JPH11108534A - Refrigerating machine unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable economical operation in cooling of the total system of a showcase group or the like by one large-output larger refrigerating machine by providing a closing plate for closing a space between condensers to prevent the shortage of air at the condensers arranged in plurality. SOLUTION: Condenser units 30ab, 30cd and 30e feach have a pair of condensers 30a and 30b, a pair of condensers 30c and 30d and a pair of 30e and 30f securely supported in a V-shaped configuration on an open leg support plate 205, the front and rear ends of the open leg support plate 205 are placed and fixed on front and rear partition frame plates 201 b by which a machine room 200a and a heat exchange room 200 b are divided and arranged in parallel. A closing plate 206 comprising an iron plate or the like is mounted in a space generated between upper ends of the condenser units 30ab, 30cd and 30ef to close. Thus, the prevention of the shortage of air can prevent a drop in the heat exchange efficiency of the condensers thereby enabling economical operation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating machine unit, and more particularly to a refrigerating machine suitable for being applied to a refrigerating apparatus for cooling a plurality of showcases or refrigerators having different cooling temperatures depending on products, such as a supermarket, using a refrigerator. It concerns the machine unit.

[0002]

2. Description of the Related Art Conventionally, in a supermarket or the like, when a large-scale refrigeration system is constituted by a refrigerator and a refrigerator such as a freezer / refrigerator showcase or a prefabricated refrigerator, the cooling of the showcase and the like is required. The refrigerators are systematized according to the required capacity of the refrigerator and the required capacity, and a plurality of them are installed for the required system.

[0003] In general supermarkets, excluding frozen commodities such as popsicles, daily and dairy products (cooling temperature: 3-7 ° C), fruits and vegetables (5-10 ° C), meat and meat
There are three refrigerated lines of fresh fish (−5 to 2 ° C.). From the viewpoint of the evaporation temperature, the showcase for daily / dairy products and fruits and vegetables is −10 ° C., while the showcase for meat and fresh fish is −17 ° C.

[0004] For example, FIG. 7 is a schematic diagram showing a conventional example of a layout and operating state of a showcase group, a refrigerator and a refrigerator in a supermarket. Here, the showcase groups 1a to 1i and the refrigerator 1j are divided into the three systems described above, and the first to third refrigerators 2a to 2c are respectively arranged and connected by the refrigerant pipes 3a to 3c. The solenoid valves 4a to 4j are provided for each of the showcases, the showcase groups 1a to 1i, and the refrigerator 1j. Each of the refrigerators 2a to 2c
By combining two or three compressors from among three types of compressors (compressors) of general 10 hp (HP), 15 hp and 20 hp, an output of 25 to 45 hp can be obtained. Things.

[0005]

By the way, in selecting equipment of a conventional refrigeration system, when performing load estimation calculation, a safety factor (margin factor) of 30% is added to the refrigeration capacity derived from necessary equipment. , The selection of the refrigerator output of the system.

For example, the required refrigerating capacity of each of the three types of showcase groups 1a to 1i and the refrigerator 1j is represented by (A) kcal / h, (B) kcal / h, and (C).
If kcal / h, the refrigerating function is (A + B + C) ×
1.3 or more is required. The safety factor (margin factor) is 30%
Breakdown of piping pressure loss: 10%, outside air temperature correction: 10
%, Pull-down support after defrosting (load increase after defrosting): 10%. The 10% load increase after defrosting is expected for the following reasons.

In the conventional refrigeration system, defrosting of the evaporator is performed by first stopping the chiller of the defrosting system, melting the frost adhering to each evaporator of the system, and then operating the chiller of the system again. Is generally used. In this method, the load on the refrigerator after the completion of defrosting temporarily increases.

That is, in FIG. 7, the first refrigerator 2a is stopped while the showcase groups 1a to 1d connected to the first refrigerator 2a are being defrosted, and the solenoid valves 4a in the refrigerant pipe 3a are stopped. ４4d are closed. Maximum load occurs after this defrost. That is, since the load of all the showcase groups 1a to 1d connected to the first refrigerator 2a increases at once, the load of the first refrigerator 2a increases significantly.

Each of the refrigerators 2a to 2c is composed of a plurality of compressors (compressors) and other element parts such as a condenser (condenser), and their outputs are 25 to 45 horsepower as described above. However, if a selection is made for a refrigeration system that requires a refrigeration capacity exceeding 45 horsepower in all systems, depending on the combination, the output must be selected more than necessary.

That is, the output configuration of this type of conventional refrigerator has a power of 25, 30, 35, and 45 horsepower. In this output configuration, selection of a refrigerator having a useless output for one system of the showcase group is performed. Occurred many times. This causes an increase in equipment cost and a decrease in operating efficiency for each system, and further increases wasteful output (power consumption) by the number of systems in the showcase group.

For example, assuming that the required freezing capacity of the showcase group is 20 hp for fruits and vegetables, 17 hp for meat and fresh fish, and 24 hp for daily and dairy products, the above-mentioned safety factor of 30
The refrigeration capacity, with the addition of%, is 26 hp for fruits and vegetables, 22.1 hp for meat and fresh fish, and 31.2 hp for daily and dairy products. Therefore, a refrigerator of 30 hp is required for fruits and vegetables, and a refrigerator of 25 hp for meat and fresh fish.
A chiller of 35 hp for dairy products is required.

That is, when the safety factor of 30% is sufficient for the total of 79.3 horsepower, the total of three refrigerators becomes 90 horsepower, and the output is selected more than necessary. By the way, the amount of refrigerant is also almost proportional to the refrigerating capacity, 95 kg at 30 hp, 80 kg at 25 hp, 115 k at 35 hp
g is required, for a total of 290 kg.

As shown in FIG. 8, when the daily showcase load measured in a certain supermarket is examined, the load ratio during the opening hours varies between 60% and 100%. The load factor at night after the store is covered by the cover is approximately 20% as indicated by the thick line.
Therefore, in order to reduce power consumption, a refrigerator having a wide capacity control range capable of coping with the 20% load at night is required.

Investigation of the annual cost of a certain supermarket shows that electricity costs occupy the second place in terms of personnel costs, and refrigeration equipment consumes considerably more power than lighter equipment such as lighting and registers. From this, it can be seen that the reduction of the electricity cost of the refrigeration system greatly contributes to the improvement of the profit of the supermarket.

Further, in the above example, the installation work of the refrigerators 2a to 2c for the three systems and the respective piping work are required, which requires much labor and time.

As measures against the above problems,
It is conceivable to cool all the systems such as the group of showcases by a single large-sized refrigerator having a large output and an increased number of compressors.

In general, a refrigerator has a machine room for accommodating a compressor and the like on a lower side, and a condenser and a cooling fan for the condenser are mounted on an upper side partitioned by a partition plate (top plate of the machine room). It is housed in a unit case having a heat exchange chamber.

In order to increase the size of the refrigerator, it is necessary to increase the heat exchange efficiency of the condenser. Therefore, for example, a plurality of condensers formed in a V shape and having a cooling fan arranged between the V shapes are arranged in parallel. A configuration in which the components are arranged is considered. In this case, when the cooling fan is driven, air is sucked from both inclined side surfaces of the V-shaped condenser to cool the condenser, and the warmed air is blown upward. However, between the side surfaces of the V-shaped condensers, there is an area where the pressure is low because air is sucked into each other. Therefore, the warm air blown out from the cooling fan is drawn from the gap between the upper ends of the respective V-shaped condensers to the side of each of the V-shaped condensers, which is under negative pressure, and is sucked into the condenser again. A phenomenon (called an air short) occurs, which significantly reduces the heat exchange efficiency of the condenser.

Further, when the number of compressors is increased to increase the size of the refrigerator, the temperature rise in the machine room increases due to the heat generated, and forced ventilation by a ventilation fan is required.
However, if a ventilation fan is provided in addition to the cooling fans for the condensers as described above, the cost is considerably increased. Therefore, it is conceivable to provide a ventilation port on the top of the machine room and perform forced ventilation with the cooling fan of the condenser.However, since this type of large refrigerator is installed outdoors, There is a problem that rainwater enters the machine room from the provided ventilation openings.

Further, when the size of the refrigerator is increased, the area of the top plate in the machine room also becomes large, so that it is not possible to cover it with one existing iron plate, and it is necessary to form a plurality of iron plates together. As described above, since this type of large-sized refrigerator is installed outdoors, in order to prevent rainwater from entering the machine room from the joints of the respective iron plates, welding or caulking of all joints, or another member. Is required, and the cost is considerably increased.

Therefore, the present invention has been made to solve such a problem, and is intended for cooling all the systems such as a group of showcases by a single large-sized refrigerator having a large output. In addition, a refrigerator unit that can economically operate by preventing air shorts in condensers that are arranged in parallel in a large refrigerator and that can ensure the ventilation of the machine room and the waterproofness of the top plate of the machine room at low cost It is intended to provide.

[0022]

In order to achieve the above object, the present invention provides a machine room for accommodating a compressor and the like, and a device which is located above the machine room and discharges air sucked from a side surface from above. A heat exchange chamber for accommodating a plurality of condensers for performing heat exchange, and a refrigerator unit including a partition plate for partitioning the machine room and the heat exchange chamber, wherein a closing plate closing a gap between the condensers It is characterized by having.

Also, a refrigerating machine having a machine room for accommodating a compressor and the like, a heat exchange room located above the machine room and accommodating a condenser, and a partition plate for separating the machine room and the heat exchange room. The partition unit is characterized in that the partition plate has a ridge near the center and is a roof type inclined in two directions facing each other with the ridge as a boundary.

Further, the partition plate is composed of at least two plate members, and a first inclined plate inclined from the ridge line of the partition plate toward one side, and one of the one sloping line from the ridge line of the partition plate. A second inclined plate inclined toward the other side surface opposite to the side surface, wherein the first inclined plate is formed larger than the second inclined plate and overlapped and joined at a position different from a ridge line of the partition plate; It is characterized by the following.

The refrigerating machine includes a machine room for accommodating a compressor and the like, a heat exchange room located above the machine room and containing a condenser, and a partition plate for separating the machine room and the heat exchange room. Machine unit, wherein the heat exchange chamber includes a frame on the partition plate, and an open leg support plate on which the condenser is mounted is fixed to the frame.

Further, the partition plate is provided with a machine room ventilation port having a protruding periphery, and the machine room ventilation port is provided below the leg supporting plate.

[0027]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 is a schematic diagram showing a layout of a cooler group such as a showcase and a refrigerator in a refrigerator according to an embodiment of the present invention and an operation state thereof.

As shown in the figure, the showcase groups 1a to 1
i and the refrigerator 1j are divided into three systems in substantially the same manner as described above, one high-power refrigerator 2 is arranged, the refrigerant pipes 3 are connected, and each showcase or showcase group 1 in each system is connected.
a to 1i, and solenoid valves 4a to 4j are provided for each refrigerator 1j. In the figure, one showcase group 1a in which the inside of one system is further finely blocked is being defrosted, and its solenoid valve 4
a is closed, but the other showcase groups 1b-1i
In addition, the refrigerator 2 operates without stopping while the solenoid valves 4b to 4j of the refrigerator 1j are kept open.

The refrigerator 2 is provided with a plurality of compressors and has a capacity control function from the minimum load equivalent to the maximum load of all of the three cooler groups 1a to 1j.
The refrigerator 2 having the optimum output is selected by a new defrosting method described later and a load estimating method based thereon.

Further, the cooling temperature of the cooler groups 1a to 1j of each system having the same evaporation temperature by using one refrigerator is required by making the heat exchange efficiency of the evaporators provided therein different. A cooling temperature is provided. Specifically, the evaporating temperature was unified to -10 ° C for conventional day-daily / dairy products and showcases for fruits and vegetables, and
The meat and fresh fish showcase at 17 ° C. has a required cooling temperature of -5 by increasing the size of the evaporator, that is, increasing the surface area of the fins to improve the heat exchange efficiency of the evaporator.
To 2 ° C.

Although not shown, the solenoid valve 4
a to 4j, each showcase 1a to 1i and refrigerator 1
A service valve is attached to a main part of the refrigerant pipe connected to j for easy operation. As a result, even if a leak or the like occurs in a part of the refrigerant pipe 3 connected from one refrigerator 2 to the entire system, the refrigerator 2
The service valve provided on the side is closed, and the refrigerator 2 can be repaired while it is running, so that the entire system can be prevented from shutting down for partial repair.

Each of the coolers is provided with a defrost timer, and the defrost timers whose operation times are shifted open and close the solenoid valves 4a to 4j provided for each block, so that freezing is performed. While the operation of the machine 2 is continued, the defrosting operation of the coolers 1a to 1j for each block is performed sequentially (sequentially). As a result, the load fluctuation of the refrigerator 2 is reduced and stabilized, and the temperature inside the refrigerator or the showcase is stabilized. That is, since the load applied to the refrigerator 2 is stabilized, the power consumption of the refrigerator 2 is reduced, and the temperature recovery after defrosting of a cooler such as a showcase or a refrigerator is quicker, so that the temperature controllability is also improved. I do.

By adopting such a new defrosting method and appropriately performing the blocking, the load increase after the defrosting is dispersed, and it becomes extremely small as a whole.
Therefore, it becomes almost negligible for the high-power refrigerator 2 having the capacity control function, and there is no problem even if the safety factor used for calculating the load estimation is reduced from 30% of the conventional one to almost 20%.

FIG. 2 is a refrigerant circuit diagram of the refrigerator 2 of the present embodiment. This refrigerator 2 has four compressors 20a to 20d (75 hp) in total, one for 15 hp and three for 20 hp to cope with a 20% load at night, and two compressors are connected by a common pipe. Have been. That is, the first compressor 20
a and mufflers 21a, 21a in the discharge pipe of the second compressor 20b.
Refrigerant pipes 22a and 22b connected via b are joined on the way, and connected to an oil separator (oil separator) 23a for the first and second compressors. Similarly, mufflers 21c, 21c are provided in discharge pipes of the third compressor 20c and the fourth compressor 20d.
Refrigerant pipes 22c and 22d connected via 21d join on the way, and are connected to an oil separator 23b for the third and fourth compressors.

Further, the first compressor 20a and the second compressor 20
Refrigerant pipes 24a and 24b connected to the suction pipe b join in the middle and connected to accumulators (gas-liquid separators) 25a for the first and second compressors. Similarly, refrigerant pipes 24c and 24d connected to the suction pipes of the third compressor 20c and the fourth compressor 20d join on the way, and are connected to accumulators 25b for the third and fourth compressors. The discharge pipe and the suction pipe of each of the compressors 20a to 20d are provided with maintenance service valves 26a to 26d and 27a to 27d.

The refrigerant pipes 28a and 28b that have come out of the oil separators 23a and 23b are joined to provide a total of three sets of two refrigerant pipes, each of which is provided with an air-cooled condenser (condenser) 30a through a plurality of fans 29. 30f. On the input side of each of the capacitors 30a to 30f,
Service valves 31a to 31c are provided for each unit, and service valves 32a to 32f are individually provided on the output side. Further, one side of the output of each unit is provided with high-pressure switches 33a to 33c for backup of the temperature sensor for controlling the fan motor.

The refrigerant pipes exiting from the condensers 30a to 30f are joined and connected to a receiver tank (liquid receiver) 34. The receiver tank 34 is provided with service valves 35 and 36 on the inlet and outlet sides of the refrigerant pipe, and a high-pressure manometer via a safety valve 37, a fusible plug 38, a check valve 38 and a capillary tube 39. 40 are attached.

The refrigerant pipe exiting the receiver tank 34 is drawn out of the refrigerator 2 as a high-pressure liquid pipe 43 via a filter dryer 41 and a moisture indicator 42, and as shown in FIG. It is branched and connected to each of the showcase groups 1a to 1i and the refrigerator 1j via the solenoid valves 4a to 4j.

Each of the showcase groups 1a to 1i and the refrigerator 1
The refrigerant pipes from j are joined to form one common pipe 3 and connected to the suction pipe 44 of the refrigerator 2, and the accumulator 25 a for the first and second compressors and the accumulator 25 a for the third and fourth compressors It is input to the accumulator 25b. A service stop valve 46 is connected to the suction pipe 44 and the low pressure manometer 4
7. A low pressure switch 48a for the first and second compressors and a low pressure switch 48b for the third and fourth compressors are attached.

The low pressure switch 48a for the first and second compressors and the low pressure switch 4 for the third and fourth compressors
Reference numeral 8b denotes a digital pressure switch that can set two different types of ON / OFF pressures.
It is provided for capacity control of 20d. That is, the four low-pressure switches 48a and 48b are different from each other.
Various ON / OFF pressures can be set. One compressor can be operated (20% load at night) to four compressors (10 daytime).
Wide capacity control up to 0% load) is possible.

On the other hand, the refrigerant pipe 49a exiting from the accumulator 25a for the first and second compressors is branched and connected to the suction pipes of the first and second compressors 20a and 20b. The refrigerant pipe 49b that has exited from the compressor accumulator 25b branches off into a third compressor 20c and a fourth compressor 2c.
0d is connected to the suction pipe.

A high-pressure liquid refrigerant is supplied to the high-pressure liquid pipe 43 downstream of the moisture indicator 42 by each compressor 20.
A liquid injection pipe (L / I pipe) 50 for cooling each of the compressors 20a to 20d with the heat of evaporation by returning to evaporate by returning to a to 20d is connected. The L / I pipe 50 is branched into four pipes for each compressor on the way, and the service stop valves 51a to 51d are respectively provided.
d, each of the compressors 20a to 52d through the solenoid valves 52a to 52d and the capillary tubes 53a to 53d for evaporation under reduced pressure.
It is input to the low pressure side of 20d.

On the other hand, the first and second compressor oil separators 23a and the third and fourth compressor oil separators 2a
An oil tank 54 for storing the separated lubricating oil is connected to 3b. Service valves 55 and 56 are provided on the inlet side and the outlet side of the oil tank 54. The pipe connected to the service valve 56 at the outlet of the oil tank is branched into four pipes for each compressor on the way, and each of the compressors 20a to 20d is connected via a service stop valve 57a to 57d and an oil regulator 58a to 58d, respectively. 20d. The oil tank 54 is connected to the suction pipe 44 of the refrigerator 2 via an oil tank pressure equalizing piping service valve 59.

On the high pressure side and low pressure side of each of the compressors 20a to 20d, an abnormally high or abnormal
High / low pressure switch 60 for protecting 0a-20d
a to 60d are capillary tubes 6 for stabilizing pressure.
They are connected via 1a to 61d.

In the present embodiment, since various service valves are provided in the above-described main part also in the refrigerator 2, even if a leak or the like occurs in a part of the refrigerant pipe or the like, it is provided on both sides of the part. By closing the service valve and repairing the refrigerator while it is running, it is possible to prevent the entire system from being stopped due to partial repair.

The refrigerator 2 of the present embodiment having the above-described configuration is installed outdoors, and has a high-pressure liquid pipe 43 and a suction pipe 44.
Are connected to the showcase groups 1a to 1i and the refrigerator 1j in the supermarket by the refrigerant pipe 3, as shown in FIG. In this case, installation work of one refrigerator and piping work thereof can be completed, so that the installation work can be simplified.

The refrigerator 2 of this embodiment has four compressors 2
0a to 20d are the low pressure switches 48a for the first and second compressors and the low pressure switches 48 for the third and fourth compressors as described above.
b, the capacity control operation is automatically performed. For example, when the load is 20% at night when the showcase is covered,
One horsepower compressor operated, 100% in daytime after opening
At the time of load, four compressors are operated.

The high-pressure high-temperature refrigerant compressed by each of the compressors 20a to 20d joins to form the oil separators 23a and 23b.
The lubricating oil mixed with the refrigerant is separated from the refrigerant, and the separated lubricating oil is temporarily stored in an oil tank 54, and is operated by the oil regulators 58a to 58d as necessary.
The values are returned to 0a to 20d.

The high-pressure high-temperature refrigerant having passed through the oil separators 23a and 23b merges and is divided and supplied to three units of air-cooled condensers 30a to 30f, where the fan 2
The liquid is condensed and liquefied by forced air cooling by the
Stored in 4.

From the receiver tank 34, the high-pressure liquid refrigerant is supplied stably to the showcase groups 1a to 1i and the refrigerator 1j connected to the refrigerator 2 via the filter dryer 41 and the moisture indicator 42. The high-pressure liquid refrigerant supplied to the showcase groups 1a to 1i and the refrigerator 1j is decompressed and expanded by passing through the expansion valve, and is supplied to an evaporator (evaporator). In the evaporator, the inside of the refrigerator is cooled by the heat of vaporization of the liquid refrigerant that has been decompressed and expanded, and is maintained at a cooling temperature according to the heat exchange efficiency.

In the present embodiment, as described above, the cooling temperatures of the showcase groups 1a to 1i and the refrigerators 1j of the respective systems in which the evaporation temperature is the same by using one refrigerator 2 are provided to them. The required cooling temperature can be obtained by making the heat exchange efficiency of the evaporator different. Here, the evaporating temperature is unified to -10 ° C, such as a display case for daily delivery, dairy products, fruits and vegetables, fruits and the like.
That is, the required cooling temperature is obtained by improving the heat exchange efficiency of the evaporator by increasing the surface area of the fin or the like.
5 ° C. to 2 ° C. is obtained.

In this manner, the low-pressure refrigerant gas that has cooled the showcase groups 1a to 1i and the refrigerator 1j of each system is returned to the suction pipe 44 of the refrigerator 2 via the refrigerant pipe 3, and is stored in the accumulator 25a. , 25b, and only the gaseous components are returned to the compressors 20a to 20d and recompressed, and the refrigeration cycle is repeated.

During this time, each of the compressors 20a to 20d is connected to an open / close shop, a showcase group 1a to 1i or a refrigerator 1
The capacity control operation is automatically performed by the first and second compressor low-pressure switches 48a and the third and fourth compressor low-pressure switches 48b according to the load fluctuation of j. Therefore, the operation state of the refrigerator is maintained at the minimum output required to maintain the required cooling temperature of each of the showcase groups 1a to 1i and the refrigerator 1j.

Here, in the conventional system, as described above, the total output of the three chillers 2a to 2c of the three systems is individually 30% safety factor for the required refrigeration capacity of 61 horsepower of all the systems.
In consideration of the above, it is necessary to select a refrigerator more than 90 horsepower in total, the required amount of refrigerant is also 290 kg, but in the system of the present embodiment, for the same total system required refrigeration capacity 61 horsepower, With the new defrosting method (sequential defrosting method) described above, the value taking into account the safety factor of 20%, which suppresses the load increase after defrosting, is 73.2 horsepower, so one 75 horsepower unit is sufficient and the refrigerant amount is 240 kg. It became. As a result, horsepower is reduced by 17%,
This means that the refrigerant amount was reduced by 17%.

Next, the reduction in power consumption by the refrigeration apparatus of this embodiment will be described. The graph in FIG. 3 shows a change in power for one day. The dotted line is the refrigeration apparatus of the present embodiment, and the solid line is the conventional refrigeration apparatus. As a result of coping with the capacity controllability of the refrigeration apparatus in the present embodiment in a time zone of a 20% load at night, a large reduction in the amount of power is achieved. In addition, a large reduction in the amount of power is achieved by the effect of output optimization and the effect of sequential defrost.
As a result of analyzing this data, about 18.5% throughout the year
Power consumption is expected to decrease.

By the way, as a result of collecting various information about a supermarket as an optimum output refrigerator, it was found that the refrigerator needs a series configuration (11 models) from 45 to 95 horsepower in increments of 5 horsepower. .

Therefore, in the present invention, in order to develop a refrigerator having a wide capacity control range corresponding to a 20% load at night, as shown in FIG.
A multi-compressor system of up to 5 units combining a horsepower (HP) refrigerator with 10, 15, and 20 horsepower compressors (compressors) is adopted, and 11 models from 45 to 95 horsepower can be realized in 5 horsepower increments. I did it.

FIG. 5 is an external perspective view of a large-sized refrigerator having, for example, five compressors among the above 11 models, and FIGS. 6 to 8 are perspective views with a part removed for easy viewing. FIG.

The unit case 200 of the refrigerator 2 is formed in a rectangular parallelepiped shape by a frame 201a, and the lower side is a machine room 200a in which machines such as five compressors, a receiver tank, and an electrical box are stored. On the upper side, capacitor units 30ab and 30c installed in a V-shape in pairs.
d, 30ef are arranged in three units, and each unit 30a
A heat exchange chamber 200b is provided in which nine cooling fans 29 are mounted three by three on the V-shaped upper part of b to 30ef.

The front and rear surfaces and both side surfaces of the machine room 200a are covered with a side plate 202 such as an iron plate.
The front and rear sides of the V-shaped portion of each of the capacitor units 30ab to 30ef are closed with an iron plate 203, and the outer front and rear surfaces, both side surfaces, and the upper surface are covered with a grid-shaped wire net 204 to prevent the inhalation of leaves and paper dust. Have been done. When the condenser cooling fan 29 rotates, the V-shaped portion is closed by the iron plate 203, so that outside air is sucked in from the front, rear, and side surfaces, and passes through the capacitors 30a to 30f to cool. The warmed air is blown upward.

Each capacitor unit 30ab, 30c
d, 30ef are a pair of capacitors 30a and 30b, 3
0c and 30d, 30e and 30f are the open leg support plates 2 respectively.
05 is fixedly supported in a V-shape, and the front and rear ends of the open leg support plate 205 are connected to the machine room 200a and the heat exchange room 200b.
Are placed and fixed on a partition frame plate (frame body) 201b before and after dividing into and are arranged in parallel. In this manner, by mounting and fixing the open leg support plate 205 to the front and rear partition frame plates 201b, even if the partition plate between the machine room 200a and the heat exchange chamber 200b is a roof type as described later, the V-shape is used. It is possible to stably support and fix the mold-type capacitor units 30ab, 30cd, 30ef, and to form a clearance for ventilation of a machine room to be described later.

A closing plate 206 made of an iron plate or the like is attached to the gap formed between the upper ends of the capacitor units 30ab, 30cd, 30ef arranged as described above, so that the gap is closed. It has become.

Accordingly, since the above-mentioned air short circuit can be prevented by the closing plate 206, a decrease in the heat exchange efficiency of the condenser can be prevented, and economic operation can be performed.

The top plate (partition plate) 2 of the machine room 200a
07 is a roof type using two iron plates (plate members) 207a and 207b, having a ridge near the center and inclining back and forth with the ridge as a boundary. Further, a large iron plate (first inclined plate) 207b located on the rear side thereof is bent in a shape of a cross section, and this bent portion 207c is formed above the front iron plate (second inclined plate) 207b. By overlapping on the side, the top joint portion of the top plate 207 has an overlapping structure. In addition, the front end portion of the inclined surface of the top plate 207 configured as described above is divided into front and rear partition frame plates 201b.
Is located below. In addition, an anti-vibration material (not shown) is interposed in the overlapping portion,
The vibration of the compressor prevents the overlapping portions from colliding with each other, thereby preventing noise and gaps from being generated.

The iron plates 207a and 207b are desirably integrally formed, but may be formed by combining a plurality of plate members. At this time, each plate member is welded or covered with another member and sealed sufficiently so that rain does not enter from a joint other than the top overlapping portion of the plate members.

By constructing the top plate 207 of the machine room 200a as described above, the roof type allows rainwater to flow down quickly without collecting, and the top joint portion is coked for waterproofing or another component is added. Without this, the waterproof property of the top plate 207 of the machine room 200a can be secured at low cost.

The top plate 207 of the machine room 200a is provided with a ventilation port 208 projecting in a box shape such that the upper opening 208a is located inside the above-mentioned open leg support plate 205. The ventilation port 208 is provided in the machine room 200a.
For each of a plurality of compressors (not shown) arranged in a horizontal line on the front side of the inside, three are formed for each leg supporting plate 205 on the front inclined surface of the top plate 207 of the machine room 200a. .

Since there is a gap between the open leg support plate 205 and the inclined top plate 207 of the machine room 200a, each V-shaped capacitor unit 3 is driven by the cooling fan 29.
When a negative pressure is applied between the inclined side surfaces of 0ab to 30ef, the inside of the leg supporting plate 205 also has a negative pressure. Therefore, the upper opening 208a
The air in the machine room 200a is sucked through the ventilation port 208 formed so that the
The inside of the machine room 200a is forcibly ventilated.

With the above configuration, forced ventilation of the machine room 200a can be realized at low cost by using the cooling fans 29 of the condenser units 30ab to 30ef. Moreover, the V-shaped capacitor units 30ab-3
By effectively utilizing the 0ef open leg support plate 205, the rainwater machine room 20 can be manufactured at low cost without providing a special rainproof cover.
0a can be prevented from entering.

In the above embodiment, the machine room 200a
Top plate 2 corresponding to the position of the hottest compressor
07 was provided with a ventilation port 208 on the front slope,
It is more effective to provide a ventilation hole similar to the above on the rear inclined surface of the top plate 207 of 00a.

[0072]

As described above, according to the present invention, a machine room for accommodating a compressor and the like is located above the machine room,
A refrigerator unit having a heat exchange chamber for accommodating a plurality of condensers that perform heat exchange by discharging air sucked from the side from above, and a partition plate for partitioning the heat exchange chamber, wherein a gap between the condensers is provided. Since a blocking plate is provided to close the gap, the gap between the condensers is blocked by the blocking plate, and air short-circuit can be prevented. Therefore, reduction in the heat exchange efficiency of the condenser can be prevented, and economical operation can be performed. Become like

A refrigerator unit comprising a machine room for accommodating a compressor and the like, a heat exchange chamber for accommodating a condenser located above the machine room, and a partition plate for partitioning the heat exchange chamber. The plate has a ridge near the center and has a roof shape inclined in two directions facing the ridge, so that rainwater can quickly flow down without collecting on the partition plate.

Further, the partition plate is composed of at least two plate members, and a first inclined plate which is inclined from the ridge line of the partition plate toward one side, and the one inclined plate from the ridge line of the partition plate. A second inclined plate inclined toward the other side surface opposite to the side surface, wherein the first inclined plate is formed larger than the second inclined plate and is overlapped and joined at a position different from the ridge line; The waterproofness of the machine room top plate can be ensured at low cost without caulking the top joint of the room top plate or adding additional parts.

Further, there is provided a refrigerator unit including a machine room for accommodating a compressor and the like, a heat exchange chamber for accommodating a condenser located above the compressor room, and a partition plate for partitioning the heat exchange chamber. The exchange chamber is provided with a frame on the partition plate, and the open leg support plate on which the condenser is placed is fixed to the frame body, so that the partition plates of the machine room and the heat exchange chamber are as described above. Even with a roof type, the condenser can be stably supported and fixed.

Further, the partition plate is provided with a ventilation opening for the machine room whose periphery is protruded, and this ventilation opening is provided below the open leg supporting plate, so that the cooling fan of the condenser is used. Forced ventilation of the machine room can be realized at low cost, and rainwater can be prevented from entering the machine room at low cost without using a special rainproof cover by effectively using the open leg support plate of the condenser. .

[Brief description of the drawings]

FIG. 1 is a schematic diagram showing a layout of a cooler group such as a showcase and a refrigerator in a refrigerator according to an embodiment of the present invention and an operation state thereof.

FIG. 2 is a refrigerant circuit diagram of the refrigerator of the embodiment.

FIG. 3 is a diagram showing a daily power change amount in the supermarket of the embodiment and the conventional example.

FIG. 4 is a diagram showing a model configuration according to the present invention.

FIG. 5 is an external perspective view showing an embodiment of a refrigerator unit according to the present invention.

FIG. 6 is a perspective view with a part removed for easy viewing of the main part of FIG. 5;

FIG. 7 is a perspective view showing a state where a part is removed to make it easy to see a main part.

FIG. 8 is a perspective view showing a state in which some parts are removed to make main parts easy to see.

FIG. 9 is a schematic diagram showing a conventional example of a layout and operating state of a showcase group, a refrigerator and a refrigerator in a supermarket.

FIG. 10 is a diagram showing a change in load per day for a showcase.

[Explanation of symbols]

1a-1i Showcase 1j Refrigerator 2 Refrigerator 3, 22a-22d, 24a-24d, 28a, 28
b, 49a, 49b Refrigerant piping 4a to 4j, 52a to 52d Solenoid valve 20a to 20d Compressor 23a, 23b Oil separator 25a, 25b Accumulator 26a to 26d, 27a to 27d, 31a to 31c, 3
2a to 32f, 35, 36, 51a to 51d, 55, 5
6 Service valve 54 Oil tank 34 Receiver tank 30a-30f Capacitor 30ab, 30cd, 30ef V-shaped capacitor unit 48a, 48b Low pressure switch 200 Unit case 200a Machine room 200b Heat exchange room 201b Partition frame plate 205 Leg support plate 206 Closure Plate 207 Top plate 207a, 207b Iron plate 207c Bent portion 208 Ventilation opening 208a Upper opening

Continued on the front page (72) Inventor Kazuhiko Mihara 2-5-5 Keihanhondori, Moriguchi-shi, Osaka Sanyo Electric Co., Ltd. (72) Tomoyuki Shiomi 2-5-5 Keihanhondori, Moriguchi-shi, Osaka Sanyo Electric Co., Ltd. (72) Inventor Kensuke Oka 2-5-5 Keihanhondori, Moriguchi-shi, Osaka Sanyo Electric Co., Ltd.

Claims (5)

[Claims] 1. A heat exchange chamber for accommodating a machine room accommodating a compressor and the like, and a plurality of condensers located above the machine room and exchanging heat by discharging air sucked in from the side from above. And a refrigerator unit provided with a partition plate for partitioning the machine room and the heat exchange chamber, the refrigerator unit comprising a closing plate closing a gap between the condensers. 2. A refrigerating machine comprising: a machine room for accommodating a compressor or the like; a heat exchange room located above the machine room and containing a condenser; and a partition plate for separating the machine room and the heat exchange room. The refrigerator unit, wherein the partition plate has a ridge near the center and is a roof type inclined in two directions facing each other with the ridge as a boundary. 3. The partition plate includes at least two plate members, a first inclined plate inclined from a ridge line of the partition plate toward one side surface, and one of the first inclined plate and the ridge line of the partition plate. A second inclined plate inclined toward the other side surface opposite to the side surface, wherein the first inclined plate is formed larger than the second inclined plate and overlapped and joined at a position different from a ridge line of the partition plate; 3. The method according to claim 2, wherein
The refrigerator unit as described. 4. A refrigerating machine comprising: a machine room for accommodating a compressor or the like; a heat exchange room located above the machine room, for accommodating a condenser; and a partition plate for separating the machine room and the heat exchange room. A refrigerator unit, wherein the heat exchange chamber includes a frame on the partition plate, and an open leg support plate on which the condenser is mounted is fixed to the frame. 5. The refrigerator according to claim 4, wherein the partition plate includes a machine room ventilation port whose periphery is protruded, and the machine room ventilation port is provided below the open leg support plate. unit.