REFRIGERATION APPARATUS

Description

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a continuation of PCT/JP2024/024416 filed on Jul. 5, 2024, which claims foreign priority of Japanese Patent Application No. 2023-115969, filed on Jul. 14, 2023, the entire contents of both of which are incorporated herein by reference.

TECHNICAL FIELD

The present invention relates to a refrigeration apparatus.

BACKGROUND ART

A refrigeration apparatus that includes a box body having an accommodation compartment as disclosed in Patent Literature (Hereinafter, referred to as PTL) 1 has been known. The refrigeration apparatus includes a cooling apparatus that cools the accommodation compartment. The cooling apparatus includes a compressor that compresses and discharges a refrigerant. The compressor is accommodated in a predetermined machine compartment in the refrigeration apparatus.

CITATION LIST

Patent Literature

• • PTL 1
  • Japanese Patent Application Laid-Open No. 2004-190917

SUMMARY OF INVENTION

Technical Problem

In a case where the refrigeration apparatus is operated as described above, the refrigerant may leak in the machine compartment due to damage to a pipe or the like through which the refrigerant flows. In a case where the refrigerant is vaporized in the machine compartment, the concentration of the refrigerant in the machine compartment may become high.

The present invention has been made in view of such circumstances, and an object of the present invention is to provide a refrigeration apparatus that can reduce a concentration of a refrigerant in a machine compartment in a case where the refrigerant leaks in the machine compartment.

Solution to Problem

One aspect of a refrigeration apparatus according to the present invention includes:

• • a housing body including an accommodation compartment and a machine accommodation section;
  • a cooling apparatus including a compressor that circulates a refrigerant and a blowing apparatus that cools the compressor, the cooling apparatus being configured to cool the accommodation compartment; and
  • a controller that controls an operation of the compressor and the blowing apparatus, in which
  • the compressor and the blowing apparatus are accommodated in the machine accommodation section, and
  • in cooling control for cooling the accommodation compartment, the controller is configured to:
  • switch between stopping and driving the compressor, and
  • after stopping the compressor, drive the blowing apparatus after a first predetermined time period set in advance.

Advantageous Effects of Invention

According to the present invention, it is possible to provide a refrigeration apparatus that can reduce a concentration of a refrigerant in a machine compartment in a case where the refrigerant leaks in the machine compartment.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a perspective view showing an overall configuration of a refrigeration apparatus according to Embodiment 1 of the present invention;

FIG. 2 is a circuit diagram of a cooling apparatus;

FIG. 3 is a plan schematic view showing an internal configuration of a machine accommodation section;

FIG. 4 is a line diagram showing a timing of an operation of a compressor and a blowing apparatus;

FIG. 5 is a line diagram showing a timing of an operation of a compressor and a blowing apparatus constituting a refrigeration apparatus according to Embodiment 2 of the present invention;

FIG. 6 is a plan schematic view showing a variation example of the refrigeration apparatus.

DESCRIPTION OF EMBODIMENTS

Hereinafter, a refrigeration apparatus according to the present invention will be described with reference to the drawings. The same components are denoted by the same reference numerals. The matters described below together with the accompanying drawings are provided for describing an exemplary embodiment and not for indicating a sole embodiment.

Embodiment 1

Refrigeration apparatus 1 according to Embodiment 1 of the present invention will be described with reference to FIGS. 1 to 4.

FIG. 1 is a perspective view of refrigeration apparatus 1 according to Embodiment 1 of the present invention. FIG. 2 is a circuit diagram of cooling apparatus 6. FIG. 3 is a schematic plan view showing an internal configuration of machine accommodation section 5. FIG. 4 is a line diagram showing a timing of an operation of compressor 601 and blowing apparatus 62.

Refrigeration apparatus 1 is, for example, an ultra-low temperature freezer. The ultra-low temperature freezer refers to a freezer that cools the interior to an ultra-low temperature (e.g., approximately −80° C.). Note that, refrigeration apparatus 1 may be a pharmaceutical refrigerator, a blood bank refrigerator, or a thermostat.

Note that, in the following descriptions of the structures of refrigeration apparatus 1 and each member constituting refrigeration apparatus 1, an orthogonal coordinate system (X, Y, Z) illustrated in each drawing is sometimes used. The X direction corresponds to the front-rear direction of refrigeration apparatus 1. The positive (+) side in the X direction corresponds to the front side of refrigeration apparatus 1. The negative (−) side in the X direction corresponds to the rear side of refrigeration apparatus 1.

Furthermore, the Y direction corresponds to the left-right direction and the width direction of refrigeration apparatus 1. The positive (+) side in the Y direction corresponds to the left side when refrigeration apparatus 1 is viewed from the front thereof. The negative (−) side in the Y direction corresponds to the right side when refrigeration apparatus 1 is viewed from the front thereof. The Z direction corresponds to the upper-lower direction of refrigeration apparatus 1. The positive (+) side in the Z direction corresponds to the upper side of refrigeration apparatus 1. The negative (−) side in the Z-direction corresponds to the lower side of refrigeration apparatus 1.

In the following, the basic configuration of refrigeration apparatus 1 will be briefly described. Refrigeration apparatus 1 according to the present embodiment includes main body 2, machine accommodation section 5, and cooling apparatus 6 (see FIG. 2).

Main body 2 includes housing body 21 and door 22 that opens and closes an opening. Housing body 21 has storage chamber 210 that is open upward inside. Storage chamber 210 is a space in which a sample is stored, and is cooled to an ultralow temperature. Door 22 opens and closes the opening of storage chamber 210.

Machine accommodation section 5 is provided below main body 2. A plurality of elements constituting cooling apparatus 6 that cools storage chamber 210 of main body 2 are stored in machine accommodation section 5. A specific configuration of machine accommodation section 5 and the elements constituting cooling apparatus 6 accommodated in machine accommodation section 5 will be described below.

Here, a configuration of cooling apparatus 6 will be described with reference to FIGS. 2 and 3.

Cooling apparatus 6 includes cooling circuit 60, blowing apparatus 62, and control apparatus 63.

Cooling circuit 60 cools storage chamber 210 of housing body 21. Cooling circuit 60 includes compressor 601, condenser 602, drier 603, gas-liquid separator 604, expansion apparatus 605, evaporator 606, heat exchanger 607, second heat exchanger 608, and second expansion apparatus 609.

As shown in FIG. 2, each of elements 601 to 609 constituting cooling circuit 60 is connected to each other through pipe 600. The refrigerant circulates in cooling circuit 60.

Compressor 601 compresses the refrigerant such that a pressure value of the refrigerant is 1 MPa or more. As a result, the refrigerant circulates in cooling circuit 60. The high-temperature refrigerant compressed by compressor 601 flows into condenser 602. The refrigerant is a non-azeotropic mixed refrigerant in which a high-boiling-point refrigerant, a medium-boiling-point refrigerant having a boiling point lower than the high-boiling-point refrigerant, and a low-boiling-point refrigerant having a boiling point lower than the medium-boiling-point refrigerant are mixed.

Condenser 602 is, for example, a wire tube type condenser. As a result, the refrigerant can be efficiently cooled. The refrigerant that has passed through condenser 602 flows into drier 603. Condenser 602 may be, for example, a pipe-on-sheet type condenser, a cross fin type condenser, or a microchannel condenser.

Drier 603 removes moisture contained in the refrigerant. Since a function of drier 603 is the same as a function of a drier in a conventionally-known refrigeration apparatus, detailed description thereof will be omitted.

Gas-liquid separator 604 is disposed between drier 603 and second heat exchanger 608 described below. Gas-liquid separator 604 separates the refrigerant flowing from drier 603 toward second heat exchanger 608 into a gas phase refrigerant and a liquid phase refrigerant.

In the refrigerant flowing from drier 603 toward second heat exchanger 608, a part of the high-boiling-point refrigerant is liquefied. The liquid phase refrigerant flowing out of gas-liquid separator 604 is decompressed by second expansion apparatus 609. The liquid phase refrigerant flows into outer pipe 608b of second heat exchanger 608.

In outer pipe 608b of second heat exchanger 608, the liquid phase refrigerant joins a returning refrigerant and cools the refrigerant flowing in inner pipe 608a of second heat exchanger 608.

Meanwhile, the gas phase refrigerant is a high-boiling-point refrigerant, a medium-boiling-point refrigerant, and a low-boiling-point refrigerant in a gaseous state. The gas phase refrigerant flowing out of gas-liquid separator 604 flows into inner pipe 608a of second heat exchanger 608.

Heat exchanger 607 is a double pipe type heat exchanger. Heat exchanger 607 is disposed between drier 603 and evaporator 606. Inner pipe 607a of heat exchanger 607 constitutes expansion apparatus 605.

Expansion apparatus 605 is, for example, a capillary tube. The refrigerant flows from compressor 601 toward evaporator 606 through expansion apparatus 605. The refrigerant flows from evaporator 606 toward compressor 601 through outer pipe 607b of heat exchanger 607. Hereinafter, the refrigerant flowing from evaporator 606 toward compressor 601 will be referred to as the returning refrigerant.

Second heat exchanger 608 is a double pipe type heat exchanger. Second heat exchanger 608 is disposed between drier 603 and heat exchanger 607. The refrigerant flows from compressor 601 toward evaporator 606 through inner pipe 608a of second heat exchanger 608. The returning refrigerant flows through outer pipe 608b of second heat exchanger 608. Second heat exchanger 608 may be covered with an insulating material (for example, a foaming body).

Evaporator 606 is disposed around storage chamber 210 of housing body 21. Evaporator 606 vaporizes the refrigerant flowing in from expansion apparatus 605.

The refrigerant that has passed through evaporator 606 flows into compressor 601. In the present embodiment, expansion tank 610 is connected to pipe element 600a connected to an inlet of compressor 601.

Expansion tank 610 has a function of adjusting an amount of the refrigerant circulating in cooling circuit 60 by accommodating a part of the gas phase refrigerant flowing through pipe element 600a.

Among elements 601 to 610 constituting cooling circuit 60 having the above-described configuration, compressor 601, condenser 602, drier 603, gas-liquid separator 604, and expansion tank 610 are disposed in machine accommodation section 5.

Blowing apparatus 62 is a blowing machine such as a fan. In the present embodiment, cooling apparatus 6 includes at least blowing apparatus 62 that cools compressor 601 and condenser 602. In the present embodiment, blowing apparatus 62 is composed of one AC fan motor.

Blowing apparatus 62 is disposed in machine accommodation section 5. Blowing apparatus 62 is disposed at a position where compressor 601 and condenser can be cooled at the same time in machine accommodation section 5. A specific arrangement of blowing apparatus 62 will be described below.

Control apparatus 63 corresponds to an example of a controller, and includes main controller 630 and control relay section 631.

Main controller 630 is, for example, an electronic circuit board. Main controller 630 controls an operation of compressor 601 based on a detection value of temperature sensor 7 (see FIG. 2) described below.

Control relay section 631 is connected to a circuit that connects main controller 630 and compressor 601. Control relay section 631 switches between stopping and driving compressor 601 under the control of main controller 630.

Control apparatus 63 having the above-described configuration controls an operation of compressor 601 at the time of start-up and an operation of compressor 601 during normal operation. That is, in cooling control (hereinafter, also simply referred to as “cooling control”) for cooling storage chamber 210 of housing body 21, control apparatus 63 switches between stopping and driving compressor 601.

In the cooling control, a state in which compressor 601 is stopped is also referred to as a stopped state of compressor 601. In the cooling control, a state in which compressor 601 is driven is also referred to as a driven state of compressor 601. In the driven state, compressor 601 compresses and discharges the refrigerant. That is, compressor 601 causes the refrigerant to circulate in cooling circuit 60.

Control apparatus 63 is connected to a power supply (not shown) and compressor 601. In other words, compressor 601 is connected to the power supply via control apparatus 63.

Control apparatus 63 (specifically, main controller 630) controls an operation of blowing apparatus 62. In the cooling control, main controller 630 switches between stopping and driving blowing apparatus 62. In the cooling control, a state in which blowing apparatus 62 is stopped is also referred to as a stopped state of blowing apparatus 62. In the cooling control, a state in which blowing apparatus 62 is driven is also referred to as a driven state of blowing apparatus 62. A detailed function of control apparatus 63 (specifically, main controller 630) will be described below.

The control apparatus that controls the operation of compressor 601 and the control apparatus that controls the operation of blowing apparatus 62 may be different control apparatuses. In this case, the control apparatus that controls the operation of compressor 601 and the control apparatus that controls the operation of blowing apparatus 62 may be communicably connected to each other.

Next, the arrangement of elements 601 to 604, 610, 62, and 631 constituting cooling apparatus 6 accommodated in machine accommodation section 5 will be described with reference to FIG. 3. FIG. 3 is a plan view of machine accommodation section 5 as viewed from above.

The upper side in FIG. 3 corresponds to a rear side of refrigeration apparatus 1. The lower side in FIG. 3 corresponds to a front side of refrigeration apparatus 1. The right side in FIG. 3 corresponds to a right side of refrigeration apparatus 1. The left side in FIG. 3 corresponds to a left side of refrigeration apparatus 1.

Machine accommodation section 5 has a box-shaped accommodation space 50. Machine accommodation section 5 includes bottom wall portion 51, front wall portion 52, rear wall portion 53, left wall portion 54, right wall portion 55, and an upper wall portion (not shown).

A space surrounded by bottom wall portion 51, front wall portion 52, rear wall portion 53, left wall portion 54, right wall portion 55, and the upper wall portion (not shown) is accommodation space 50.

Bottom wall portion 51 is a rectangular plate shape parallel to the front-rear direction and the left-right direction, and constitutes a bottom surface of machine accommodation section 5.

Front wall portion 52 is a rectangular plate shape parallel to the up-down direction and the left-right direction, and constitutes a front side surface of machine accommodation section 5. Front wall portion 52 has front side ventilation port 520 that extends through front wall portion 52 in the front-rear direction.

Rear wall portion 53 is a rectangular plate shape parallel to the up-down direction and the left-right direction, and constitutes a rear side surface of machine accommodation section 5. Rear wall portion 53 faces front wall portion 52 in the front-rear direction. Rear wall portion 53 has rear side ventilation port 530 that extends through rear wall portion 53 in the front-rear direction.

Left wall portion 54 is a rectangular plate shape parallel to the up-down direction and the front-rear direction, and constitutes a left side surface of machine accommodation section 5.

Right wall portion 55 is a rectangular plate shape parallel to the up-down direction and the front-rear direction, and constitutes a right side surface of machine accommodation section 5. Right wall portion 55 faces left wall portion 54 in the left-right direction.

The upper wall portion (not shown) is a rectangular plate shape parallel to the front-rear direction and the left-right direction, and constitutes an upper surface of machine accommodation section 5. The upper wall portion (not shown) faces bottom wall portion 51 in the up-down direction. The upper wall portion (not shown) may be regarded as the bottom wall portion of main body 2.

Compressor 601, condenser 602, drier 603, gas-liquid separator 604, expansion tank 610, blowing apparatus 62, and control relay section 631 are disposed in accommodation space 50 of machine accommodation section 5.

In the present embodiment, all of compressor 601, condenser 602, drier 603, gas-liquid separator 604, expansion tank 610, blowing apparatus 62, and control relay section 631 are disposed in right-side accommodation space 500a that is a space on one side of accommodation space 50 in the left-right direction (specifically, a right half space).

In other words, all of compressor 601, condenser 602, drier 603, gas-liquid separator 604, expansion tank 610, blowing apparatus 62, and control relay section 631 are disposed in a space on a right side of double-dotted chain line α₁ shown in FIG. 3 in accommodation space 50. Double-dotted chain line α₁ is a straight line parallel to the front-rear direction, and is a line indicating a middle position of accommodation space 50 in the left-right direction. The space on the right side of double-dotted chain line α₁ shown in FIG. 3 is right-side accommodation space 500a.

Compressor 601 is disposed in a rear half portion of right-side accommodation space 500a. Condenser 602 is disposed in a front half portion of right-side accommodation space 500a. More specifically, condenser 602 is disposed in right-side accommodation space 500a in the vicinity of front wall portion 52.

Compressor 601 and condenser 602 are provided on a straight line (double-dotted chain line α₂ shown in FIG. 3) parallel to the front-rear direction. Double-dotted chain line α₂ shown in FIG. 3 may be regarded as a straight line passing through centers of compressor 601 and condenser 602 in the left-right direction.

Double-dotted chain line α₂ shown in FIG. 3 is an imaginary line passing through a space on one side half in right-side accommodation space 500a (specifically, a right half space). The right half space in right-side accommodation space 500a may be regarded as a space on the most right side in a case where accommodation space 50 is divided into four in the left-right direction.

Centers of compressor 601 and condenser 602 in the left-right direction are present in the right half space in right-side accommodation space 500a. The right half space in right-side accommodation space 500a is a space on the right side of double-dotted chain line α₃ shown in FIG. 3 in accommodation space 50.

As described above, compressor 601 and condenser 602 are disposed at positions offset on the right side in accommodation space 50. Actions and effects obtained from such a configuration will be described below.

Blowing apparatus 62 is disposed between compressor 601 and condenser 602 in the front-rear direction. Specifically, blowing apparatus 62 is disposed on a front side of compressor 601. Blowing apparatus 62 is disposed on a rear side of condenser 602.

Blowing apparatus 62 is disposed on double-dotted chain line α₂ shown in FIG. 3. That is, compressor 601, condenser 602, and blowing apparatus 62 are provided on a straight line (double-dotted chain line α₂ shown in FIG. 3) parallel to the front-rear direction.

As shown by arrows A₂ and A₃ in FIG. 3, blowing apparatus 62 sucks air (cooling air) from the front side and blows the air to the rear side. The air sucked by blowing apparatus 62 is air that has passed through front side ventilation port 520 of front wall portion 52 and has entered accommodation space 50 of machine accommodation section 5 from the outside.

Condenser 602 is cooled by the air sucked by blowing apparatus 62 flowing around condenser 602. In this manner, blowing apparatus 62 cools condenser 602.

Blowing apparatus 62 blows the air toward compressor 601. Compressor 601 is cooled by the air blown by blowing apparatus 62 flowing around compressor 601. In this manner, blowing apparatus 62 cools compressor 601.

As described above, in the present embodiment, compressor 601 and condenser 602 are cooled by one blowing apparatus 62. Such a configuration contributes to a reduction in the number of components of cooling apparatus 6 and a reduction in the size of cooling apparatus 6. A flow of the air in accommodation space 50 will be described below.

Control apparatus 63 is disposed on one side (specifically, the left side) of compressor 601 in the left-right direction of compressor 601.

In the present embodiment, control apparatus 63 is disposed on the left side of compressor 601 and between compressor 601 and condenser 602 in the front-rear direction. In other words, control apparatus 63 is disposed at a position facing front passage P₁ present between compressor 601 and condenser 602 from the left side. Front passage P₁ extends in the left-right direction.

Control apparatus 63 blocks the air flowing in front passage P₁ in a direction indicated by arrow A₄ in FIG. 3. Control apparatus 63 is cooled by this air and guides the air to the rear.

Expansion tank 610 corresponds to an example of a first device, and is disposed in rear of control apparatus 63. Expansion tank 610 is disposed on a straight line (double-dotted chain line α₄ shown in FIG. 3) passing through a center of control apparatus 63 and parallel to the front-rear direction.

Drier 603 and gas-liquid separator 604 are disposed on a right side of compressor 601 and on a left side of right wall portion 55 of machine accommodation section 5 in right-side accommodation space 500a.

Compressor 601, condenser 602, drier 603, gas-liquid separator 604, expansion tank 610, blowing apparatus 62, and control relay section 631 as described above are connected to each other in the relationship shown in FIG. 2.

Next, a flow of the air in accommodation space 50 of machine accommodation section 5 will be described with reference to FIG. 3. In accommodation space 50, in a case where blowing apparatus 62 is operated, the air enters accommodation space 50 from the outside of accommodation space 50 through front side ventilation port 520 of front wall portion 52 as indicated by arrow A₁.

The front side, the rear side, the left side, and the right side with respect to the flow of the air in accommodation space 50 are determined based on a positional relationship between compressor 601 and blowing apparatus 62. That is, the directions related to the flow of the air in accommodation space 50 may be different from the directions indicated by the orthogonal coordinate system (X, Y, Z) shown in FIGS. 1 and 3 depending on the positional relationship between compressor 601 and blowing apparatus 62.

Specifically, a direction in which blowing apparatus 62 is disposed with respect to compressor 601 is the front side. A direction opposite to the direction in which blowing apparatus 62 is disposed with respect to compressor 601 is the rear side.

In the present embodiment, the front-rear direction related to the flow of the air in accommodation space 50 matches the front-rear direction related to refrigeration apparatus 1 (that is, the X direction in the orthogonal coordinate system shown in FIGS. 1 and 3).

In addition, the left-right direction in a case in which compressor 601 is viewed from blowing apparatus 62 matches the left-right direction related to the flow of the air in accommodation space 50. In the present embodiment, the left-right direction related to the flow of the air in accommodation space 50 matches the left-right direction related to refrigeration apparatus 1 (that is, the Y direction in the orthogonal coordinate system shown in FIGS. 1 and 3).

Specifically, the left side in a case in which compressor 601 is viewed from blowing apparatus 62 is the left side related to the flow of the air in accommodation space 50. In addition, the right side in a case in which compressor 601 is viewed from blowing apparatus 62 is the right side related to the flow of the air in accommodation space 50.

The directions related to the flow of the air in accommodation space 50 are also applied to directions related to the arrangement of compressor 601, condenser 602, drier 603, gas-liquid separator 604, expansion tank 610, blowing apparatus 62, and control relay section 631 in accommodation space 50.

Hereinafter, the descriptions related to the flow of the air in accommodation space 50 will be made again. The air that has entered accommodation space 50 from the outside of accommodation space 50 passes through condenser 602 and is sucked into blowing apparatus 62 from the front side as indicated by arrow A₂ in FIG. 3. In this case, condenser 602 is cooled by the air passing through condenser 602.

Next, the air sucked into blowing apparatus 62 is blown to the rear side of blowing apparatus 62 as indicated by arrow A₃ in FIG. 3. The air blown from blowing apparatus 62 is blown to compressor 601 from the front side as indicated by arrow A₃ in FIG. 3. In this case, compressor 601 is cooled by the air blown by blowing apparatus 62.

The air blown to compressor 601 is split by housing 601a of compressor 601.

Here, the structure of compressor 601 will be briefly described. Compressor 601 includes housing 601a. As shown in FIG. 3, housing 601a has an elliptical shape in plan view. That is, compressor 601 has an elliptical shape in plan view. The plan view means viewing compressor 601 from above.

Compressor 601 (specifically, housing 601a) is disposed on a straight line (specifically, double-dotted chain line α₂ in FIG. 3) including a major axis of the elliptical shape, which is the shape of housing 601a in plan view. Therefore, blowing apparatus 62 and condenser 602 are also disposed on the straight line (specifically, double-dotted chain line α₂ in FIG. 3) including the major axis of the elliptical shape, which is the shape of housing 601a in plan view.

The air blown to housing 601a hits a front surface of housing 601a and is split at least in the left-right direction along the front surface of housing 601a. Specifically, the air blown to housing 601a hits the front surface of housing 601a and is radially split along the front surface of housing 601a.

The amount of the air split by the front surface of housing 601a in each direction is determined by a shape of the front surface of housing 601a. In the present embodiment, the amount of the air split by the front surface of housing 601a is the largest in the left-right direction. Hereinafter, the flow of the air split in the left-right direction by the front surface of housing 601a will be described. The flow of the air split in a direction other than the left-right direction by the front surface of housing 601a will be omitted from the description.

The air split to the left side by the front surface of housing 601a flows toward the left side in front passage P₁ present between compressor 601 and condenser 602 as indicated by arrow A₄ in FIG. 3. The air flowing toward the left side in front passage P₁ hits control apparatus 63.

In this case, control relay section 631 is cooled by the air flowing in front passage P₁ and hitting control relay section 631. Then, control relay section 631 guides the air flowing in front passage P₁ and hitting control relay section 631 to the rear as indicated by arrow A₅ in FIG. 3. Control relay section 631 does not need to guide all of the air flowing in front passage P₁ and hitting control relay section 631 to the rear.

The air guided to the rear by control relay section 631 flows to the rear through left passage P₂ formed on the left side of compressor 601. Left passage P₂ corresponds to an example of a first passage. Left passage P₂ is a passage extending in the front-rear direction, which is formed by compressor 601, control relay section 631, and expansion tank 610.

Compressor 601 functions as a wall portion on one side (specifically, the right side) of left passage P₂. In addition, control relay section 631 and expansion tank 610 function as wall portions on the other side (specifically, the left side) of left passage P₂. Therefore, expansion tank 610 together with control relay section 631 guides the air split by compressor 601 to the rear.

Another device (that is, the first device) may be disposed at a position of expansion tank 610 shown in FIG. 3. Examples of the other device include gas-liquid separator 604. In this case, gas-liquid separator 604 may include a cylindrical separation section (not shown) that separates the refrigerant and a plate-shaped base portion (not shown) that supports the separation section on bottom wall portion 51 of machine accommodation section 5. Then, gas-liquid separator 604 may be disposed at a position of expansion tank 610 in FIG. 3 in a state where the base portion is along left passage P₂ in FIG. 3.

The air flowing in left passage P₂ flows along a side surface (specifically, a left side surface) of compressor 601 on one side. In this case, compressor 601 is cooled by the air flowing in left passage P₂.

Thereafter, the air flowing in left passage P₂ flows to the rear of compressor 601 as indicated by arrow A₆ in FIG. 3. Then, the air flowing to the rear of compressor 601 is discharged to the outside of accommodation space 50 through rear side ventilation port 530 of rear wall portion 53 as indicated by arrow A₁₀ in FIG. 3.

On the other hand, the air split to the right side by the front surface of housing 601a flows toward the right side in front passage P₁ present between compressor 601 and condenser 602 as indicated by arrow A₇ in FIG. 3. Then, the air flowing toward the right side in front passage P₁ hits right wall portion 55 of machine accommodation section 5.

Then, right wall portion 55 guides the air flowing in front passage P₁ and hitting right wall portion 55 to the rear as indicated by arrow A₈ in FIG. 3. Right wall portion 55 does not need to guide all of the air flowing in front passage P₁ and hitting right wall portion 55 to the rear.

Right wall portion 55 corresponds to an example of a sidewall portion. The air guided to the rear by right wall portion 55 flows to the rear through right passage P₃ formed on the right side of compressor 601. Right passage P₃ corresponds to an example of a second passage. Right passage P₃ is a passage extending in the front-rear direction, which is formed by compressor 601 and right wall portion 55.

Compressor 601 functions as a wall portion on one side (specifically, the left side) of right passage P₃. In addition, right wall portion 55 functions as a wall portion on the other side (specifically, the right side) of right passage P₃. In the present embodiment, compressor 601, condenser 602, and blowing apparatus 62 are disposed at positions offset on the right side in accommodation space 50. Therefore, right wall portion 55 can be used as the wall portion on the right side of right passage P₃.

The air flowing in right passage P₃ flows along a side surface (specifically, a right side surface) of compressor 601 on the other side. In this case, compressor 601 is cooled by the air flowing in right passage P₃. In addition, the air flowing in right passage P₃ cools drier 603 and gas-liquid separator 604. Drier 603 and gas-liquid separator 604 do not hinder the flow of the air flowing in right passage P₃ as long as the height is low.

Thereafter, the air flowing in right passage P₃ flows to the rear of compressor 601 as indicated by arrow A₉ in FIG. 3. Then, the air flowing to the rear of compressor 601 is discharged to the outside of accommodation space 50 through rear side ventilation port 530 of rear wall portion 53 as indicated by arrow A₁₀ in FIG. 3.

Next, an operation of compressor 601 and blowing apparatus 62 will be described. The operation of compressor 601 and blowing apparatus 62 is controlled by control apparatus 63. In the cooling control for cooling storage chamber 210 of housing body 21, control apparatus 63 switches between stopping and driving compressor 601. In addition, in the cooling control for cooling storage chamber 210, control apparatus 63 (specifically, main controller 630) switches between stopping and driving blowing apparatus 62.

In the present embodiment, control apparatus 63 switches between stopping and driving compressor 601 based on a temperature of storage chamber 210 of housing body 21. Therefore, refrigeration apparatus 1 includes temperature sensor 7 (see FIG. 2) that detects the temperature of storage chamber 210 of housing body 21. Temperature sensor 7 is provided at a predetermined position of storage chamber 210. Temperature sensor 7 transmits the detection value to control apparatus 63 (specifically, main controller 630).

Specifically, in a case where the temperature of storage chamber 210 satisfies a predetermined condition (hereinafter, referred to as a first predetermined condition), main controller 630 controls control relay section 631 to drive compressor 601. The first predetermined condition is that the temperature of storage chamber 210 is higher than a target temperature (for example, −80° C.) by a predetermined value (hereinafter, referred to as a “first predetermined value”).

In addition, in a case where the temperature of storage chamber 210 satisfies a predetermined condition (hereinafter, referred to as a second predetermined condition), main controller 630 controls control relay section 631 to stop compressor 601. The second predetermined condition is that the temperature of storage chamber 210 is equal to or substantially equal to the target temperature (for example, −80° C.).

As described above, the driving time period of compressor 601 changes depending on the temperature of storage chamber 210. In addition, the stop time period of compressor 601 is equal to or longer than a minimum stop time period. The minimum stop time period corresponds to an example of a second predetermined time period and is a time period set in advance. Main controller 630 stores the minimum stop time period.

Main controller 630 does not drive compressor 601 even in a case where the temperature of storage chamber 210 satisfies the first predetermined condition in a case where the time period during which compressor 601 is stopped is shorter than the minimum stop time period. In this case, main controller 630 drives compressor 601 at a time point at which the time period during which compressor 601 is stopped is equal to or longer than the minimum stop time period.

In addition, in the blowing control of switching between stopping and driving blowing apparatus 62, main controller 630 drives blowing apparatus 62 after set start time period T_set (see FIG. 4) after compressor 601 is stopped. Set start time period T_set corresponds to an example of a first predetermined time period and is a time period set in advance. Main controller 630 stores the set start time period. Set start time period T_set (first predetermined time period) is shorter than the above-described minimum stop time period (second predetermined time period).

As is understood, main controller 630 drives blowing apparatus 62 after the set start time period after compressor 601 is stopped, so that machine accommodation section 5 can be ventilated before compressor 601 is driven next. Therefore, even in a case where the refrigerant leaks in machine accommodation section 5, the concentration of the refrigerant in machine accommodation section 5 is reduced before compressor 601 is driven.

In addition, main controller 630 drives blowing apparatus 62 after the set start time period after compressor 601 is stopped, so that the rotational speed of blowing apparatus 62 can be maximized at the time point when compressor 601 is driven next. As a result, in a state where compressor 601 is driven, blowing apparatus 62 can efficiently cool compressor 601.

In addition, main controller 630 stops blowing apparatus 62 at the same time as compressor 601 is stopped. Such a configuration contributes to energy saving. The timing at which compressor 601 is stopped and the timing at which blowing apparatus 62 is stopped may be different from each other.

Next, the timing of the operation of compressor 601 and the timing of the operation of blowing apparatus 62 will be described with reference to FIG. 4. FIG. 4 is a line diagram showing a timing of an operation of compressor 601 and blowing apparatus 62.

In FIG. 4, pulse waveform L₁ indicated by a thin solid line indicates the timing of the operation of compressor 601. In a case where the waveform of pulse waveform L₁ rises, compressor 601 is driven (that is, the driven state is established).

In a case where the waveform of pulse waveform L₁ falls, compressor 601 is stopped (that is, the stopped state is established). In the cooling control, compressor 601 repeats driving (ON) and stopping (OFF) under the control of main controller 630. The horizontal axis of FIG. 4 represents time.

In addition, in FIG. 4, pulse waveform L₂ indicated by a thick solid line indicates the timing of the operation of blowing apparatus 62. In a case where the waveform of pulse waveform L₂ rises, blowing apparatus 62 is driven (that is, the driven state is established).

In a case where the waveform of pulse waveform L₂ falls, blowing apparatus 62 is stopped (that is, the stopped state is established). In the cooling control, blowing apparatus 62 repeats driving (ON) and stopping (OFF) under the control of main controller 630. For convenience of description, in FIG. 4, the height of pulse waveform L₁ and the height of pulse waveform L₂ are different from each other.

In addition, in FIG. 4, concentration C of the refrigerant in machine accommodation section 5 in a case where it is assumed that the refrigerant has leaked in machine accommodation section 5 is indicated by a dotted line. The horizontal axis of FIG. 4 is time with respect to concentration C of the refrigerant. The vertical axis of FIG. 4 is concentration with respect to concentration C of the refrigerant.

In FIG. 4, the scale indicating the concentration on the vertical axis is omitted. In addition, for convenience of description, concentration C of the refrigerant in FIG. 4 is shown to repeatedly change between maximum concentration C_high and minimum concentration C_low.

In addition, in FIG. 4, temperature T of storage chamber 210 is indicated by a single-dotted chain line. The horizontal axis of FIG. 4 is time with respect to temperature T of storage chamber 210. The vertical axis of FIG. 4 is temperature with respect to temperature T of storage chamber 210. In FIG. 4, the scale indicating the temperature on the vertical axis is omitted.

As shown in FIG. 4, in a case where the cooling control starts, main controller 630 controls control relay section 631 at time t₁ in FIG. 4 to drive compressor 601. In this case, blowing apparatus 62 is stopped.

Then, in a case where the temperature of storage chamber 210 reaches the target temperature (for example, −80° C.), main controller 630 controls control relay section 631 at time t₂ in FIG. 4 to stop compressor 601. A difference between time t₂ and time t₁ in FIG. 4 is the driving time period of compressor 601. The driving time period of compressor 601 changes depending on the rate of change of the temperature of storage chamber 210.

After having stopped compressor 601, main controller 630 determines a time (time T₁ in FIG. 4) at which blowing apparatus 62 is driven based on the time (time t₂ in FIG. 4) at which compressor 601 is stopped.

Specifically, main controller 630 determines, as the time at which blowing apparatus 62 is driven, a time obtained by adding set start time period T_set stored in advance to time t₂. That is, a difference between time T₁ and time t₂ in FIG. 4 is set start time period T_set.

Main controller 630 controls control relay section 631 to stop compressor 601, and then controls control relay section 631 to drive blowing apparatus 62 after set start time period T_set. In other words, main controller 630 drives blowing apparatus 62 at time T₁ in FIG. 4 after compressor 601 is stopped.

In a case where it is assumed that the refrigerant has leaked in machine accommodation section 5, as shown by the dotted line (concentration C of the refrigerant in machine accommodation section 5) in FIG. 4, concentration C of the refrigerant in machine accommodation section 5 increases with increasing elapsed time period from time t₁ at which compressor 601 is driven.

For convenience of description, in FIG. 4, concentration C of the refrigerant in machine accommodation section 5 is maximum concentration C_high immediately before time T₁ at which blowing apparatus 62 is driven.

In a case where compressor 601 is driven in a state where concentration C of the refrigerant in machine accommodation section 5 is maximum concentration C_high, and the refrigerant is flammable, the refrigerant may be ignited. Therefore, in the present embodiment, main controller 630 drives blowing apparatus 62 before time t₃ at which compressor 601 is driven.

The time at which compressor 601 is driven is not determined in advance. That is, the time at which compressor 601 is driven changes depending on temperature T of storage chamber 210. Therefore, the time at which blowing apparatus 62 is driven cannot be determined with reference to the time at which compressor 601 is driven. Therefore, in the present embodiment, the time at which blowing apparatus 62 is driven is determined with reference to the time (time t₂ in FIG. 4) at which compressor 601 is stopped.

In addition, main controller 630 drives blowing apparatus 62 at time T₁, and then drives compressor 601 at time t₃ in FIG. 4. Main controller 630 determines the timing at which compressor 601 is driven based on the temperature of storage chamber 210.

That is, main controller 630 drives compressor 601 in a case where the temperature of storage chamber 210 of housing body 21 satisfies the predetermined condition (first predetermined condition). In this case, blowing apparatus 62 is being driven (that is, in the driven state). Since blowing apparatus 62 is driven before time t₃ in FIG. 4, as shown by concentration C of the refrigerant in FIG. 4, concentration C of the refrigerant at time t₃ in FIG. 4 is minimum concentration C_low.

In addition, main controller 630 stops compressor 601 at time t₄ in FIG. 4. Main controller 630 determines the timing at which compressor 601 is stopped based on the temperature of storage chamber 210 of housing body 21.

That is, in a case where the temperature of storage chamber 210 reaches the target temperature (for example, −80° C.), main controller 630 stops compressor 601 at time t₄ in FIG. 4. In addition, main controller 630 stops blowing apparatus 62 at the same time as compressor 601 is stopped.

The timing at which main controller 630 stops blowing apparatus 62 is the same as the timing at which compressor 601 is stopped. Therefore, in the driven state of compressor 601, compressor 601 is always cooled by blowing apparatus 62.

As a result, compressor 601 is efficiently cooled by blowing apparatus 62. Thereafter, main controller 630 determines a time (time T₃ in FIG. 4) at which blowing apparatus 62 is driven based on the time (time t₄ in FIG. 4) at which compressor 601 is stopped after compressor 601 is stopped. Subsequent control on compressor 601 and blowing apparatus 62 performed by main controller 630 is as described above.

Actions and Effects of the Present Embodiment

According to refrigeration apparatus 1 of the present embodiment having the above-described configuration, it is possible to provide a refrigeration apparatus that can reduce the concentration of the refrigerant in machine accommodation section 5 in a case where the refrigerant has leaked in machine accommodation section 5. The reason for this is as described above.

In addition, in the present embodiment, the layout of machine accommodation section 5 as described above is adopted. Therefore, in machine accommodation section 5, the air taken in from the outside by blowing apparatus 62 can be efficiently guided to the outside as indicated by the arrows A₁ to A₁₀ in FIG. 3. That is, in a case where the refrigerant has leaked in machine accommodation section 5, machine accommodation section 5 can be efficiently ventilated.

In particular, in the present embodiment, blowing apparatus 62 and condenser 602 are disposed on the same straight line (on double-dotted chain line α₂ shown in FIG. 3). Therefore, in a case where it is assumed that the refrigerant has leaked in condenser 602, the leaked refrigerant can be efficiently guided to the outside as indicated by the arrows A₁ to A₁₀ in FIG. 3.

Embodiment 2

The refrigeration apparatus according to Embodiment 2 of the present invention will be described with reference to FIGS. 2, 3, and 5. FIG. 5 is a line diagram showing the timing of the operation of compressor 601 and blowing apparatus 62. In the present embodiment, the control operation of main controller 630 in control apparatus 63 is different from the control operation of main controller 630 in Embodiment 1. The configuration other than the function of main controller 630 is the same as the configuration of refrigeration apparatus 1 according to Embodiment 1 described above. Therefore, the description of the configuration other than the function of main controller 630 will be made with reference to FIGS. 2 and 3.

In the present embodiment, main controller 630 performs temporary driving control of temporarily driving blowing apparatus 62 before set start time period T_set elapses after compressor 601 is stopped. Set start time period T_set is a time period set in advance.

In FIG. 5, the control performed by main controller 630 after blowing apparatus 62 is driven at time T_a in FIG. 5 until when blowing apparatus 62 is stopped at time T_b in FIG. 5 is the temporary driving control.

Hereinafter, the timing of the operation of compressor 601 and the timing of the operation of blowing apparatus 62 in the present embodiment will be described with reference to FIG. 5. FIG. 5 is a line diagram showing the timing of the operation of compressor 601 and blowing apparatus 62.

In FIG. 5, pulse waveform L_1a indicated by a thin solid line indicates the timing of the operation of compressor 601. In a case where the waveform of pulse waveform L_1a rises, compressor 601 is driven (that is, the driven state is established).

In a case where the waveform of pulse waveform L_1a falls, compressor 601 is stopped (that is, the stopped state is established). In the cooling control, compressor 601 repeats driving (ON) and stopping (OFF) under the control of main controller 630. The horizontal axis of FIG. 5 is time.

In addition, in FIG. 5, pulse waveforms L_2a and L_2b indicated by thick solid lines indicate the timings of the operation of blowing apparatus 62. In a case where the waveform of pulse waveforms L_2a and L_2b rises, blowing apparatus 62 is driven (that is, the driven state is established).

In a case where the waveform of pulse waveforms L_2a and L_2b falls, blowing apparatus 62 is stopped (that is, the stopped state is established). In the cooling control, blowing apparatus 62 repeats driving (ON) and stopping (OFF) under the control of main controller 630. For convenience of description, in FIG. 4, the height of pulse waveform L_1a and the height of pulse waveforms L_2a and L_2b are different from each other.

In addition, in FIG. 5, concentration C of the refrigerant in machine accommodation section 5 in a case where it is assumed that the refrigerant has leaked in machine accommodation section 5 is indicated by a dotted line. The horizontal axis of FIG. 4 is time with respect to concentration C of the refrigerant.

The vertical axis of FIG. 5 is concentration with respect to concentration C of the refrigerant. In FIG. 5, the scale indicating the concentration on the vertical axis is omitted. In addition, for convenience of description, concentration C of the refrigerant in FIG. 5 is shown to repeatedly change between maximum concentration C_high and minimum concentration C_low.

In addition, in FIG. 5, temperature T of storage chamber 210 (see FIG. 2) of housing body 21 is indicated by a single-dotted chain line. The horizontal axis of FIG. 5 is time with respect to temperature T of storage chamber 210. The vertical axis of FIG. 5 is temperature with respect to temperature T of storage chamber 210. In FIG. 5, the scale indicating the temperature on the vertical axis is omitted.

As shown in FIG. 5, in a case where the cooling control starts, main controller 630 first drives compressor 601 at time t₁ in FIG. 5. In this case, blowing apparatus 62 is stopped.

Then, in a case where the temperature of storage chamber 210 reaches the target temperature (for example, −80° C.), main controller 630 stops compressor 601 at time t₂ in FIG. 5. A difference between time t₂ and time t₁ in FIG. 5 is the driving time period of compressor 601. The driving time period of compressor 601 changes depending on the rate of change of the temperature of storage chamber 210.

After having stopped compressor 601, main controller 630 determines a time (time T₁ in FIG. 5) at which blowing apparatus 62 is driven based on the time (time t₂ in FIG. 5) at which compressor 601 is stopped.

Specifically, main controller 630 determines, as the time at which blowing apparatus 62 is driven, a time obtained by adding set start time period T_set stored in advance to time t₂. That is, a difference between time T₁ and time t₂ in FIG. 4 is set start time period T_set.

In the present embodiment, set start time period T_set is longer than set start time period T_set in Embodiment 1 described above. That is, the time period from the stop of compressor 601 to the driving of blowing apparatus 62 is long. In the present embodiment, set start time period T_set may be set in advance.

The reason why set start time period T_set in the present embodiment is longer than set start time period T_set in Embodiment 1 is, for example, that the stop time period of compressor 601 is long.

The stop time period of compressor 601 is a time period from time t₂ to time t₃ in FIG. 5. Main controller 630 determines the timing (for example, time t₃ in FIG. 5) at which compressor 601 is stopped based on the temperature of storage chamber 210. Therefore, the stop time period of compressor 601 is not a value determined in advance.

However, the stop time period of compressor 601 can be estimated based on information on a usage status of refrigeration apparatus 1. Main controller 630 may determine set start time period T_set according to the estimated stop time period of compressor 601 based on the information on the usage status of refrigeration apparatus 1. That is, in the present embodiment, set start time period T_set may be a variable value determined by main controller 630.

For example, main controller 630 can estimate the stop time period of compressor 601 based on the temperature of storage chamber 210 and the temperature of the outside of refrigeration apparatus 1 (in other words, the temperature of the outside air). In a case where the temperature of the outside of refrigeration apparatus 1 is relatively low, the temperature of storage chamber 210 is not likely to increase relatively. Therefore, the stop time period of compressor 601 is relatively long.

On the contrary, in a case where the temperature of the outside of refrigeration apparatus 1 is relatively high, the temperature of storage chamber 210 is likely to increase relatively. Therefore, the stop time period of compressor 601 is relatively short. Main controller 630 estimates the stop time period of compressor 601 by such a method.

Then, main controller 630 may set set start time period T_set based on the estimated stop time period of compressor 601. In the present embodiment, main controller 630 performs the temporary driving control in a case where the stop time period of the compressor is longer than a third predetermined time period. The third predetermined time period may be a time period set in advance.

Hereinafter, the description of FIG. 5 will be returned. In the present embodiment, main controller 630 drives blowing apparatus 62 at time t_a between the time (time t₂ in FIG. 5) at which compressor 601 is stopped and the time (time T₁ in FIG. 5) at which blowing apparatus 62 is scheduled to be driven. That is, main controller 630 starts the temporary driving control of blowing apparatus 62.

Then, main controller 630 stops blowing apparatus 62 after a predetermined time has elapsed from the driving of blowing apparatus 62 (that is, at time T_a in FIG. 5). That is, main controller 630 ends the temporary driving control of blowing apparatus 62. In a situation where the temporary driving control is being performed, compressor 601 is stopped.

The driving time period (that is, the difference between time T_b and time T_a) of blowing apparatus 62 in the temporary driving control may be a time period determined in advance. Main controller 630 may store the driving time period of blowing apparatus 62 in the temporary driving control. The temporary driving control of blowing apparatus 62 can efficiently ventilate machine accommodation section 5 in a case where the stop time period of compressor 601 is long.

Next, main controller 630 drives blowing apparatus 62 after set start time period T_set has elapsed from time t₂ at which compressor 601 was stopped (that is, at time T₁). Such control by main controller 630 may be referred to as normal driving control of blowing apparatus 62.

That is, in the present embodiment, main controller 630 performs the temporary driving control of blowing apparatus 62 together with the normal driving control of blowing apparatus 62.

In a case where it is assumed that the refrigerant has leaked in machine accommodation section 5, as shown by the dotted line (concentration C of the refrigerant in machine accommodation section 5) in FIG. 5, concentration C of the refrigerant in machine accommodation section 5 increases with increasing elapsed time period from time t₁ at which compressor 601 is driven.

In the present embodiment, since main controller 630 performs the above-described temporary driving control, concentration C of the refrigerant in machine accommodation section 5 is reduced after the temporary driving control is performed (that is, after time T_a). In this way, since blowing apparatus 62 is driven at time T₁, machine accommodation section 5 can be reliably ventilated before time t₃ at which compressor 601 is driven. That is, in a case where it is assumed that the refrigerant has leaked in machine accommodation section 5, concentration C of the refrigerant in machine accommodation section 5 can be reliably reduced before time t₃ at which compressor 601 is driven.

In addition, main controller 630 drives compressor 601 at time t₃ in FIG. 5 after having driven blowing apparatus 62 at time T₁. Main controller 630 determines the timing at which compressor 601 is driven based on the temperature of storage chamber 210.

That is, main controller 630 drives compressor 601 in a case where the temperature of storage chamber 210 satisfies the predetermined condition (first predetermined condition). In this case, blowing apparatus 62 is being driven (that is, in the driven state). Since blowing apparatus 62 is driven before time t₃ in FIG. 5, concentration C of the refrigerant at time t₃ in FIG. 5 is minimum concentration C_low as shown by concentration C of the refrigerant in FIG. 5.

In addition, main controller 630 stops compressor 601 at time t₄ in FIG. 5. Main controller 630 determines the timing at which compressor 601 is stopped based on the temperature of storage chamber 210.

That is, in a case where the temperature of storage chamber 210 reaches the target temperature (for example, −80° C.), main controller 630 stops the compressor at time t₄ in FIG. 5. In addition, main controller 630 stops blowing apparatus 62 at the same time as compressor 601 is stopped.

The timing at which main controller 630 stops blowing apparatus 62 is the same as the timing at which compressor 601 is stopped. Therefore, in the driven state of compressor 601, compressor 601 is always cooled by blowing apparatus 62.

As a result, compressor 601 is efficiently cooled by blowing apparatus 62. Thereafter, after having stopped compressor 601, main controller 630 determines a time (time T₃ in FIG. 5) at which blowing apparatus 62 is driven based on the time (time t₄ in FIG. 5) at which compressor 601 is stopped. Subsequent control on compressor 601 and blowing apparatus 62 performed by main controller 630 is as described above. Other configurations and actions/effects are the same as those of Embodiment 1 described above.

Supplementary Notes

In a case of implementing the refrigeration apparatus according to the present invention, the configuration of the machine accommodation section is not limited to the configuration of machine accommodation section 5 described above. For example, the machine accommodation section may be machine accommodation section 5A shown in FIG. 6. Machine accommodation section 5A is narrower than machine accommodation section 5 in the above-described embodiment. Specifically, the dimension of machine accommodation section 5A in the left-right direction is half of the dimension of machine accommodation section 5 in the left-right direction.

Machine accommodation section 5A has a box-shaped accommodation space 50A. Machine accommodation section 5A includes bottom wall portion 51A, front wall portion 52A, rear wall portion 53A, left wall portion 54A, right wall portion 55A, and an upper wall portion (not shown). The configurations of accommodation space 50A, bottom wall portion 51A, front wall portion 52A, rear wall portion 53A, left wall portion 54A, right wall portion 55A, and the upper wall portion (not shown) are substantially the same as the configurations of accommodation space 50, bottom wall portion 51, front wall portion 52, rear wall portion 53, left wall portion 54, right wall portion 55, and the upper wall portion in the above-described embodiment, except that the sizes are different. Other configurations shown in FIG. 6 are the same as the configurations shown in FIG. 3.

In addition, in the case of refrigeration apparatus 1 according to the above-described embodiment, compressor 601, condenser 602, and blowing apparatus 62 are disposed on a straight line (double-dotted chain line α₂ in FIG. 3) parallel to the front-rear direction. However, although not shown, the compressor, the condenser, and the blowing apparatus may be disposed on a straight line (not shown) parallel to a direction (for example, the left-right direction) other than the front-rear direction. Of course, such a configuration is also included in the technical scope of the present invention.

In addition, blowing apparatus 62 in the above-described embodiment is composed of one AC fan motor, but the configuration of the blowing apparatus is not limited to the configuration of blowing apparatus 62. For example, the blowing apparatus may be composed of a plurality (for example, four) of DC fan motors that are smaller than the AC fan motor constituting blowing apparatus 62. In this case, the four DC fan motors may be disposed in two rows in the up-down direction and two rows in the left-right direction.

Moreover, the refrigeration apparatus does not need to include all of the above-described configurations when the refrigeration apparatus according to the present invention is implemented. The configurations that the refrigeration apparatus has may be appropriately selected as long as no technical contradictions arise.

INDUSTRIAL APPLICABILITY

The present invention is applicable to various refrigeration apparatuses.

REFERENCE SIGNS LIST

• • 1 Refrigeration apparatus
  • 2 Main body
  • 21 Housing body
  • 210 Storage chamber
  • 22 Door
  • 5 Machine accommodation section
  • 50, 50A Accommodation space
  • 500a Right-side accommodation space
  • 51, 51A Bottom wall portion
  • 52, 52A Front wall portion
  • 520 Front side ventilation port
  • 53, 53A Rear wall portion
  • 530 Rear side ventilation port
  • 54, 54A Left wall portion
  • 55, 55A Right wall portion
  • P₁ Front passage
  • P₂ Left passage
  • P₃ Right passage
  • 6 Cooling apparatus
  • 60 Cooling circuit
  • 600 Pipe
  • 600a Pipe element
  • 601 Compressor
  • 601a Housing
  • 602 Condenser
  • 603 Drier
  • 604 Gas-liquid separator
  • 605 Expansion apparatus
  • 606 Evaporator
  • 607 Heat exchanger
  • 607a Inner pipe
  • 607b Outer pipe
  • 608 Second heat exchanger
  • 608a Inner pipe
  • 609 Second expansion apparatus
  • 610 Expansion tank
  • 62 Blowing apparatus
  • 63 Control apparatus
  • 630 Main controller
  • 631 Control relay section
  • 7 Temperature sensor