JP2010530949A - Refrigerated containers for land, road and rail vehicles - Google Patents

Abstract

The present invention relates to a refrigerated container for land, roads, and railway vehicles, and a chute having a horizontal wall is formed on the inner side of the rear side of the refrigerated container vertically and greatly over the width of the container. On the wall, warmed refrigerated air collected under the roof area of the container can be supplied to a chute with downward deflection, at least one port having an annular part inserted therein, The refrigerated air that is formed on the horizontal wall and is warmed can be guided to the heat exchange surface of the evaporator of the refrigerant circuit, and the heat exchange surface is chuteed through the blower through the flow cross section of the annular part The refrigerated air that protrudes into the interior and is cooled by the heat exchange surface is led back to the floor area of the refrigeration container from the bottom of the chute. In accordance with the present invention, a lateral flow director for warmed refrigeration air, which is guided inside by a blower, is introduced into the horizontal wall to introduce warmed refrigeration air laterally into the flow cross section of the annular part. It is provided on and on the side surface.

Description

  The present invention relates to refrigerated containers for land, road, and rail vehicles.

  Such a container is basically formed in a rectangular shape and has, for example, a length of 40 feet (approximately 14 m) in the longitudinal axis. These are typically mounted on the vehicle such that the longitudinal axis of the container is parallel to the longitudinal axis of the vehicle.

  The container door is installed at one end, while the other end carries a refrigeration unit that is inserted through a notch. Generally, the refrigeration unit is bolted, often removably, to a flange that surrounds the outer end of the notch.

  The inner floor of the container is provided with a ridge in the longitudinal direction so as to form a longitudinal groove for introducing frozen air. The upper surface of the longitudinal basket is usually a straight T-shape that supports the cargo in the container.

  The end door area is provided with means to ensure that the refrigerated air heated by the cargo rises up to the roof of the container, which has not been done so far through the cargo. A height mark or other means to adjust the height of the cargo, the warmed air that exists between the cargo and the roof of the container is returned to the end of the container opposite the end door, It is provided so that it can be returned to the refrigeration unit.

  The refrigeration unit forms a vertical chute inside its corresponding end of the container, and the chute extends the circulation of the frozen air to form a closed circuit as described above.

  Protruding into the chute is the heat exchange surface of the evaporator of the refrigerant circuit. The refrigerant circuit has a normal structure, and typically includes, in addition to the evaporator, a compressor, a condenser, and expansion means that are connected in this order to the evaporator in a closed circuit.

  The chute is normally covered by a double metal sieve in the form of an aluminum sheet, but allows air to pass through, for example as a safety guard against injuries caused by falling of external objects and unwanted human access. . Although present between the covers, the surface of the front side wall and the surface of the inner wall of the container is a plenum that is released to the storage space of the container. Inside this storage space, the flow of warmed air returning is diverted to the chute through the cover. The plenum extends substantially or completely over the full width of the container.

  Under the cover, clearly spaced from the cover, the chute is separated by a horizontal wall, where the port is a round hole associated with the container that extends downward for warmed refrigerated air. Usually configured asymmetrically. However, in special cases it is just possible to provide just one or more ports.

  Inserted into each port in the horizontal wall is an annular part that is secured to the horizontal wall by an external flange-type structure on which it is placed and secured for purpose. The annular part is fastened on the horizontal wall in order to function as an air feeder for the axial blower in each case. An axial blower directs rising warmed refrigerated air to the heat exchange surface of the evaporator. The result is the rising warmed refrigerated air heat that is released into the refrigerant in the refrigerant circuit, which is now suitable for freezing again in the longitudinal direction on the container floor. Returned to the groove.

  To optimize the use of the space available in the refrigeration unit and in particular the chute, with a simple design, in particular by selecting as large as possible the flow porting section of the annular part for the rising warmed refrigeration air Various attempts have been made early on. However, the maximum diameter of the cross section is the distance between the inner surface of the container end opposite the end door and the surface of the adjacent wall opposite the cargo, and the interior of the chute derived therefrom. It is determined by the dimensions. Thus, until now, the outer flange-type structure of the annular part has been configured on both sides, but the axial direction of the container so as not to restrict the flow cross section of the internal opening of the annular part in the axial direction of the container. Was not configured.

  The present invention is based on the object of further improving the efficiency in freezing the cargo of a refrigerated container with a simple design.

  This object is achieved by the features of claim 1.

  It was shown by comparative tests that these characteristics made it possible to increase the efficiency considerably. Depending on the application involved in practice, this efficiency drives the low energy consumption required for power electric axial fans and the improved lateral osmotic flow of cargo with refrigerated air as well as axial fans. It can be used for various purposes including a smaller power stage for the motor to be driven. In particular, it has now been discovered that refrigeration is now more uniform laterally in the container than before. The explanation for this surprising effect is that the refrigeration air in the side area of the container cargo space is now more circulated than before because it has remained more or less less than before . The flow profile in the returning flow of warmed refrigeration air is now less axial, i.e. more uniform.

  As can be read from claim 2, the introduction of warmed air can be made uniform in the flow cross section of the annular part which reduces the resulting noise, and these effects are realized even more as read from claim 3. One special effect according to claim 3 is to capture more of the warmed air that is removed more radially.

  As can be read from claim 4, it can now be avoided or at least reduced that the free edge of the lateral flow director causes turbulence as an obstacle to the inflow of warmed refrigerated air. As can be seen from claim 5, this effect is now more reduced in avoiding dead space in the flow, but at the same time, at least in the form of an outer part of the annular part, the flange type of the annular part Support can be obtained at the horizontal wall of the chute.

  Claim 6 is based on the idea of arranging a flow director and, if possible, a flange-type support, so that the valuable space required to accommodate the cargo is no longer blocked.

  Claim 7 details the idea of claim 6, but the diameter of the flow cross section of the annular part between the inside of the front wall of the chute facing the cargo space and the front surface of the back wall of the container is: It is selected as large as possible.

  Usually, the annular part constitutes a cylindrical sleeve, and from its top, the secondary part of the annular flange protrudes at right angles on both sides for fixing to the horizontal wall, and the flow cross section of this sleeve is annular. is there. Such an annular internal cross section is also preferred within the scope of the invention, in particular in the arrangement of claim 7. However, this is not limited to interlocking with claim 7 and does not exclude a sleeve portion having a cross section other than an annular shape within the scope of the present invention. In particular, in this case, preferably a curved flat flow cross-section, e.g. an oval internal contour or a flat that extends conveniently laterally in the chute in order to avoid affecting the use of cargo space. Being a face is interesting.

  Claim 8 shows how the invention can be realized in a particularly simple manner by means of a modified essential annular part with several structural means, as a result, as in the known case It shows how efficient it can be for a surprisingly large increase in applications.

  Known cylindrical annular parts are usually made of aluminum or an aluminum alloy. As can be read from claim 9, the three-dimensional external shape that provides interlocking with the flow director also stabilizes the thin insert sleeves in the horizontal wall in a positional relationship, so that within the scope of the present invention, the thin Injection molded plastic may be provided (see claim 10).

  The features of claim 11 are known per se, but the significance of claim 11 is that a two-stage blower powered without gears is now the scope of the present invention as a particularly direct problem-solving technique. It can be used within.

  Basically, any known type of blower can be used in the scope of the present invention, for example, a radial blower including a special adapter can be used, and for this reason it is known in the scope of the present invention. It is preferable to use an axial blower.

  One such axial blower, however, is more conveniently adapted within the scope of the present invention to further improve performance efficiency by making minor changes in shape.

  A commonly used axial blower simply comprises straight blades that thicken towards the shaft for stabilization. Instead, according to the present invention, as given in claim 13, preferably not only to improve the dimensional stability of the blades, as in the special features of claims 14-18, but also if necessary It is preferable that the shape function so as to bring about a change in the thickness of the film. What is further reduced is, in particular, the noise generated as well as the driving force of the corresponding blower. Also contributing to such a positive effect is that the warmed refrigerated air sent by the axial blower blades now has some time delay due to the corresponding blades spreading radially outwards. It is the fact that it is received.

  Claim 19 first states in the preamble the restrictions on the inherited features in the normal annular part. In a further development as read from claim 19 and their preferred further aspects in claims 20 and 21, preferred embodiments of the annular part within the scope of the invention are detailed. In order to support the annular part and to secure the annular part to the horizontal wall of the shaft when necessary, it is possible to construct the flange structure according to the invention, as the flow director now requires in claim 21 In that case, it is arranged in a radial inner space with respect to the side of the sleeve and, in order to maximize flow, along the full axial width of the inner cross section of the chute, in the corresponding side flange structure It is directly connected to the front side of the back wall of the container that continues radially so as to return further in the direction of the horizontal wall. Such a flange structure is advantageously solved by the tip.

  A surprising increase in efficiency by simply replacing the conventional annular part (also used by the applicant so far) is the comparative test described below with the annular part according to the invention detailed by the exemplary configuration. It will become clear from the explanation.

  These comparative tests, by way of example, show that the power consumption (in watts) of an electric power axial fan can be changed according to the present invention by simply replacing a known annular part with a novel annular part. To the extent that it can be changed.

  As another example, the interaction with the special shape of the blades of an axial blower has been demonstrated, where non-target comparative test results have been obtained this time.

  The axial blower still operated with continuous blades having pitches of 19 °, 22 °, and 25 ° (standard).

  In all cases, the motor that powers the axial blower was a gearless electric motor that switched between low and high speeds at 2 and 4 poles, respectively.

  The test results are as shown in [Table 1].

  This means that the power consumption of the axial blower can now be reduced from 13% to 40% without considering any adaptation of the axial blower blade shape in the high speed mode (460V, 60Hz). It has already been made clear.

The present invention will now be described in detail using an exemplary embodiment with reference to the following diagram.
FIG. 1 is a partial cross-sectional view of the back of a container along the longitudinal axis. FIG. 1A is a partial cross-sectional view at the same height as that shown in FIG. 1 but at an angle perpendicular to the horizontal axis of the container. FIG. 2A is a view seen from the top to the bottom. FIG.2 (b) is the figure seen from the bottom to the top. FIG. 2 (c) is a cross-sectional side view of the annular component used in the assembly as shown in FIGS. 1 and 1 (a). FIG. 3 is an isometric view of the blade ring of the axial blower used in the assembly as shown in FIGS. 1 and 1 (a).

  Referring to FIG. 1, it is shown how the end of a container includes a floor panel 2, a roof panel 4, and a container back wall 6. On the upper surface of the floor panel 2, a ridge is formed in the longitudinal direction of the container, and a groove (not shown) is formed between the ridges in order to direct the frozen air.

  The back wall 6 includes a notch 10 that spans virtually the entire height and likewise more or less the entire width, through which the refrigeration unit 12 is inserted into the interior of the container.

  The outer wall 14 of the refrigeration unit 12 is a functional extension of the back wall 6 of the container, which can be considered functionally identical to the outer wall 14.

  Facing the container's cargo space 16 in this arrangement, the refrigeration unit 12 forms a vertical chute where warmed refrigeration air is directed to the refrigeration unit 12 on the rear side of the container. The lower part of the chute 18 is tapered in the axial direction, thereby creating a storage space 20 for the main functional elements of the refrigeration unit 12 in line with the outside of the container back wall 6. Above the chute for a single point of importance within the scope of the present invention, the chute 18 extends toward the inside of the outer wall 14 of the refrigeration unit 12 which functions as the back wall of the container as described above.

  Although the functional elements of the refrigeration unit located in the storage space 20 are conventional, i.e. consistent with any known assembly, the key to the present invention is the heat exchange of the refrigeration unit evaporator. That is, the surface 22 protrudes from the expanded portion of the chute 18.

  At the heat exchanging surface 22 in the chute 18, the warmed refrigerated air in the chute is cooled to a low operating temperature and flows into the longitudinal groove between the undersides of the constricted portion of the chute 18. The arrows indicate the circulation of the frozen air in FIG. The refrigerated air flows upward from the longitudinal groove along the entire length of the cargo space 16 surrounding the cargo to be collected at the bottom of the roof panel 4 and after collecting heat from the cargo space 16 and the cargo. The chute 18 is returned to the expanded part. A setting 24 roughly located on the top surface (or somewhat below) of the chute 18 ensures that the plenum 26 remains free to receive the refrigerated air warmed at the bottom of the roof panel 4. .

  At the same height as setting 24 or somewhat higher, grating 28 is usually on the upper surface of the widened portion of chute 18 to prevent external objects or clumps from entering chute 18. It extends. In addition, the lattice 28 is a safety guard that prohibits access to the chute 18 from various directions from above to below. The cargo space 16 is formed by a front side wall 30 of the refrigeration unit 12 that is substantially planar and extends perpendicular to the height and width of the container in accordance with the dimensions of the notch 10, Therefore, it continues in parallel with the outer wall 14 constricting the internal structure of the chute 18 between the upper part and the bottom part of the chute 18.

  What is clearly shown is that the horizontal wall 32 is located at the lower part of the lattice 28 parallel to the horizontal wall 32 (in this embodiment, it is roughly located 20 cm to 30 cm below). ). In this arrangement, the plenum 34 is disposed on the one hand between the front side wall 30 and the outer wall 14 and on the other hand between the grid 28 and the horizontal wall 32, and the chute 18 for receiving warmed refrigeration air. At the top. As shown in FIG. 1 (a), the plenum 34 extends between the side walls that extend over the entire width within the range indicating the width of the notch 10. In this arrangement, the side spacing is kept sufficiently small so that it can be ignored for all practical purposes.

  The same assembly is provided on the left and right of the longitudinal center line (imaginary line 36 in FIG. 1 (a)), only one of which will be discussed in detail, while the other is It is envisioned to be mirror image symmetric through a central line or corresponding central plane of the container.

  Accordingly, what is shown in FIG. 1 is exactly the left-hand portion shown in FIG.

  The horizontal wall 32, as shown here, is clamped in the center, but in this case on the left side, by a port 38 having an annular internal cross section.

  Inserted into the port 38 of the horizontal wall 32 from top to bottom is an annular piece 40 which will now be described in detail with reference to FIGS. 2 (a) -2 (c).

  The annular part 40 includes a cylindrical sleeve portion 42 inserted into the port 38, and sends the refrigerated air heated as seen from the flow section to the axial blower 44. The blower 44 includes an electric power gearless two-pole and four-pole motor 46 for selectively driving the axial blower air 44 at a low speed or a high speed. That is, the axial blower 44 that is normally driven by the electric motor 46.

  Referring now to FIG. 3, it is shown how the axial blower 44 also characterizes the ring-shaped vane 48, the novel structure of which will now be described in detail in the context of the present invention. Let's go.

  Initially, however, the annular part 40 provided with a seat by the sleeve 42 gives more consideration to the structure on the upper surface of the sleeve 42 as shown in FIGS. 2 (a) to 2 (c). Will.

  The complete annular part 40 is an indispensable injection mold formed with a wide choice of plastic, polyamide, or polypropylene, which is reinforced for the purpose in any case by glass or carbon fiber cited just as an example. It is a part. By selecting such a material, it is possible to form a wall with a thickness of only 1.5 mm, which is sufficient when compared with a normal wall with a thickness of 2 nm when formed with aluminum or an aluminum alloy, which is a considerable cost reduction. It becomes possible.

  The sleeve 42 has a circular flow cross-section 50 of maximum diameter, where the maximum is the diameter of the flow cross-section 50 between the inside of the outer wall 14 of the refrigeration unit 12 and the inside of the front wall 30. It means that it corresponds to the sum of twice the wall thickness of the sleeve 42 in the interval. As is apparent in the direction of this interval in FIG. 2A, this corresponds to twice the dimension of the flow cross section of the diameter D and the dimension d of the sleeve wall thickness.

  The upper surface of the sleeve 42 is then shaped into a lateral flow director 52 that extends over the full width of the chute 18 by means of a curve that has a continuous opening in both sides, ie in the horizontal direction of the container or parallel to its end. It is changing. Each side flow director 52 protrudes radially laterally by a tip 54, which tip 54 defines a free edge in the horizontal wall 32 and the inflow direction of air, as can be seen clearly from FIG. 2 (c). In the direction of the surface of the top to avoid, it is bent roughly inward in an annular shape. In addition, the protrusion 54 is supported by the upper surface of the horizontal wall 32, on which the protrusion 54 also functions as a flange-type fastener. For this purpose, the free edge 56 of each tip 54 can be arranged (not shown), for example to engage a support groove in the upper surface of the horizontal wall.

  In conclusion, FIG. 3 shows how the fan ring 58 of the axial blower 44 is preferably adapted.

  The fan ring 58 includes a hub 60 that can be secured to the output shaft of the drive motor 46 using a clip 62.

  As is clear from the isometric view of FIG. 3, the blades 48 of the axial blower 44 that are concavely curved in the transport direction are evenly distributed with respect to the periphery of the hub 60, and the blades 48 are also shown in FIG. Although it is bent all over in the direction of rotation indicated by the arrow in 3, the carrying direction is considered to pass through the plane of the drawing.

2 Floor panel 4 Roof panel 6 Back wall 8 畝 10 Notch 12 Refrigeration unit 14 Outer wall 16 Cargo space 18 Chute 20 Storage space 22 Heat exchange surface 24 Setting 26 Plenum 28 Grid 30 Front wall 32 Horizontal wall 34 Plenum 36 Virtual line 38 Port 40 annular part 42 sleeve 44 axial blower 46 electric motor 48 blade 50 flow cross section 52 side flow director 54 protrusion 56 free edge 58 fan ring 60 hub 62 clip

Claims (21)

A refrigerated container for land, road and rail vehicles
Inside the rear side of the refrigerated container is formed a chute (18) that extends vertically and greatly across the width of the container and has a horizontal wall (32), on the horizontal wall (32), Warmed refrigerated air collected under the roof area of the container can be supplied to the chute (18) with downward deflection;
At least one port (38) with an inserted annular part (40) is formed in the horizontal wall (32), and the warmed refrigerated air passes through the heat exchange surface (22) of the evaporator of the refrigerant circuit. )
The heat exchanging surface projects through the blower (44) into the chute (18) through the flow cross section of the annular part;
The frozen air cooled by the heat exchange surface is led back to the floor area of the refrigeration container from the bottom of the chute,
In order to introduce the warmed refrigerated air laterally into the flow cross-section of the annular part (40), the flow director (52) for the warmed refrigerated air led inside by the blower (44) Is provided on and on the side of the horizontal wall (32),
A freezing container characterized by that. The refrigeration container according to claim 1,
Each of the lateral flow directors (52) is configured to be bent.
A freezing container characterized by that. The refrigeration container according to claim 2,
Each of the lateral flow directors (52) is preferably released laterally outwardly, like an open flower,
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 3,
The lateral flow director (52) is curved back toward the horizontal wall (32) of the chute (18);
A freezing container characterized by that. The refrigeration container according to claim 4,
The edge of the back curve is supported by the horizontal wall (32),
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 5,
The space between the lateral flow directors (52) on opposite sides facing the cargo space (16) of the container is at least partially, preferably completely open,
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 6,
The space between the lateral flow directors (52) on both sides facing the cargo space (16) of the container is at least partly formed by the back wall (6, 14) of the container,
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 7,
The lateral flow director (52) is an indispensable component of the annular part (49),
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 8,
The annular part (40) and / or the lateral flow director (52) is formed by injection molded plastic,
A freezing container characterized by that. In the refrigeration container according to claim 8 or 9,
The annular part (40), together with the lateral flow director (52), comprises a dimensionally thin chamber.
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 10,
The electric motor (46) of the axial blower (44) is a 2-pole and 4-pole gearless electric motor,
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 11,
Each of the blowers (44) is an axial blower,
A freezing container characterized by that. The refrigeration container according to claim 12,
The blades of the axial flow fan (44) draw a concave curved surface in the carrying direction,
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 14,
The lateral flow director (52) protrudes from 2 cm to 5 cm, preferably 3 cm, from the upper plane of the horizontal wall (32) of the chute (18).
A freezing container characterized by that. The refrigerated container according to claim 13 and 14,
The depth of the concave surface configuration of each of the blades (48) is 1/4 to 1/2, preferably 1/3 of the height of the protruding portion.
A freezing container characterized by that. In the refrigeration container according to claim 12 or 13,
Each of the blades (48) of the axial blower (44) is twisted all over in the rotational direction.
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 16,
The lateral flow director (52) having a circular opening extends radially from the opening to its side edge by 5 cm to 10 cm, preferably 7 cm.
A freezing container characterized by that. The refrigerated container according to claim 16,
The twist with respect to the radial axis of the blade (48) is in the range of 5 ° to 25 °, preferably 10 °,
A freezing container characterized by that. In the refrigeration container according to any one of claims 1 to 18,
The annular part (40) constitutes a sleeve part inserted into the port (38) of the horizontal wall (32), and the flow cross section (50) of the sleeve part draws the warmed refrigerated air. A flange structure that forms a flow cross section for moving to the chute (18), and that the upper surface of the sleeve projects outwardly in the lateral direction to fix the annular part (40) to the horizontal wall (32) In particular, the diameter of the flow cross section of the sleeve corresponds to the space from the back wall of the container to the front inner wall surface of the chute 18 with a difference of twice the wall thickness of the back wall. The flange structure is configured on both sides along a direction extending in a lateral direction of the back wall of the container, at least mainly in fragments.
The lateral flange structure in the outward direction adjacent to the edge of the sleeve is laterally lateral by a protruding end (54) provided to be bent to secure the annular part to the upper surface of the horizontal wall (32). Forming each of the side flow directors (52) protruding into
A freezing container characterized by that. The refrigeration container according to claim 19,
The lateral flow director (52) protrudes from the end of the sleeve (42) by a continuously open curve,
A freezing container characterized by that. The refrigeration container according to claim 19 or 20,
The lateral flow director (52) formed by the side flange structure is fully or at least largely continuous between the front side of the chute (18) and the front side of the back wall (6, 14). Configured,
A freezing container characterized by that.

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