling direction of the vehicle.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/987,521 US20020026805A1 (en) | 1999-01-25 | 2001-11-15 | Refrigerated transport vehicle |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11016260A JP2000213849A (en) | 1999-01-25 | 1999-01-25 | Refrigerated transport vehicle |
JP11-016260 | 1999-01-25 | ||
US09/482,087 US6374626B1 (en) | 1999-01-25 | 2000-01-13 | Refrigerated transport vehicle |
US09/987,521 US20020026805A1 (en) | 1999-01-25 | 2001-11-15 | Refrigerated transport vehicle |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/482,087 Continuation US6374626B1 (en) | 1999-01-25 | 2000-01-13 | Refrigerated transport vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
US20020026805A1 true US20020026805A1 (en) | 2002-03-07 |
Family
ID=11911601
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/482,087 Expired - Lifetime US6374626B1 (en) | 1999-01-25 | 2000-01-13 | Refrigerated transport vehicle |
US09/987,521 Abandoned US20020026805A1 (en) | 1999-01-25 | 2001-11-15 | Refrigerated transport vehicle |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/482,087 Expired - Lifetime US6374626B1 (en) | 1999-01-25 | 2000-01-13 | Refrigerated transport vehicle |
Country Status (9)
Country | Link |
---|---|
US (2) | US6374626B1 (en) |
EP (1) | EP1022527A3 (en) |
JP (1) | JP2000213849A (en) |
CN (1) | CN1153696C (en) |
ID (1) | ID25665A (en) |
IL (1) | IL134119A0 (en) |
SG (1) | SG88767A1 (en) |
TR (1) | TR200000233A1 (en) |
TW (1) | TW543560U (en) |
Cited By (5)
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---|---|---|---|---|
US20090288438A1 (en) * | 2008-05-22 | 2009-11-26 | Viegas Herman H | Distributed refrigeration system |
US20110162395A1 (en) * | 2008-09-17 | 2011-07-07 | Bruno Chakiachvili | Electrically powered transport refrigeration units |
US20120159973A1 (en) * | 2010-11-22 | 2012-06-28 | Donald Kirner | Condensate drain assembly |
US9464839B2 (en) | 2011-04-04 | 2016-10-11 | Carrier Corporation | Semi-electric mobile refrigerated system |
US20180245835A1 (en) * | 2015-02-27 | 2018-08-30 | Daikin Industries, Ltd. | Refrigeration apparatus for containers |
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CN1302367A (en) * | 1999-04-28 | 2001-07-04 | 塞莫金公司 | Transport temperature control unit |
JP2003097873A (en) * | 2001-09-26 | 2003-04-03 | Mitsubishi Heavy Ind Ltd | Operation method for refrigeration unit for land transportation, and refrigeration unit for land transportation |
US7246502B2 (en) * | 2003-12-12 | 2007-07-24 | Trans/Air Manufacturing Corp | Self-contained flush-mount bulkhead air conditioning unit with novel evaporator/blower assembly housing |
US7614242B1 (en) * | 2004-11-23 | 2009-11-10 | Carlos Quesada Saborio | Transport refrigeration system |
JP4681522B2 (en) * | 2006-09-26 | 2011-05-11 | 株式会社クボタ | Work vehicle |
JP2008202913A (en) | 2007-02-22 | 2008-09-04 | Mitsubishi Heavy Ind Ltd | Refrigerating unit |
US8899059B2 (en) * | 2010-08-26 | 2014-12-02 | Wheeled Coach Industries, Inc. | External condenser and light assembly |
JP5754917B2 (en) * | 2010-11-05 | 2015-07-29 | 三菱重工業株式会社 | Refrigeration unit for vehicle transportation |
CN103057458B (en) * | 2011-10-21 | 2016-07-13 | 东普雷股份有限公司 | The frame structure of vehicle-mounted refrigerating plant |
CN102745040B (en) * | 2012-07-16 | 2014-07-16 | 苏州博阳制冷设备有限公司 | Direct-current driven freezing and refrigerating car |
CN105960354B (en) | 2014-02-03 | 2020-09-25 | 开利公司 | Vertical sliding solution for a condenser unit for a refrigerated goods truck |
CN105216585B (en) * | 2015-10-14 | 2018-04-17 | 珠海格力电器股份有限公司 | Refrigerator car air-conditioning system and its control method and refrigerator car |
CN105437919B (en) * | 2015-12-17 | 2018-08-10 | 珠海格力电器股份有限公司 | Hybrid cold storage plant, refrigerating transport vehicle and refrigerating method |
US20180274838A1 (en) * | 2017-03-27 | 2018-09-27 | Veba Meditemp B.V. | Air temperature regulating device |
CN107101520B (en) * | 2017-07-07 | 2021-04-02 | 安徽科瑞克保温材料有限公司 | Inner fin heat exchange tube, condenser and mobile refrigeration house thereof |
CN111936800A (en) | 2018-04-13 | 2020-11-13 | 开利公司 | Transport refrigeration modular unit |
BE1027191B1 (en) * | 2019-04-16 | 2020-11-17 | Crelem Bakeries Nv | TRANSPORT OF BAKERY PRODUCTS |
CN111301260B (en) * | 2020-03-16 | 2022-01-04 | 王会涛 | Multifunctional logistics vehicle |
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DE2558822C3 (en) | 1975-12-27 | 1980-09-11 | Peter Volker Dipl.-Ing. 4300 Essen Grosskopf | Cooling truck with a refrigeration machine in block design |
JPH0686976B2 (en) | 1985-10-17 | 1994-11-02 | ダイキン工業株式会社 | Refrigeration equipment for containers |
DE3856206T2 (en) * | 1987-03-16 | 1999-03-11 | Hitachi Ltd | Sintered ceramic body and process for its manufacture |
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US5222373A (en) * | 1992-09-16 | 1993-06-29 | Thermo King Corporation | Transport refrigeration condenser unit suitable for horizontal and vertical mounting |
US5265435A (en) * | 1992-12-31 | 1993-11-30 | Phyllis M. Morefield | Vehicle refrigeration system |
JP3787962B2 (en) * | 1996-08-05 | 2006-06-21 | 株式会社デンソー | Air conditioner for vehicles |
WO1999000632A1 (en) | 1997-06-30 | 1999-01-07 | Zexel Co., Ltd. | Refrigerating apparatus for vehicles |
US5878592A (en) * | 1998-05-20 | 1999-03-09 | Carrier Corporation | Evaporator housing |
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-
1999
- 1999-01-25 JP JP11016260A patent/JP2000213849A/en active Pending
- 1999-07-17 TW TW092201291U patent/TW543560U/en not_active IP Right Cessation
-
2000
- 2000-01-13 US US09/482,087 patent/US6374626B1/en not_active Expired - Lifetime
- 2000-01-17 CN CNB001010875A patent/CN1153696C/en not_active Expired - Lifetime
- 2000-01-18 SG SG200000295A patent/SG88767A1/en unknown
- 2000-01-19 IL IL13411900A patent/IL134119A0/en unknown
- 2000-01-20 EP EP00400141A patent/EP1022527A3/en not_active Withdrawn
- 2000-01-24 ID IDP20000051D patent/ID25665A/en unknown
- 2000-01-25 TR TR2000/00233A patent/TR200000233A1/en unknown
-
2001
- 2001-11-15 US US09/987,521 patent/US20020026805A1/en not_active Abandoned
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090288438A1 (en) * | 2008-05-22 | 2009-11-26 | Viegas Herman H | Distributed refrigeration system |
US8037704B2 (en) | 2008-05-22 | 2011-10-18 | Thermo King Corporation | Distributed refrigeration system |
US20110162395A1 (en) * | 2008-09-17 | 2011-07-07 | Bruno Chakiachvili | Electrically powered transport refrigeration units |
US20120159973A1 (en) * | 2010-11-22 | 2012-06-28 | Donald Kirner | Condensate drain assembly |
US9464839B2 (en) | 2011-04-04 | 2016-10-11 | Carrier Corporation | Semi-electric mobile refrigerated system |
US20180245835A1 (en) * | 2015-02-27 | 2018-08-30 | Daikin Industries, Ltd. | Refrigeration apparatus for containers |
US11015855B2 (en) * | 2015-02-27 | 2021-05-25 | Daikin Industries, Ltd. | Refrigeration apparatus for containers |
Also Published As
Publication number | Publication date |
---|---|
IL134119A0 (en) | 2001-04-30 |
CN1153696C (en) | 2004-06-16 |
TW543560U (en) | 2003-07-21 |
EP1022527A2 (en) | 2000-07-26 |
EP1022527A3 (en) | 2001-02-28 |
US6374626B1 (en) | 2002-04-23 |
TR200000233A1 (en) | 2003-01-21 |
CN1262192A (en) | 2000-08-09 |
SG88767A1 (en) | 2002-05-21 |
ID25665A (en) | 2000-10-19 |
JP2000213849A (en) | 2000-08-02 |
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Legal Events
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