WO2008001525A1

WO2008001525A1 - Refrigerated container

Info

Publication number: WO2008001525A1
Application number: PCT/JP2007/057589
Authority: WO
Inventors: Kouji Matsuoka; Takayasu Satou
Original assignee: Yanmar Co., Ltd.
Priority date: 2006-06-27
Filing date: 2007-04-04
Publication date: 2008-01-03
Also published as: JP2008008517A; CN101501414A

Abstract

A refrigerated container (1) where the temperature in a container (3) is controlled by a refrigeration unit (4) for circulating refrigerant by a compressor (11). The exit path of a condenser (12) is bifurcated into two routes. A bypass route (114), one of the two, is connected to an expansion valve via a solenoid valve (115), and the other route is connected to the expansion valve (113) after passing an expansion section and a supercooling heat exchanger (13n), which is a part of an evaporator (13), in that order. In supercooling operation, the solenoid valve (115) is closed.

Description

Specification

Refrigeration container

Technical field

[0001] The present invention relates to a technique of a refrigerant circuit configuration of a refrigeration container.

Background art

[0002] Conventionally, the technology of a refrigerated container having a refrigeration unit on the open end of the container is known. The refrigeration unit can cool the inside of the container in a wide temperature range depending on the cargo loaded on the container, from freezing to refrigeration. However, the cooling load differs greatly between the 30 ° C setting (freezing) and the low temperature setting near 0 ° C (refrigeration). In such a case, for example, the refrigeration unit is equipped with a supercooler to handle a wide range of cooling loads with a single compressor. Supercooling is the action of cooling the high-pressure and high-temperature refrigerant liquid condensed in the condenser. The supercooling effect can reduce the inlet enthalpy of the evaporator and improve the evaporator capacity, that is, the cooling capacity.

For example, Patent Document 1 discloses a refrigerant circuit structure that supercools liquid refrigerant by exchanging heat between the compressor suction refrigerant and the liquid refrigerant from the receiver in FIG. 1 (reference numeral 6 is a supercooling heat exchanger). It discloses the composition. Also disclosed is a configuration in which the expansion valve is fully opened to limit the refrigeration capacity of the refrigerant circuit in chilled operation.

Patent Document 1: Japanese Patent No. 3239804

Disclosure of the invention

Problems to be solved by the invention

However, as in Patent Document 1, a configuration in which the supercooler is provided as a separate and independent heat exchanger requires a separate device arrangement space. In addition, the configuration in which the expansion valve is fully opened to limit the refrigeration capacity of the refrigerant circuit is the same as that during the refrigeration operation, so the amount of reduction in the compressor load is poor.

Therefore, the problem to be solved is to present a refrigerant circuit configuration capable of omitting the supercooler as a heat exchanger and a refrigerant circuit configuration capable of limiting the amount of refrigerant circulation in the refrigeration container. Means for solving the problem

[0004] The problems to be solved by the present invention are as described above. Next, means for solving the problems will be described.

[0005] The present invention relates to a refrigeration container in which the temperature in a container is controlled by a refrigeration unit that circulates refrigerant using a compressor. The condenser outlet path is divided into two, and the path is connected to an expansion valve via an on-off valve. On the other hand, the other path is connected to the expansion valve after passing through a part of the expansion section and the evaporator in this order, and the on-off valve is closed during the supercooling operation.

[0006] The present invention provides a refrigeration container that controls the temperature in a container with a refrigeration unit that circulates a refrigerant in a compressor, wherein the compressor suction path is provided in two paths in parallel, and one path is connected via an on-off valve. Connected to the compressor, the other path is connected to the compressor via an opening adjustment valve, and the on-off valve is opened during refrigeration operation, and the on-off valve is closed during chilled operation. .

The invention's effect

[0007] As the effects of the present invention, the following effects are obtained.

[0008] In the present invention, a part of the evaporator communicating with the container in a low-temperature environment such as a refrigeration operation can be used as a supercooler, and a separate supercooler can be omitted as a heat exchanger. In addition, since the entire amount of circulating refrigerant is supercooled with the low-temperature air inside the container, the refrigeration efficiency is better than when the supercooling refrigerant is branched.

In the present invention, the responsiveness of the refrigerant circulation amount adjustment and the opening degree adjustment accuracy can be improved during the freezing operation and the refrigeration operation.

Brief Description of Drawings

FIG. 1 is a side view and a rear view showing a state in which a refrigerated container according to the present invention is loaded on a truck.

[Fig. 2] Front view of the refrigeration unit.

[Fig. 3] Perspective view of the left front force.

[4] Perspective view of the right front force.

[Fig. 5] Front view with the outer plate removed.

FIG. 6 is a rear view with the outer plate removed. [7] AA sectional view in FIG. 5 showing the arrangement of the condenser and the evaporator.

圆 8] AA diagram showing a state where the condenser fan bracket in FIG. 7 is rotated.

9) BB cross-sectional view in FIG. 5 showing the configuration of the exhaust tail pipe.

圆 10] CC sectional view in Fig. 5 showing the outlet structure of the exhaust tail pipe.

[11] DD sectional view in FIG. 9 showing the support structure of the exhaust tail pipe.

FIG. 12 is a cross-sectional view taken along the line EE in FIG.

圆 13] FF cross section in Fig. 9 showing the drainage structure of the exhaust tailpipe.

FIG. 14 is a right side view of the refrigeration unit showing a state where the engine is taken out of the refrigeration unit.圆 15] Right side view of a refrigerated container provided with a ladder and a grip for approaching the operation unit.

FIG. 16 is a cross-sectional view taken along the line GG in FIG. 15, showing the configuration of the operation unit.

圆 17] A right side view of the refrigeration unit showing a state in which the fuel tank is rotated.

[Fig. 18] FF sectional view in Fig. 9 showing the bottom structure of the fuel tank.

FIG. 19 is a front view showing a power cable storage box.

圆 20] Perspective view of the evaporator attached with the defrost heater as well as the downward force.

FIG. 21 is a side view of the same as seen from the X direction in FIG.

[22] A refrigerant circuit diagram showing the refrigerant circuit configuration of the refrigerating unit.

FIG. 23 is a side view showing the configuration of a two-temperature zone container.

[24] A perspective view showing a rear chamber control unit.

FIG. 25 is a cross-sectional view of HH in FIG. 24 showing the rear chamber control unit.

Explanation of symbols

1 Refrigeration container

3 container

4 Refrigeration unit

12 Condenser

13 Evaporator

13η Subcooling heat exchanger

113 expansion valve

114 Bypass path 115 Solenoid valve

BEST MODE FOR CARRYING OUT THE INVENTION

Next, embodiments of the invention will be described.

FIG. 1 is a side view and a rear view showing a state in which a refrigerated container according to the present invention is loaded on a truck, FIG. 2 is a front view of the refrigeration unit, and FIG. 3 is a perspective view as seen from the left front. 4 is a perspective view of the right front force as well, FIG. 5 is a front view of the same with the outer plate removed, and FIG. 6 is a rear view of the same with the outer plate removed.

Fig. 7 is a cross-sectional view taken along line AA in Fig. 5 showing the arrangement of the condenser and the evaporator, Fig. 8 is an AA view showing a state in which the condenser fan bracket in Fig. 7 is rotated, and Fig. 9 is a configuration of the exhaust tail pipe. FIG. 6 is a BB sectional view in FIG.

FIG. 10 is a CC sectional view in FIG. 5 showing the outlet structure of the exhaust tail pipe, FIG. 11 is a DD sectional view in FIG. 9 showing the support structure of the exhaust tail pipe, and FIG. 12 is an EE sectional view in FIG.

Fig. 13 is a cross-sectional view of the FF in Fig. 9 showing the drainage structure of the exhaust tail pipe, Fig. 14 is a right side view of the refrigeration unit showing the engine taken out of the refrigeration unit, and Fig. 15 is close to the operation unit It is a right view of the freezing container provided with the ladder and the holding part.

16 is a cross-sectional view taken along the line GG in FIG. 15 showing the configuration of the operation unit, FIG. 17 is a right side view of the refrigeration unit showing a state where the fuel tank is rotated, and FIG. 18 is a cross-sectional view taken along line FF in FIG. FIG.

FIG. 19 is a front view showing a power cable storage box, FIG. 20 is a perspective view of an evaporator with a defrost heater attached, as viewed from below, and FIG. 21 is a side view of FIG.

22 is a refrigerant circuit diagram showing the refrigerant circuit configuration of the refrigeration unit, FIG. 23 is a side view showing the configuration of the two-temperature zone container, and FIG. 24 is a perspective view showing the rear chamber control unit.

FIG. 25 is a cross-sectional view taken along the line HH in FIG. 24 showing the rear chamber control unit.

[0013] First, a refrigerated container according to an embodiment of the present invention will be briefly described. Containers are large containers used for freight transportation. Carriers use containers to carry out integrated transportation to and from the door to reduce costs and prevent damage and theft. Also, the refrigeration unit is low A machine that supplies hot air to cool and freeze items. In other words, the refrigeration container is a large container used for freight transportation with the refrigeration unit having a low temperature inside the container. The refrigerated container can be set in various low temperature zones such as freezing or refrigeration. The refrigeration unit controls the operation so that the temperature inside the container reaches the set temperature. In this way, the refrigerated container can transport various cargoes such as frozen food, ice cream, fresh fish or fruits. Also, refrigerated containers are intended for integrated transportation

It can be adapted for transportation by ship, rail or truck. For example, FIG. 1 shows a refrigerated container 1 loaded on a track 2.

As shown in FIG. 1, the refrigerated container 1 is also configured with a container 3 and a refrigeration unit 4 force. Container 3 is made up of members that have heat insulation properties compared to ordinary containers (not refrigerated containers).

The container 3 is configured to have an opening on one side of the wife and a door 5 that can be opened and closed on the other side. The refrigeration unit 4 supported by the frame 6 is attached to the opened wife surface. On the other hand, cargo can be taken in and out from the wife's face, which has an openable door 5. Here, the refrigeration unit 4 will be briefly described. Hereinafter, for the sake of brevity, in the refrigerated container 1 in which the refrigeration unit 4 is attached to the container 3, the surface exposed to the outside is the front of the refrigeration unit 4, and the rear surface (= the surface exposed inside the container), left and right, Enter the width, depth and height.

As shown in FIGS. 5 and 6, the refrigeration unit 4 constitutes a refrigeration cycle in one unit. More specifically, the refrigeration unit 4 includes a compressor 11 that sucks a low-temperature / low-pressure gas refrigerant and compresses it into a high-temperature / high-pressure gas refrigerant, and a condensation that condenses the high-temperature / high-pressure gas refrigerant into a high-temperature / high-pressure liquid refrigerant. , A receiver 19 that retains high-temperature and high-pressure liquid refrigerant, an expansion valve 113 that expands the high-temperature and high-pressure liquid refrigerant into a low-temperature and low-pressure liquid-gas refrigerant (see FIG. 22), and a low-temperature and low-pressure liquid refrigerant. And an evaporator 13 for evaporating the gas refrigerant into a low-temperature and low-pressure gas refrigerant. The condenser 12 is an air-cooled heat exchanger that uses a condenser fan 16 driven by a condenser fan electric motor 14 to cool the refrigerant with outside air. The evaporator 13 is an air-cooled heat exchanger that cools the internal air by allowing the evaporator fan motor 15 to absorb the heat of evaporation from the internal air to the refrigerant by using the evaporator fan 17. [0016] The refrigeration unit 4 includes a generator 21 that supplies power to the compressor 11, an engine 22 that drives the generator 21, a fuel tank 23 that stores the fuel of the engine 22, an intake pipe 32, and An intake system 31 composed of an air cleaner 33 and an exhaust system 41 composed of an exhaust pipe 42 and a muffler 43 are provided. Further, the refrigeration unit 4 includes an electrical component box 51 and a power cable 52. The electrical component box 51 includes an electronic control unit (hereinafter referred to as an ECU) 50 that controls equipment such as the engine 22 and the compressor 11, and an operation panel 94 that sets the internal temperature and the like.

With such a configuration, the generator 21 is driven by the engine 22, and the compressor 11, the condenser fan motor 14 or the evaporator fan motor 15 is driven by the electricity supplied by the generator 21, The temperature control of the refrigeration unit 4 is performed. Furthermore, it can be driven by electricity supplied from an external commercial power source.

[0017] Hereinafter, the configuration of each part of the refrigeration unit 4 of the present embodiment will be described in detail. Next, a refrigerant circuit configuration having a supercooling circuit using the evaporator of the refrigeration unit 4 will be described in detail. Furthermore, the two temperature zone control structure of the container 3 of the refrigeration container 1 will be described in detail.

In the following, the operators handling the refrigeration unit 4 such as those who perform maintenance / inspection of the refrigeration unit 4 and those who operate the temperature setting of the refrigeration unit 4 are all workers.

First, an overall layout configuration of the refrigeration unit 4 will be described with reference to FIGS.

As shown in FIGS. 5 to 7, the refrigeration unit 4 is configured by arranging devices in a casing 61. The casing 61 is configured to be largely divided into an upper part 101, a central part 102, and a lower part 103 in the height direction. The central portion 102 is configured to be divided into a right central portion 102a and a left central portion 102b in the width direction.

In the upper part 101, a condenser 12, a condenser fan motor 14 and a condenser fan 16 are arranged on the front side, and an evaporator 13, an evaporator fan motor 15 and an evaporator fan 17 are arranged on the back side. In the central part 102, the engine system power is arranged in the right central part 102a, and the refrigerant system is arranged in the left central part 102b. In other words, the engine system and the refrigerant system are arranged in the same level. A fuel tank 23 is disposed in the lower part 103. With this configuration, for example, even when the refrigerated container 1 is loaded on the truck 2, the fuel tank 23 and the oil filler port 36 (see FIG. 3) are easily accessible. There is. That is, the worker can easily perform the refueling operation. In this way, maintainability is improved in the refrigeration unit 4.

Further, since the generator 21, the engine 22 and the compressor 11 which are heavy objects are arranged in the same hierarchy, the mounting base of the generator 21 and the engine 22 can be configured as the common frame 62. Since the number of parts can be reduced by using a common mounting base, it is possible to reduce parts management man-hours and assembly man-hours.

Further, as shown in FIGS. 5 to 7, the fuel tank 23 is disposed in the lower portion 103 of the casing 61. The fuel tank 23 is formed so that the length in the longitudinal direction is substantially the same as the length in the width direction of the casing 61.

By adopting such a configuration, the fuel tank 23 can secure a maximum volume in a given space in the casing 61, so that a long-term oil-free operation can be realized.

In addition, as shown in FIG. 5, an oil feed pipe 28 engine 22 and a fuel tank 23 are connected via a feed pump 24 and an oil filter 25. Here, the feed pump 24 is a pump that supplies the fuel stored in the fuel tank 23 to the engine 22. The oil filter 25 is a filter that filters the supplied fuel. The feed pump 24 and the oil filter 25 are disposed adjacent to the right side of the fuel tank 23 in the lower part 103 of the casing 61.

By adopting such a configuration, the feed pump 24 can suppress the height difference from the fuel tank 23, and the fuel oil feeding efficiency of the feed pump 24 is improved.

Next, the heat exchanger layout configuration of the refrigeration unit 4 will be described in detail with reference to FIGS.

As shown in FIGS. 5 to 7, in the upper part 101 of the casing 61, the condenser 12 is placed on the front side and the evaporator 13 is placed on the back side; '63 c.

The condenser 12 is formed with a large heat exchange area compared to the evaporator 13. The condenser 12 flows so that the outside air flows in the direction penetrating the wife surface of the container 3 (arrow P in FIG. 7). Placed in. Further, the evaporator 13 is arranged so that the air in the cabinet flows in the vertical direction (arrow Q in FIG. 7).

[0023] By adopting such a configuration, the following advantages can be obtained. Usually, in the refrigeration cycle, the condensation capacity needs to be greater than the evaporation capacity because of the relationship of condensation capacity = compression function + evaporation capacity. Therefore, the heat exchange area of the condenser is made larger than that of the evaporator. In this case, the depth dimension of the refrigeration unit 4 increases if the condenser is arranged like the evaporator. On the other hand, if the heat exchange area is made substantially the same, it is necessary to increase the condenser fan air volume more than the evaporator. However, in this case, the number of fans, the fan diameter, or the fan speed increases. And the increase in the number of fans and the fan diameter leads to an increase in storage space, and the compactness of the refrigerator unit 4 cannot be achieved. In addition, the power consumption increases as the fan speed increases. In addition, the amount of heat generated by the current increases, so that the heat deterioration of the fan motor is accelerated.

Therefore, the heat exchange area of the condenser is made larger than that of the evaporator, the condenser makes the outflow / inflow surface of the outside air face the container wife surface, and the evaporator makes the inflow / outflow surface of the inside air face the horizontal plane. By doing so, the refrigeration unit 4 can be made compact by suppressing an increase in the fan air volume of the condenser.

Further, as shown in FIG. 7, the condenser fan 16 is disposed below the rear surface of the condenser 12 and below the heat insulating wall 63c with the fan shaft as a vertical direction. With such a configuration, the condenser cooling air is guided downward after passing through the condenser 12 so as to penetrate the end face of the container 3.

Further, with the above-described configuration, for example, the height of the refrigeration unit can be suppressed as compared with a configuration in which the condenser fan 16 and the condenser fan electric motor 14 are installed on the top of the refrigeration unit 4. Is discharged to the outside of the unit by the air guide 65 shown in FIG. With such a ventilation structure, for example, even if the refrigeration container 1 is loaded on the truck 2 and the truck engine is positioned in front of and below the refrigeration unit 4, the condenser cooling air is discharged to the truck engine side. As a result, it is possible to reduce the hot air around the truck engine from rising to the refrigeration unit 4 side.

Further, as shown in FIGS. 6 to 8, the condenser fan electric motor 14 is It is supported. As shown in FIG. 8, the bracket 60 is configured with the depth side supported by the casing 61 as a support shaft. The bracket 60 is configured to be pivotable downward by providing a pivot shaft at the rear side in the horizontal direction (arrow L in FIG. 8).

With such a configuration, the operator can easily replace or inspect the condenser fan motor 14 and the condenser fan 16 without removing the condenser 12. In this way, in the refrigeration unit 4, the maintainability of the condenser fan motor 14 and the condenser fan 16 is improved.

Further, as shown in FIG. 7, the evaporator 13 is supported by a mounting base 64. The mounting base 64 is installed on a heat insulating wall 63c constituting the casing 61. Further, the heat insulating wall 63c is formed so that the opening becomes larger toward the lower inside of the container in order to reduce the flow resistance of the internal air passing through the evaporator 13. Here, the mounting base 64 is configured to support the evaporator 13 with the upper part horizontal and to be installed on the heat insulating wall 63c with the lower part inclined according to the inclination of the heat insulating wall 63c! RU

By adopting such a configuration, for example, when the operator removes the evaporator 13 in order to replace or check the evaporator 13, the evaporator 13 can be prevented from slipping down. In this way, the maintainability of the evaporator 13 in the refrigeration unit 4 is improved.

Next, the ventilation structure of the condenser 12 of the refrigeration unit 4 will be described with reference to FIG. 2 to FIG. 5 or FIG.

As shown in FIGS. 2 to 4, the lower engine cover 68 is provided in front of the refrigeration unit 4. The lower engine cover 68 is configured to cover a substantially lower portion and a substantially upper portion of the lower portion 103 in the right center portion 102a where the engine 22 is disposed. In other words, the front side of the engine 22 and the upper front side of the fuel tank 23 are covered. The lower engine cover 68 forms a gap R with the fuel tank 23.

By adopting such a configuration, a certain distance is secured between the air guide portion 65 and the gap R in the height direction of the refrigeration unit 4. On the other hand, a constant distance is secured between the air guide portion 65 and the gap R in the width direction of the refrigeration unit 4. In this way, by preventing the condenser cooling air discharged from the air guide portion 65 from flowing back to the right central portion 102a through the gap R, the cooling performance and intake efficiency of the engine 22 are reduced in the refrigeration unit 4. Has improved. Further, as shown in FIG. 5, the Rajeta fan 26 is provided on the right side surface of the right center portion 102 a of the refrigeration unit 4, that is, the right side surface of the refrigeration unit 4. The cooling air sucked in by the Rajjtafan 26 is introduced into the right center portion 102a through the gap R, passes under the common frame 62 of the engine 22 and the generator 21 and passes through the introduction portion 32a near the partition wall 66 to the right. It flows into the central portion 102a and flows out into the opening 9 (arrow S in FIGS. 2 to 5 and 7).

By adopting such a configuration, the cooling air can be cooled in the order of low temperature power high temperature of the exhaust heat temperature of the generator 21 and the engine 22. Therefore, the cooling efficiency of the generator 21 is improved.

In addition, since the Raje-tafan 26 is provided in the central portion 102, the height of the refrigeration unit 4 can be suppressed.

Next, the configuration of the intake / exhaust system of the engine 22 will be described in detail with reference to FIG. 2 to FIG. 6 or FIG. 9 to FIG.

As shown in FIG. 5, the intake pipe 32 can suck a part of the cooling air by the Rajeta fan 26 by adopting such a configuration that introduces outside air from the opening facing the introduction portion 32a.

In addition, as shown in FIG. 5 or FIG. 6, the partition wall 66 is provided at the approximate center in the width direction of the central portion 102. The partition wall 66 separates the right center portion 102a where the engine system is disposed and the left center portion 102b where the refrigerant system is disposed. The muffler 43 is attached to the partition wall 66 above the left center portion 102b. The electrical component box 51 is arranged on the right side of the upper part 101.

With such a configuration, the muffler 43 and the electrical component box 51 can be isolated. In this way, the electrical component box 51 can be prevented from being affected by exhaust heat from the engine due to the muffler 43. That is, heat protection is realized in the electrical component box 51.

Further, as shown in FIGS. 2 to 4, the panel 67 is provided in front of the left central portion 102b where the refrigerant system is arranged. By adopting such a configuration that the mesh 67a that allows ventilation is formed, the left central portion 102b can be naturally ventilated without providing a fan or the like. In this way, in the refrigeration unit 4, the cooling efficiency of the refrigerant control device (for example, an electromagnetic valve or an electronic expansion valve) and the muffler 43 is improved. Further, as shown in FIG. 5, the exhaust pipe 42 is provided to exhaust the exhaust from the engine 22 to the outside. The exhaust pipe 42 discharges the exhaust from the muffler 43 to the outside through the exhaust tail pipe 44. In the upper part 101, the exhaust tail pipe 44 is configured between the condenser 12 and the electrical component box 51 in the lead straight direction. Further, as shown in FIG. 9, the exhaust tail pipe 44 has the exhaust direction as the back side of the refrigeration unit 4.

With such a configuration, the exhaust tail pipe 44 can be stored in the refrigeration unit 4, and the exhaust of the engine 22 can be discharged at the upper end of the refrigeration unit 4. The discharge direction can be opposite to the traveling direction of the truck 2 when loaded on the truck 2, for example. In this way, re-suction of engine exhaust is prevented in the refrigeration unit 4.

Further, as shown in FIGS. 9 and 10, the outlet portion of the exhaust tail pipe 44 is covered with a cover 70 at the ceiling portion of the refrigeration unit 4. This cover 70 is a cover with a simple structure that opens only in the exhaust direction. In addition, the exhaust tail pipe 44 is provided with a waterproof weir 71 on the periphery of the through portion of the casing 61 in the ceiling portion of the refrigeration unit 4. This waterproof weir 71 is provided in close proximity to the exhaust tail pipe 44.

By adopting such a configuration, intrusion of rainwater into the exhaust tail pipe 44 is prevented. Moreover, rainwater collected on the ceiling of the refrigeration unit 4 cannot enter the casing 61 from the periphery of the casing 61 through portion of the exhaust tail pipe 44. In this way, the refrigeration unit 4 prevents rainwater from entering.

Further, as shown in FIGS. 9 to 12, the exhaust tail pipe 44 is configured inside the casing 61. The exhaust tail pipe 44 has a vertical portion 44a disposed in the vertical direction between the condenser 12 and the electrical component box 51 (see FIG. 5). The vertical portion 44a is supported by the casing 61 in a vibration-proof manner. More specifically, the exhaust tail pipe 44 is supported on the casing 61 by a bracket 72 via a support material 73 and a coasting material 74.

With such a configuration, the bracket 72 supports the exhaust tail pipe 44 while absorbing the thermal deformation of the exhaust tail pipe 44 even when the exhaust tail pipe 44 is deformed due to aging or exhaust heat. can do. In this manner, in the refrigeration unit 4, the exhaust pipe 42 can be prevented from being damaged, and the durability is improved.

Further, as shown in FIG. 5, the exhaust tail pipe 44 is arranged in the horizontal direction below the condenser 12. It has a horizontal portion 44b disposed. Furthermore, as shown in FIG. 13, a drain outlet 45 is provided in the horizontal portion 44b. The drain outlet 45 is connected to the drain hose 46. Although not shown, the drain hose 46 is provided so that it can be drained outside the refrigeration unit 4.

Further, the drain water drain 45 is provided with a step so that the drain water can be captured. With such a configuration, even if the temperature of the exhaust tail pipe 44 decreases after the engine 22 is stopped and dew condensation water is generated inside the exhaust tail pipe 44, the drain outlet 45 Condensed water can be discharged to the outside of the refrigeration unit 4 quickly. In this way, the refrigeration unit 4 is prevented from malfunctioning due to the backflow of condensed water to the engine 22.

Next, the maintenance means of the engine 22 will be described in detail using FIG.

As shown in FIG. 14, the engine 22 is suspended from the refrigeration unit 4 by being suspended by a chain block 77 attached to the removable bracket 76 during maintenance. The detachable bracket 76 is formed of, for example, H-shaped steel, and is configured to be detachable to the upper end portion of the casing 61 with a bolt or the like. During maintenance, remove the bolts and replace them so that one end of the removable bracket 76 protrudes forward.

The common frame 62 is a common frame for the engine 22 and the generator 21. Here, the common frame 62 is formed with a horizontal mounting surface without unevenness.

With this configuration, the operator can easily move the engine 22 horizontally using the detachable bracket 76 and the chain block 7 7, so that the operator can pull it out of the refrigeration unit 4 or into the refrigeration unit 4. Can be pushed in. This exchange means can be applied not only to engine 22 but also to heavy objects such as generator 21 or compressor 11. In this way, maintainability is improved in the refrigeration unit 4.

Next, the operation unit 91 will be described in detail with reference to FIGS. 15 and 16.

As shown in FIG. 15, the refrigeration unit 4 is provided with an operation unit 91 on the right side surface. The operation unit 91 is arranged so that the lower side of the operation unit 91 is positioned near the center line of the refrigeration unit 4.

With this configuration, for example, even when the refrigeration unit 4 is loaded on the truck 2, the operator can easily operate the operation unit 91 from the driver's seat and from the side. . Further, with the above-described configuration, for example, even when the refrigerated container 1 is buried by snowfall, the operation unit 91 is not buried. That is, the operator can easily operate the operation unit 91. Thus, the operability of the refrigeration unit 4 is improved.

In addition, as shown in FIG. 15, the frame 6 is provided with a ladder portion 92 and a grip portion 93 on the right side surface. In the ladder portion 92, the lower end force of the frame 6 is also provided up to the operation portion 91. In addition, the grip portion 93 is provided on the frame 6 so as to be positioned in the vicinity of the operation portion 91. Note that the ladder part 92 is simple enough to allow an operator to step on the foot.

With this configuration, for example, even when the refrigeration unit 4 is loaded on the truck 2, the operator can easily approach the operation panel 94 and operate it. In this way, the operability of the refrigeration unit 4 is improved.

Further, as shown in FIG. 16, the operation section 91 constitutes an operation panel storage chamber 95. The operation panel storage room 95 has a partially opened depth surface. An operation panel 94 is fitted into the opening surface. By storing the operation panel 94 in the operation panel storage chamber in this way, it is possible to prevent sunlight from being reflected on the surface of the operation panel 94 or the scenery behind it from being reflected. In this way, visibility is improved in the operation unit 91.

Further, with the above-described configuration, the operation panel 94 can be double waterproofed by the waterproof treatment of the operation panel 94 and the waterproof treatment of the operation panel storage chamber 95. In this way, the operation unit 91 is designed to prevent rainwater intrusion!

Further, as shown in FIG. 16, the operation panel storage chamber 95 is covered with a door 96 on the surface. The door 96 is configured such that its upper end is pivotally supported with respect to the side plate so that it can be opened and closed upward.

With such a configuration, for example, when an operator opens the door 96, the door 96 becomes eaves and can prevent intrusion of rainwater. Also, if the operator releases the hand, it closes with the dead weight of the door 96, thus preventing forgetting to close.

As shown in FIG. 16, more specifically, the operation panel 94 is installed in the opening portion opened in the depth surface of the operation panel storage chamber 95 via the packing 99 and the grommet 100. In other words, packing 99 is provided on the periphery of the mounting surface of the operation panel 94 to the operation panel storage chamber 95, and a grommet is attached to the bolt that fixes the operation panel 94 to the operation panel storage chamber 95. 100 is fitted to support vibration proofing. On the other hand, the door 96 is attached to the periphery of the opening opened on the surface of the operation panel storage chamber 95 via the packing 98.

With this configuration, the operation panel 94 can be sealed at both the door 96 and the periphery of the operation panel 94. In this way, rainwater intrusion is prevented in the operation panel 94.

In addition, as shown in FIG. 16, the door 96 is provided with a transparent window 97 at a substantially central portion.

With such a configuration, the operator can confirm only the display on the operation panel 94 without opening and closing the door 96. In this way, the operability is improved in the operation unit 91.

Next, the configuration of the fuel tank 23 will be described in detail with reference to FIGS. 2 to 4, FIG. 17 and FIG.

As shown in FIGS. 2 to 4, the fuel tank 23 is disposed in the lower portion 103 of the casing 61. The lower engine cover 68 covers the lower half surface of the central portion 102 and the substantially upper portion of the lower portion 103 on the surface of the refrigeration unit 4.

By adopting such a configuration, the lower engine cover 68 can be made lighter than in the case where the entire surface of the lower part 103 is covered. That is, the operator can easily detach the lower engine cover 68. In this way, the maintainability of the refrigeration unit 4 is improved.

Further, with the above-described configuration, the upper part of the fuel tank 23 can be blinded with only one lower engine cover 68 as compared with a case where the entire surface of the lower part 103 is divided and covered with a cover. In this way, the number of parts of the refrigeration unit 4 is reduced.

Further, as shown in FIG. 17, the fuel tank 23 is carried by a frame 35 having a frame shape around the fuel tank 23. The frame 35 is configured to be pivotable up and down with respect to the casing 61 by pivotally supporting the depth side at the lower end (the back side of the refrigeration unit 4) with a support shaft (arrow M in FIG. 17).

With such a configuration, during manufacturing, the assembly operator pivots the rear part while holding the fuel tank 23 on the frame 35, and lifts the fuel tank 23 to fix the front part. The fuel tank 23 can be attached to the casing 61 by an easy process. In this way, the assemblability is improved when the refrigeration unit 4 is manufactured.

Further, with the above-described configuration, the height of the fuel tank 23 can be made equal to the height of the lower portion 103 of the casing 61 even when the oil filler port 36 is provided in the upper portion of the fuel tank 23. In this way, in the refrigeration unit 4, the volume of the fuel tank 23 is increased. If the common frame 62 is provided with a projecting opening of the oil filler port 36, as shown in FIG. 7 or FIG. 8, the fuel tank 23 even if the common frame 62 overlaps the oil filler port 36 in the height direction. Can be installed. Accordingly, the height of the refrigeration unit 4 can be suppressed as compared with the case where the common frame 62 is raised by the height of the oil filler port 36.

Further, with the above-described configuration, when the fuel tank 23 is inspected, the operator releases the fixing of the front portion of the frame 35 and pivots downward so that the upper portion of the fuel tank 23 is directed forward. Can be made. That is, the operator can easily inspect the upper part of the fuel tank 23. In this way, in the refrigeration unit 4, the maintainability of the fuel tank 23 is improved.

In addition, as shown in FIG. 18, the fuel tank 23 includes a strainer 27 inside. The strainer 27 is provided at the tip of the oil feed pipe 28 on the fuel tank 23 side. The strainer 27 is recessed through an elastic body 29 in a recess 23 a formed at the bottom of the fuel tank 23. With such a configuration, the feed pump 24 can suck the fuel to the bottom of the fuel tank 23. In this way, the effective volume of the fuel tank 23 is improved.

In addition, with the above-described configuration, even when vibration is applied to the fuel tank 23 or when there is a dimensional error in the strainer 27, the elastic body 29 causes vibration between the bottom of the fuel tank 23 and the strainer 27. 'I can alleviate the collision. In this way, the reliability of the fuel tank 23 is improved.

Next, the storage of the power cable 52 will be described in detail with reference to FIG.

As shown in FIG. 19, the refrigeration unit 4 is provided with a power cable 52 so that a commercial power source can also supply power. The refrigeration unit 4 may be driven by the supply of an external commercial power source or the like through the power cable 52 when it is transported by train or ship. The power cable 52 is located at the lower right of the casing 61 when not in use. The storage box 54 is stored in a squeezed state.

The power cable 52 has a power plug 53 at the tip. In the power cable storage box 54, a storage cylinder 55 is provided at the left end. The storage cylinder 55 is provided with its tip inclined upward. When the power cable 52 is stored in the power cable storage box 54, the power plug 53 is stored in the storage tube 55.

By adopting such a configuration, it is possible to prevent water from accumulating inside the power plug 53 when not in use, for example, in rainy weather.

Next, the defrost heater 80 will be described in detail with reference to FIG. 20 and FIG.

As shown in FIG. 20, a defrost heater 80 is provided for the purpose of preventing frost formation of the evaporator 13. In FIG. 20, the evaporator 13 is illustrated with the fins and tubes omitted to facilitate the component force. The defrost heater 80 is formed of a round bar-like heating element that generates heat when energized.

As shown in FIG. 21, the evaporator 13 has an evaporator frame 13a at both ends and a notch 13b formed at the lower end of the fin (not shown). The notch 13b has a semi-long hole shape that matches the cross-sectional shape of the defrost heater 80. The defrost heater 80 is attached by being fitted into the notch 13b.

With such a configuration, for example, when replacing the defrost heater 80, the operator can easily push the defrost heater 80 from the evaporator 13 by simply depressing or fitting the defrost heater 80 from the notch 13b. Detachable. In this way, the maintainability of the defrost heater 80 is improved.

Further, as shown in FIGS. 20 and 21, the defrost heater 80 has a U-shaped folded configuration on one side.

With such a configuration, the wiring of the defrost heater 80 can be concentrated on the other side. In this way, workability is improved when the refrigeration unit 4 is manufactured or when the defrost heater 80 is replaced.

Further, as shown in FIGS. 20 and 21, the defrost heater 80 is fixed at both ends by a pressing member 81 from the lower side of the evaporator frame 13a by V and below.

With this configuration, after installation, the defrost heater 80 drops from the notch 13b. Is prevented. That is, a plurality of defrost heaters 80 can be fixed and prevented from falling off with a simple configuration. In this way, the safety of the defrost heater 80 is improved.

Next, the refrigerant circuit configuration of the refrigeration unit 4 will be described in detail with reference to FIG.

As shown in FIG. 22, in the refrigerant circuit of the refrigeration unit 4, the evaporator 13, the evaporator fan 17, and the evaporator fan motor 15 are arranged inside the container 107, and the rest are arranged outside the container 106. In addition to the compressor 11, the condenser 12, the expansion valve 113, the receiver 19, and the evaporator 13, the refrigerant sucked between the evaporator 13 and the compressor 11 is used as a device constituting the refrigerant circuit. An accumulator 117 for storage or gas-liquid separation and an opening adjustment valve 116 for adjusting the refrigerant circulation amount are provided. The evaporator 13 includes two heat exchanges, that is, the evaporator 13m and the supercooling heat exchange 1311. Further, the supercooling bypass path 112 short-circuits the condenser 12 outlet and the receiver 19 inlet via the solenoid valve 111. Further, the suction bypass path 114 is configured in parallel with the opening degree adjustment valve 116 via the electromagnetic valve 115.

With such a configuration, the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the condenser 12 and dissipates heat to the outside air to condense. Then, the liquefied refrigerant flows into the receiver 19 through the path 112 and is rapidly reduced in pressure by the throttle action of the expansion valve 113 and flows into the evaporator 13 as a mist. Then, the inside of the container 3 is frozen and refrigerated by the endothermic action accompanying the evaporation of the refrigerant, and the vaporized refrigerant is sucked into the compressor 11.

As shown in FIG. 22, the supercooling heat exchanger 13η is configured as a part of the evaporator 13 disposed in the container interior 107. Supercooling is the action of cooling the high-pressure, high-temperature refrigerant liquid condensed in the condenser 12. The supercooling effect can reduce the inlet enthalpy of the evaporator 13 and increase the evaporator capacity.

And don't need supercooling!ヽ In the case of low load operation (for example, refrigeration operation), it is possible to perform operation in which the solenoid valve 111 is turned on and the refrigerant is not passed through the supercooling heat exchanger 13η in the supercooling bypass path 112.

By adopting such a configuration, it is possible to omit the arrangement of a separate supercooling heat exchanger (for example, a supercooling heat exchanger that exchanges heat with the suction refrigerant that is installed on the outside 106). In this way, frozen Unit 4 saves space on the outside 106!

In addition, since the entire amount of circulating refrigerant is supercooled with the low-temperature air inside the container 107, refrigeration efficiency is better than when the supercooling refrigerant is branched.

Further, as shown in FIG. 22, the opening degree adjustment valve 116 adjusts the refrigerant circulation amount of the entire refrigerant circuit by adjusting the amount of refrigerant sucked by the compressor 11. Refrigeration operation is operated with less refrigeration capacity than refrigeration operation. Therefore, during the refrigeration operation, the solenoid valve 115 is closed and the operation is performed only with the refrigerant amount adjusted by the opening adjustment valve 116. On the other hand, during the refrigeration operation, since a large refrigeration capacity is required, the solenoid valve 115 is opened and the refrigerant circulation amount is secured by using both the bypass path 114 and the opening adjustment valve 116 path.

In this way, in the refrigeration operation that requires a large amount of refrigerant circulation, the bypass path 114 is also used, and in the refrigeration operation that requires a small amount of refrigerant circulation, the opening adjustment valve 116 can be adjusted. By doing so, both responsiveness and accuracy of opening adjustment are improved.

Here, the refrigeration operation is an operation that keeps the internal air temperature below zero degrees, and the refrigeration operation is an operation that keeps the internal air temperature higher than zero degrees (= a low temperature state where moisture does not freeze).

Next, the two-temperature zone container 7 will be described in detail with reference to FIGS. 23 to 25.

As shown in FIG. 23, the two-temperature zone container 7 is a container 3 having a room of two different temperature zones, ie, the front chamber 3a and the rear chamber 3b. The front chamber 3a is disposed on the refrigeration unit 4 side of the container 3 for refrigeration. The front chamber 3a is directly cooled by the cooling air of four refrigeration units. On the other hand, the rear chamber 3b is disposed on the door 5 side of the container 3 for refrigeration. The rear chamber 3 b is cooled by cooling air whose temperature is controlled by the rear chamber unit 130.

Further, as shown in FIG. 24, the rear chamber unit 130 is composed of a heating / mixing chamber 126 arranged at the left and right of the front chamber 3a cold air suction chamber 125 in the center in the width direction of the container 3. . The blower fan 122 is provided at the opening of the front chamber 3a of the duct 120 and the cool air suction chamber 125. The blower fan 121 is provided at the suction opening of the heating / mixing chamber 126. With such a configuration, the frozen air sent from the front chamber 3a to the rear chamber 3b via the duct 120 and the air heated by the heater unit 123 of the mixing chamber 126 are heated. Heating · Mixed in the mixing space before the outflow part to the air duct 129 in the mixing chamber 126, and the mixed air is supplied to the floor surface of the rear chamber 3b through the air duct 129.

Hereinafter, the configuration of the rear chamber unit 130 will be described in detail.

As shown in FIG. 24, inside the duct 120 and the front chamber 3a cold air suction chamber 125, refrigerated air having a temperature lower than that of the refrigerated air circulating in the rear chamber 3b flows. Therefore, the duct 120 and the front chamber 3a cool air suction chamber 125 are configured to surround the entire periphery with a heat insulating material (not shown). With such a configuration, condensation on the duct 120 and the rear chamber 3b side of the front chamber 3a cold air suction chamber 125 can be prevented. In this way, dew condensation on the ceiling of the rear chamber 3b is prevented and the cargo is prevented from getting wet.

Further, as shown in FIG. 25, the heating / mixing chamber 126 has a drain pan 127 at the bottom. This is because in the heating / mixing chamber 126, the frozen air in the front chamber 3a sucked from the duct 120 and the refrigerated air in the rear chamber 3b sucked by the blower fan 121 are mixed, so that condensed water is generated.

With such a configuration, the drain pan 127 can guide the generated condensed water to the air guide duct 129 and guide the air from the air guide duct 129 to the floor of the container 3. Condensed water guided to the floor is drained outside the container 3 drainage groove (not shown). In this way, cargo wetting is prevented in the rear chamber 3b.

[0057] Further, as shown in FIG. 24, each of the blower fans 121, 122, 121 is arranged in a row in the width direction of the container 3 as a total of nine fans by arranging three fans with the same diameter in a row. .

With such a configuration, each fan can be made small, and thus the height dimension of the rear chamber unit 130 can be suppressed. In this way, the effective height for loading and unloading is increased in the rear chamber 3b.

In addition, the heater unit 123 shown in FIGS. 24 and 25 has a configuration in which the heating element 140 and the support member 141 are integrated.

With such a configuration, the operator can easily attach and detach the heater unit 123 at the time of manufacturing or replacement of the heater unit 123. In this way, in the heater unit 123, assembly and maintenance are improved. Further, as shown in FIGS. 24 and 25, a shutter 128 is provided in front of the blower fan 122 of the duct 120. The shutter 128 is made of a plate-like elastic body, and its upper part is fixed to the upper side of the duct 120. The shutter 128 is configured so that a weight is attached to the lower part and is in close contact with the lower side.

By adopting such a configuration, the shutter 128 can rotate to the blower fan 122 side at the lower part. That is, when the refrigeration air in the front chamber 3a is sucked by the blower fan 122, the shirt 128 is blown up and the front chamber 3a communicates with the front chamber 3a cool air suction chamber 125. When the blower fan 122 is stopped, the shutter 128 is released. The front chamber 3a is closed and is shut off from the front chamber 3a cold air suction chamber 125. In this way, in the duct 120, the refrigerated air in the front chamber 3a is prevented from naturally flowing into the rear chamber 3b except for forced suction by the blower fan 122.

[0060] The present invention can be used for a refrigeration container having a refrigeration unit on the open end of the container.

Claims

The scope of the claims

[1] In a refrigeration container that controls the temperature inside the container with a refrigeration unit that circulates refrigerant in the compressor, the condenser outlet path is divided into two, and one path is connected to the expansion valve via an on-off valve, and the other path Is connected to the expansion valve after passing through a part of the path of the expansion section and the evaporator in this order, and the open / close valve is closed during the supercooling operation.

[2] In a refrigeration container that controls the temperature in a container with a refrigeration unit that circulates refrigerant in a compressor, the compressor suction path is provided in two paths in parallel, and one path is connected to the compressor via an on-off valve. The other path is connected to the compressor via an opening adjustment valve, and the open / close valve is opened during a freezing operation, and the open / close valve is closed during a chilled operation. .