JP6056471B2 - Refrigeration air conditioner - Google Patents

Description

  The present invention relates to a refrigerating and air-conditioning apparatus that equalizes a flow velocity distribution of wind acting on an evaporator provided in a duct.

  Conventionally, a refrigeration air conditioner is configured such that a cooler unit that houses a refrigerant evaporator is connected to a lee of a blower unit that houses a blower, and air sent from the blower passes through the refrigerant evaporator.

For this reason, when the air flow changes abruptly between the blower and the refrigerant evaporator, when the inlet of the cooler unit is provided at the side of the cooler unit, not at the position facing the refrigerant evaporator, the refrigerant evaporator There is a bias in the amount of air passing through.
That is, since the air flowing in from the inlet of the cooler unit tends to go straight, the amount of air passing through the refrigerant evaporator is small near the inlet, and the amount of air passing through the refrigerant evaporator is large near the inlet.

  In the structure in which the outside air sucked from the fan is bent at a substantially right angle in the cooler case (cooler unit) and blown to the heat exchanger for cooling, at a position facing the inlet in the duct of the air blown from the fan, Guide plates and resistors are installed to block the air flow. After the air blown from the fan travels straight and collides with the guide plate or resistor, the air changes direction almost at right angles, and the outside air flows to the cooling heat exchanger, and the air velocity acting on the cooling heat exchanger A vehicle air conditioner that equalizes the distribution is shown. (See Patent Document 1)

JP-A-7-266844 (paragraphs 0021-0022, FIG. 1)

  However, when the evaporator is increased in size in the refrigeration air conditioner, even if a resistor or the like is installed at a position where the outside air blown from the fan is opposed to the inlet in the duct as in the configuration of Patent Document 1, it evaporates. There is a problem that it is difficult to make the flow velocity distribution acting on the vessel uniform.

The present invention solves the above problems,
An object of the present invention is to provide a refrigeration air conditioner capable of uniforming the flow velocity distribution of wind acting on an evaporator provided in a duct.

The refrigeration air conditioner of the present invention
A housing having a suction port through which air is sucked;
A blower port is formed, and a fan that blows the air from the suction port to the blower port;
A duct through which the air flows from the air outlet;
An evaporator disposed in the duct at a distance larger than the diameter of the fan from the air blowing port to the leeward side,
The air blown into the duct from the air outlet passes through the evaporator after colliding with a portion facing the air outlet in the duct ,
In the refrigerating and air-conditioning apparatus, a distance between the portion and the evaporator is longer than a diameter of the fan .

  The refrigerating and air-conditioning apparatus of the present invention can make the flow velocity distribution acting on the evaporator provided in the duct uniform.

The front view of the refrigerating and air-conditioning apparatus 100 which concerns on Embodiment 1 is shown. The top view of the machine room 1 of the refrigeration air conditioning apparatus 100 which concerns on Embodiment 1 is shown. The right view of the refrigerating and air-conditioning apparatus 100 which concerns on Embodiment 1 is shown. The left view of the refrigerating and air-conditioning apparatus 100 which concerns on Embodiment 1 is shown. The top view of the fan room 2 of the refrigeration air conditioning apparatus 100 which concerns on Embodiment 1 is shown. 2 shows a refrigeration cycle of the refrigeration air-conditioning apparatus 100 according to Embodiment 1. The perspective view of the duct 9 of the refrigeration air conditioner 100 which concerns on Embodiment 1 is shown. The front view of the duct 9 of the refrigeration air conditioning apparatus 200 which concerns on Embodiment 2 is shown. The perspective view of the duct 9 of the refrigeration air conditioning apparatus 300 which concerns on Embodiment 3 is shown. It is sectional drawing (D0-D0 cross section) of the deflection | deviation board 13a of the refrigeration air conditioning apparatus 300 which concerns on Embodiment 3. FIG. The perspective view of the duct 9 of the refrigeration air conditioning apparatus 400 which concerns on Embodiment 4 is shown. It is sectional drawing (D0-D0 cross section) of the deflection | deviation board 13b of the refrigerating and air-conditioning apparatus 400 which concerns on Embodiment 4. FIG. The perspective view of the duct 9 of the refrigerating and air-conditioning apparatus 500 which concerns on Embodiment 5 is shown. It is a front view of the deflection plate 13c of the refrigeration air conditioning apparatus 500 which concerns on Embodiment 5. FIG. The perspective view of the duct 9 of the refrigerating and air-conditioning apparatus 600 which concerns on Embodiment 6 is shown. It is sectional drawing (D0-D0 cross section) of the process part 14a of the refrigerating and air-conditioning apparatus 600 which concerns on Embodiment 6. FIG. The perspective view of the duct 9 of the refrigeration air conditioning apparatus 700 which concerns on Embodiment 7 is shown. It is sectional drawing (D0-D0 cross section) of the process part 14b of the refrigeration air conditioning apparatus 700 which concerns on Embodiment 7. FIG. In the refrigerating and air-conditioning apparatus according to Embodiments 1 to 3, the flow velocity distribution inside the duct 9 is shown. In the refrigerating and air-conditioning apparatus according to Embodiments 4 to 5, the flow velocity distribution inside the duct 9 is shown.

  Hereinafter, a refrigerating and air-conditioning apparatus according to an embodiment of the present invention will be described with reference to the drawings. In the following description, terms for indicating directions (for example, “right”, “left”, “front”, “rear”, etc.) are used as appropriate for easy understanding. Therefore, these terms are not terms that limit the positional relationship of the present invention.

Embodiment 1 FIG.
FIG. 1 is a front view of a refrigerating and air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
The refrigerating and air-conditioning apparatus 100 includes a housing 11 having a machine room 1 in the lower stage and a blower room 2 in the upper stage.
The machine room 1 has a substantially rectangular parallelepiped shape. Inside the machine room 1, there are a fan 7 for sucking air, a duct 9 for transporting the air sucked by the fan 7 to the air-conditioned space, an evaporator 10 arranged in the duct 9 through which low-temperature and low-pressure refrigerant flows, and refrigerant In order to circulate the refrigerant in the refrigeration cycle, components such as a compressor 19 that compresses and discharges the refrigerant are arranged. The duct 9 includes a suction duct 9a, a first duct 9b, and a second duct 9c.

  The blower chamber 2 is disposed on the machine chamber 1 and has a substantially rectangular parallelepiped shape. In the blower chamber 2, a condenser 31 through which high-temperature and high-pressure refrigerant flows and a blower 32 that blows air to the condenser 31 are arranged. The condenser 31 includes three condensers 31a, 31b, and 31c (details will be described later with reference to FIG. 5).

  The compressor 19 and the evaporator 10 in the machine chamber 1 and the condenser 31 in the blower chamber 2 are connected by a refrigerant pipe (not shown) to form a refrigeration cycle, and the refrigerant compressed by the compressor 19 circulates in the refrigeration cycle. doing.

  In FIG. 1, a fan 7 is disposed at the front right end of the machine room 1. A suction port for the fan 7 to suck in air is formed in the central portion of the fan 7, and a suction through which the air sucked by the fan 7 passes at a position on a side surface of the housing 11 facing the suction port of the fan 7. A mouth 3 is formed. The diameter of the fan 7 is R.

The fan 7 is formed with a blower port 7a, and air sucked in the horizontal direction from the suction port 3 is blown in the vertical direction from the blower port 7a.
The fan 7 is a turbo fan, a sirocco fan, or the like, and is a fan that blows out air sucked from the rotation axis direction in a direction perpendicular to the rotation axis.

  A first duct 9 b is connected to the air outlet 7 a of the fan 7. The vertical width of the air duct introduction portion of the first duct 9b is narrow, and the vertical width is widened from the windward side to the leeward side. The first duct 9b has a constant vertical width when it travels a certain distance from the air blowing port 7a toward the leeward direction, and an evaporator 10 is provided at a location where the vertical width is constant. Yes.

Further, an eliminator 12 for removing moisture contained in the air is provided downstream of the evaporator 10.
Although not shown, a pressure sensor that detects the pressure state inside the duct may be installed inside the first duct 9b.

A second duct 9c is provided on the leeward side of the first duct 9b. The second duct 9c has a substantially rectangular parallelepiped shape. The second duct 9c is connected to the first duct 9b, and air flows through the duct from the windward side to the leeward side.
The second duct 9c is wider than the first duct 9b in the vertical direction, and the lower surface of the second duct 9c is positioned higher than the lower surface of the first duct 9b.

The second duct 9c is connected to the first duct 9b. The second duct 9c has a supply port 16 for blowing out the air cooled by the evaporator 10 to the outside.
The supply port 16 is formed in the lower part of the second duct 9 c, and the bellows duct 20 is connected to the supply port 16. The supply port 16 is provided with a damper 17a. The damper 17a is a device that adjusts the amount of air blown from the second duct 9c to the supply port 16.
The cold air that has passed through the evaporator 10 passes through the second duct 9c and the bellows duct 20, and is supplied from the air outlet 21 to the target space to be air-conditioned.

An air opening 18 is formed in the upper part of the second duct 9c, and a damper 17b is provided in the air opening 18. Air in the second duct 9 c is blown out from the atmosphere opening 18 into the blower chamber 2.
The damper 17b is a device that adjusts the air volume when the air in the second duct 9c is released to the outside. Note that the damper 17b is closed during refrigeration and air conditioning, and when the pressure in the second duct 9c suddenly increases, such as when the refrigeration and air conditioning apparatus is started up, the damper 17b is opened and then gradually closed to open the second duct 9c. Adjust the pressure inside. The damper 17b may be opened and closed manually, or may be configured by a motor-driven damper, and the controller 15 automatically detects the opening of the damper by detecting the pressure in the first duct 9b and the second duct 9c with a sensor. You may control.

  Since the lower surface of the second duct 9c is arranged at a position higher than the lower surface of the first duct 9b, there is a space below the second duct 9c, and an operator enters the space to open and close the damper 17b. Etc. can be performed.

  The evaporator 10 is supplied with low-temperature and low-pressure refrigerant that has passed through an expansion valve 34 (shown in FIG. 6) that depressurizes the refrigerant. The air in the first duct 9b passing through the evaporator 10 is cooled by exchanging heat with the low-temperature and low-pressure refrigerant. That is, the evaporator 10 serves as a cooling means for cooling the air passing through the first duct 9b.

  The evaporator 10 is generally composed of a plurality of heat radiating fins such as aluminum having a high thermal conductivity and a refrigerant pipe penetrating through the heat radiating fins while meandering. The refrigerant flows through the refrigerant pipe, and the refrigerant and the air passing through the evaporator 10 exchange heat on the surface of the radiation fin. The plurality of heat radiation fins are arranged in parallel with the air flow direction.

  On the front side of the fan 7, a control unit 15 that is a general control panel for supplying power is disposed. A board (not shown) is arranged in the control unit 15, and a microcomputer, a resistor, a capacitor, a reactance, a transistor, and the like are mounted on the board, and are electrically connected by a signal line, a power supply line, etc. The electric circuit is formed. The control unit 15 converts AC power supplied from a commercial power source into AC power having an arbitrary frequency, and supplies the AC power to actuators such as the compressor 19 and the blower 32. The control unit 15 controls driving of the compressor 19, the blower 32, and the like.

  A substantially cylindrical compressor 19 is arranged inside the machine room 1 on the front side of the bellows duct 20 and on the left side of the control unit 15.

Here, the flow of the wind in the machine room 1 will be described. Outside air is sucked in by the fan 7 from the suction port 3 formed on the side surface of the housing 11, and blown out from the blower port 7 a formed in the upper part of the fan 7 to the first duct 9 b. The air blown upward from the blower opening 7a to the first duct 9b first collides with the upper part of the introduction portion of the first duct 9b.
The air that has flowed in from the blower opening 7a of the fan 7 and collided with the upper part of the introduction portion of the first duct 9b changes the traveling direction to the left where the evaporator 10 is located, and travels inside the first duct 9b. The air is made uniform from the blower port 7a to the evaporator 10. The air that has reached the evaporator 10 is cooled by exchanging heat with a low-temperature refrigerant flowing through the evaporator 10 while passing through the evaporator 10.

  Moisture is removed from the air cooled through the evaporator 10 while passing through the eliminator 12. The air that has passed through the eliminator 12 flows from the first duct 9b to the second duct 9c, and is supplied from the air outlet 21 to the cooling space through the bellows duct 20 connected to the second duct 9c.

In FIG. 1, seven blowers 32 are installed in two stages on the front face of the blower chamber 2, and the blower 32 blows air to seven blower outlets 33 formed on the front face of the blower chamber 2.
Further, a condenser 31 is provided along both side surfaces and the back surface.

FIG. 2 is a top view of machine room 1 of refrigerating and air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
As described above with reference to FIG. 1, the suction port 3 for sucking air is formed on the back side of the machine room 1 in FIG. 2.
The suction port 3 and the fan 7 are connected by a suction duct 9a, and the air sucked from the suction port 3 is blown from the fan 7 to the first duct 9b through the suction duct 9a.

  Inside the suction duct 9a are a filter 4 comprising an air filter for removing dust and dust in the air and a medium performance filter for preventing salt damage in the order from the windward to the leeward of the ventilation path, and suction air A silencer 5 for suppressing the suction sound and a heater 6 for heating the suction air when heating is necessary are installed.

  Note that the heater 6 is stopped when the refrigerating and air-conditioning apparatus 100 is in a cooling operation, that is, when the compressor 19 is driven and a low-temperature refrigerant flows into the evaporator 10. When the refrigerating and air-conditioning apparatus 100 performs a heating operation, the heater 6 is driven, the compressor 19 is stopped, and the refrigerant does not flow into the evaporator 10. When the refrigerating and air-conditioning apparatus 100 performs a heating operation, air heated by the heater 6 is blown from the air outlet 21 to the conditioned space through the fan 7, the first duct 9 b, the second duct 9 c, and the bellows duct 20.

A fan motor 8 for driving the fan 7 is provided on the front side of the fan 7, that is, on the opposite side of the suction duct 9 a with respect to the fan 7.
In addition, the control part 15 is provided in the front side of the fan motor 8, and the compressor 19 is arrange | positioned in the left side of the control part 15, and the front side of the 1st duct 9b and the 2nd duct 9c.

In FIG. 2, the shape of the first duct 9b viewed from the upper surface is a rectangular shape in which the interval width from the front side to the rear side is the same width along the leeward direction from the windward side.
Similarly, the shape of the 2nd duct 9c seen from the upper surface is a rectangular shape of the same width as the 1st duct 9b from the windward to the leeward direction.

Here, the flow of the wind in the machine room 1 will be described.
When air is sucked in from the suction port 3 formed in the fan 7 and blown out from the blower port 7a, it first collides with the upper part of the first duct 9b. The air that has collided with the upper portion of the first duct 9b changes the traveling direction to the left where the evaporator 10 is located, and travels inside the first duct 9b.

  The shape of the 1st duct 9b seen from the upper surface becomes a shape of the same width from the front to the back direction in the 1st duct 9b. However, the width in the up-down direction, which is a direction perpendicular to the leeward direction from the windward, has a shape in which the first duct 9b extends from the windward toward the leeward direction. The direction of travel is changed to the left direction where the air travels and the interior of the first duct 9b travels.

  The air reaching the evaporator 10 is cooled while passing through the upper part of the evaporator 10. Thereafter, the air flowing into the second duct 9c is supplied from the supply port 16 to the air-conditioning target space.

  On the front side of the fan 7 and the fan motor 8, a control unit 15, which is a general control panel that supplies power, is disposed.

  The compressor 19 is disposed between the front plate of the machine room 1 and the first duct 9b and the second duct 9c, and is disposed on the left side of the control unit 15 in FIG.

3 is a right side view of the refrigerating and air-conditioning apparatus 100 according to Embodiment 1. FIG.
As described above with reference to FIG. 1, the filter 4, the silencer 5, the heater 6, the fan 7, and the fan motor 8 are provided in the machine room 1 in order from the right side of the machine room 1 where the air inlet 3 for sucking air is formed. The control unit 15 is arranged. A first duct 9 b is connected to the upper portion of the fan 7.

  Inside the blower chamber 2, a plurality of blowers 32 are provided behind a plurality of blower outlets 33 formed in the front of the machine room 1. A condenser 31 a is arranged along the right side surface of the blower chamber 2.

4 is a left side view of the refrigerating and air-conditioning apparatus 100 according to Embodiment 1. FIG.
A damper 17a, a bellows duct 20, and an air outlet 21 are provided on the lower front side of the second duct 9c, and a space is formed on the front side of the bellows duct 20. This space is located below the lower front side of the second duct 9c.

By creating a space at this position, an operator can manually open and close the damper 17a or perform maintenance of the compressor 19 when an abnormality occurs. Alternatively, the compressor 19 may be disposed in this space.
An air opening 18 is formed in the upper part of the second duct 9c, and a damper 17b is provided in the air opening 18. Air in the second duct 9 c is blown out from the atmosphere opening 18 into the blower chamber 2.

  Inside the blower chamber 2, a plurality of blowers 32 are provided behind a plurality of blower outlets 33 formed in the front of the machine room 1. A condenser 31 b is arranged along the left side surface of the blower chamber 2.

FIG. 5 is a top view of the blower chamber 2 of the refrigerating and air-conditioning apparatus 100 according to Embodiment 1.
As described earlier with reference to FIG. 1, the blower chamber 2 is provided on the left end back side with a plurality of blowers 32, a plurality of blower outlets 33, three flat plate air-cooled condensers 31 a, 31 b, and 31 c surrounding them. The damper 17b and the air opening 18 are formed.

A condenser 31 a is disposed along the right side surface of the blower chamber 2, and a condenser 31 b is disposed along the left side surface of the blower chamber 2. Moreover, the condenser 31c is arrange | positioned at the back side of the air blower chamber 2 so that both the left and right ends may be surrounded by the condenser 31a and the condenser 31b. The condensers 31a, 31b, 31c are connected by refrigerant piping.
Inside the blower chamber 2, these three flat air-cooled condensers 31 a, 31 b, and 31 c are arranged so as to be perpendicular to the upper surface of the machine chamber 1.

A plurality of blower outlets 33 for blowing out hot air generated from the air-cooled condenser 31 are formed on the front side surface of the blower chamber 2. Behind that, a plurality of blowers 32 for blowing hot air from the air-cooled condenser 31 toward the blower outlet 33 are arranged.
The plurality of blowers 32 blow air from the inside of the blower chamber 2 to the outside through the blower outlet 33. That is, air is sucked into the blower chamber 2 from the right side, left side, and back of the blower chamber 32 by driving the blower 32. The sucked air is heated by exchanging heat in the air-cooled condensers 31a, 31b, 31c, and then blown out from the blower outlet 33.

The air opening 18 formed in the upper part of the second duct 9 c described in FIG. 2 is formed in the blower chamber 2. The damper 17b provided in the atmosphere opening 18 adjusts the amount of air blown from the second duct 9c inside the machine room 1 to the atmosphere opening 18.
When the air pressure inside the first duct 9b or the second duct 9c increases excessively, the air inside the duct 9 is released by opening the atmosphere opening 18 to release the air from the first duct 9b or the second duct 9c. The pressure can be released and reduced.
The air opening 18 is provided between the air-cooled condenser 31 b and the left side surface of the blower chamber 2. By providing the air-cooled condenser 31b on the windward side as described above, the air cooled through the evaporator 10 passes through the condenser 31b from the atmosphere opening port 18.

FIG. 6 shows a refrigeration cycle of the refrigeration air conditioner 100.
In the refrigeration cycle, the refrigerant circulates in the order of the compressor 19 → the condenser 31 → the expansion valve 34 → the evaporator 10 → the compressor 19 →. The compressor 19, the condenser 31, the expansion valve 34, and the evaporator 10 are connected by refrigerant piping.

  First, the refrigerant is compressed by the compressor 19 and discharged to the condenser 31 as a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant is cooled by exchanging heat with air in the condenser 31 to become a low-temperature and high-pressure refrigerant. The low-temperature high-pressure refrigerant that has exited the condenser 31 is decompressed by the expansion valve 34 to become a low-temperature low-pressure refrigerant. The low-temperature and low-pressure refrigerant that has passed through the expansion valve 34 exchanges heat with the air conveyed to the air-conditioned space by the evaporator 10 and becomes high-temperature and low-pressure refrigerant. The high-temperature and low-pressure refrigerant exiting the evaporator 10 is compressed again by the compressor 19 and discharged as a high-temperature and high-pressure refrigerant.

In the refrigerating and air-conditioning apparatus 100 of the first embodiment, the compressor 19, the evaporator 10, and the fan 7 that sends air to the evaporator 10 are provided in the machine room 1, and the blower that blows air to the condenser 31 and the condenser 31. 32 is provided in the blower chamber 2.
The expansion valve 34 may be provided on either the machine room 1 or the blower room 2 side.

FIG. 7 is a perspective view of the first duct 9b and the second duct 9c of the refrigerating and air-conditioning apparatus 100 according to Embodiment 1. In FIG. 7, the eliminator 12 and the like are omitted.
In the first embodiment, a refrigerating and air-conditioning apparatus 100 having a first duct 9b will be described with reference to FIG.

  First, in FIG. 7, the direction from the windward to the leeward direction in the first duct 9b is defined as the B direction (horizontal direction), and the direction perpendicular to the windward from the leeward direction is defined as the H direction (vertical direction).

Further, in the first duct 9b, the vertical width of the first duct 9b at the innermost position (hereinafter referred to as A3 position) having the narrowest vertical width is defined as Ha. Similarly, in the first duct 9b, the vertical width of the first duct 9b at the front position where the vertical width is widest (hereinafter referred to as the position A1) is defined as Hb.
Hereinafter, the same definition will be applied to the second to seventh embodiments.

  Although not shown in FIG. 7, a fan 7 having a diameter R in the B direction is arranged at the front right end of the machine room 1 below the introduction portion of the first duct 9 b.

As shown in FIG. 7, the vertical width Ha of the air duct introduction portion of the first duct 9b is narrow, and the vertical width Hb is widened from the windward to the leeward. The first duct 9b has a constant vertical width of Hb as it travels a certain distance from the air blowing port 7a toward the leeward direction, and the evaporator 10 is located at a location where the vertical width is constant. Is provided.
In addition, the part shown by the star in FIG. 7 is the site | part 7b where the air introduce | transduced from the inlet 3 of the fan 7 goes straight and collides with the 1st duct 9b upper part. The air that has collided with the colliding portion 7b flows in the leeward direction while changing the traveling direction to the B direction, flows while spreading in the H direction while traveling the length La, and reaches the evaporator 10.

Now, let the total length of the duct which combined the 1st duct 9b and the 2nd duct 9c be length L, and let the distance from the ventilation port 7a of the fan 7 to the evaporator 10 be length La.
In the present invention, the air velocity distribution of the air blown from the fan 7 and acting on the evaporator 10 is obtained by taking a space corresponding to this length La along the windward to leeward direction from the air blowing port 7a to the evaporator 10. It can be made uniform.
The length La is preferably at least ¼ or more of the length L (the total length of the duct). Alternatively, the length La is preferably larger than the diameter R of the fan 7. That is, the distance from the portion 7b or the air blowing port 7a where the air introduced by the fan 7 collides in the first duct 9b to the windward side of the evaporator 10 is sufficiently larger than the diameter R of the fan 7 in the B direction. It is a guideline.

Since the evaporator 10 has a height in the vertical direction inside the first duct 9b, the length La, which is the distance between two points from the air blowing port 7a to the windward side of the evaporator 10, is the vertical direction of the evaporator 10. And the air outlet 7a are different depending on which two points are selected.
For example, the length La varies (Lmin to Lmax) depending on how to take a point in the vertical direction on the windward plane of the evaporator 10 and how to make a point in the horizontal direction at the air outlet 7a. For this reason, even if the length La is set to Lmax, it is better if Lmax> R.

  In the present embodiment, since the duct space can be provided in the B direction (windward to leeward direction), the distance from the blower opening 7a of the fan 7 to the evaporator 10 can be increased, and the first duct 9b Since the air traveling the length La after colliding with the upper portion of the introduction portion is dispersed in the vertical direction, the air velocity distribution acting on the evaporator 10 can be made uniform.

  Moreover, since the shape of the 1st duct 9b can be made into a horizontally long shape by taking sufficient distance for length La from this ventilation port 7a to the evaporator 10, the evaporator 10 is made into B direction inside a duct. It can be placed in any position.

Further, by taking a sufficient distance for the length La ( La> diameter R of the fan 7 ) from the air blowing port 7a to the evaporator 10, the shape of the first duct 9b can be made into a horizontally long shape. Since a space for installing the fan 7 can be secured below 7a, the refrigerating and air-conditioning apparatus 100 can be downsized in the vertical direction. That is, since Ha <Hb, a space can be secured under Ha, and the fan 7 can be disposed in the space, so that the refrigeration air conditioner 100 can be downsized. In particular, it is desirable that the horizontal length of the introduction portion at which the height Ha of the first duct 9 b is larger than the diameter R of the fan 7.

  As described above, the refrigerating and air-conditioning apparatus 100 according to Embodiment 1 only takes the space corresponding to this length La from the air blowing port 7a to the evaporator 10 to make it collide with the upper part of the introduction portion of the first duct 9b. The air velocity distribution of air blown from the fan 7 and acting on the evaporator 10 can be made uniform.

  In the first embodiment, the shape of the first duct 9b extending in the vertical direction from the windward to the leeward has been described. However, the shape may be extended in the horizontal direction from the windward to the leeward.

Embodiment 2. FIG.
In the first embodiment, the refrigerating and air-conditioning apparatus 100 having the first duct 9b in which the vertical width of the first duct 9b satisfies Ha <Hb has been described. In the second embodiment, the vertical direction of the first duct 9b is described. A refrigerating and air-conditioning apparatus 200 having a first duct 9b configured to have a width of Ha = Hb will be described with reference to FIG.

  Compared with the refrigerating and air-conditioning apparatus 100 according to the first embodiment, in the second embodiment, the lower right end portion of the first duct 9b does not have a shape in which the vertical width increases from the windward to the leeward, The width in the direction is equal to Ha = Hb.

  As shown in FIG. 8, the vertical width of the air duct introduction portion of the first duct 9b is constant, and the same width continues from the windward side to the leeward side. It is the same that the evaporator 10 is provided in the first duct 9b where the vertical width is constant.

  In the present invention, the air velocity distribution of the air blown from the fan 7 and acting on the evaporator 10 is obtained by taking a space corresponding to this length La along the windward to leeward direction from the air blowing port 7a to the evaporator 10. It can be made uniform.

The length La is preferably at least ¼ or more of the length L (the total length of the duct).
Alternatively, the length La is preferably larger than the diameter R of the fan 7. That is, the distance from the portion 7b (the air blowing port 7a) where the air introduced by the fan 7 collides in the first duct 9b to the windward side of the evaporator 10 is sufficiently larger than the diameter R of the fan 7 in the B direction. Large is a guide.

  In the second embodiment, since the duct space can be provided in the B direction (windward to leeward direction), the distance from the air blowing port 7a of the fan 7 to the evaporator 10 can be increased, and the air is blown from the fan 7. It is possible to provide a refrigerating and air-conditioning apparatus that can make the air velocity distribution uniform by simply colliding the generated air with the upper portion of the introduction portion of the first duct 9b.

  Moreover, since the shape of the 1st duct 9b can be made into a horizontally long shape by taking sufficient distance for length La from this ventilation port 7a to the evaporator 10, the evaporator 10 is made into B direction inside a duct. It can be placed in any position. In addition, by setting Ha = Hb, the first duct 9b can be formed into a substantially rectangular parallelepiped shape, so that the design and manufacture of the first duct 9b are facilitated.

  As described above, the refrigerating and air-conditioning apparatus 200 according to the second embodiment only takes the space corresponding to the length La from the air blowing port 7a to the evaporator 10 to collide with the upper part of the introduction portion of the first duct 9b. The air velocity distribution of air blown from the fan 7 and acting on the evaporator 10 can be made uniform.

Embodiment 3 FIG.
In the third embodiment, in the refrigerating and air-conditioning apparatus 100 having the first duct 9b in which the vertical width of the first duct 9b described in the first embodiment satisfies Ha <Hb, a cross section is provided inside the first duct 9b. A refrigerating and air-conditioning apparatus 300 additionally provided with an I-shaped deflecting plate 13a (flow velocity equalizing means) will be described with reference to FIGS.
In addition, the same number is attached | subjected to the same component in Embodiment 1, and description is abbreviate | omitted.

  The first embodiment described with reference to FIG. 7 has a problem that the flow velocity at the upper end and the left and right ends inside the duct 9 is slightly higher than the flow velocity at the center in the duct 9. As measures against this, a refrigerating and air-conditioning apparatus 300 having a configuration in which a deflection plate is provided in the first duct 9b will be described.

  As shown in FIG. 9, the vertical width Ha of the air duct introduction portion of the first duct 9b is narrow, and the vertical width increases from the windward side to the leeward side. The first duct 9b has a constant vertical width Hb when it travels a certain distance from the air blowing port 7a toward the leeward direction, and the evaporator 10 is provided at a location where the vertical width Hb is constant. It has been.

  The deflection plate 13a has an outermost peripheral portion in contact with the inside of the first duct 9b at the upper end and the left and right ends inside the first duct 9b, and has a gate shape. The deflecting plate 13a may be provided at the lower end of the first duct 9b. However, in the third embodiment, the flow velocity at the lower end of the first duct 9b is not large compared to the upper end and the left and right ends. FIG. 9 shows a configuration in which the first duct 9b is not provided.

FIG. 10 shows the deflection plate 13a in FIG. 9 as viewed from the direction of the cross section D0-D0.
The deflection plate 13a is a convex portion provided on the inner surface inside the first duct 9b along the direction perpendicular to the leeward direction from the windward side.
The shape of the deflecting plate 13a has a convex structure in which the deflecting plate 13a protrudes in an I shape from the outer peripheral portion toward the inside of the first duct 9b. The deflection plate 13a may be integrally formed with the first duct 9b or may be provided separately. In general, a material having moisture resistance and corrosion resistance such as plastic is used, but a metal member or the like may be arbitrarily changed.

  The third embodiment described here can improve the problem that the I-shaped deflecting plate 13a is arranged inside the first duct 9b and the flow velocity at the upper end and the left and right ends inside the duct 9 is slightly high, and evaporation The flow velocity distribution acting on the vessel 10 can be made uniform (described later in FIG. 19).

Next, in the third embodiment, the wind speed distribution when the position where the deflector plate 13a is arranged from the windward along the leeward direction is changed will be described.
As shown in FIG. 9, the arrangement of the deflecting plate 13 a can be changed from the position close to the evaporator 10 to the front (A1), the center (A2), and the back (A3).

  First, the case where the deflection plate 13a is arranged in front will be described. At this time, the gate-shaped deflecting plate 13a is disposed at a position indicated by A1 inside the first duct 9b.

  In the third embodiment, when the deflector plate 13a is installed in front (A1) inside the first duct 9b, as shown later in FIG. 19 (b), the air volume is 101% and the wind speed distribution is ± 6%. Although the air volume is larger and better than that described in the first embodiment, the wind speed distribution is generally poor.

  Next, the case where the deflection plate 13a is arranged at the center will be described. At this time, the deflection plate 13a, which is shorter in the H direction than when it is disposed in front (A1), is disposed at a position indicated by A2 inside the first duct 9b.

  When the deflecting plate 13a is installed in the center (A2) inside the first duct 9b, as shown later in FIG. 19 (d), the air volume varies 100% and the wind speed distribution ± 0.2%. The best results are obtained in both the balance of the air volume and the wind speed distribution than described in 1.

  Finally, the case where the deflection plate 13a is arranged at the back (A3) will be described. At this time, the deflecting plate 13a, which is shorter in the H direction than when it is arranged at the center (A2), is arranged at a position indicated by A3 in the first duct 9b.

  When the deflection plate 13a is installed in the back (A3) inside the first duct 9b, as shown later in FIG. 19 (c), the air volume is 99% and the wind speed distribution is ± 0.3%. Although the wind speed distribution is improved compared to that described in 1, the air volume is reduced.

  Note that the deflecting plate 13a may be disposed at a free position other than the above three as long as it is inside the first duct 9b. Further, the deflecting plate 13a may be movable along the leeward direction from the windward by a motor or the like instead of being fixed at a fixed position inside the first duct 9b.

  In the third embodiment described here, an I-shaped deflecting plate 13a is arranged at a free position inside the first duct 9b inside the first duct 9b, and the flow velocity distribution acting on the evaporator 10 is made uniform. The problem that the flow velocity at the upper end of the duct 9 and the left and right ends is slightly high can be improved. (It will be described later with reference to FIG. 19)

  As described above, the refrigerating and air-conditioning apparatus 300 according to Embodiment 3 can make the flow velocity distribution acting on the evaporator 10 uniform by disposing the deflection plate 13a having an I-shaped cross section on the inner periphery of the first duct 9b. effective.

Embodiment 4 FIG.
In the fourth embodiment, in the refrigerating and air-conditioning apparatus 100 having the first duct 9b in which the vertical width of the first duct 9b described in the first embodiment satisfies Ha <Hb, the V-shape is formed inside the first duct 9b. A refrigerating and air-conditioning apparatus 400 having a configuration in which a deflecting plate 13b having a shape is additionally arranged will be described with reference to FIGS.
In the fourth embodiment, the deflection plate 13b corresponds to a flow velocity uniformizing unit.
In addition, the same number is attached | subjected to the same component as Embodiment 1, and description is abbreviate | omitted.

  The deflection plate 13b is in contact with the inside of the first duct 9b at the uppermost end and the left and right ends inside the first duct 9b, and has a gate shape as shown in FIG.

12 is a cross-sectional view taken along the line D1-D1 of the deflection plate 13b in FIG.
The deflection plate 13b is a convex portion provided on the inner surface inside the first duct 9b along the direction perpendicular to the leeward direction from the windward side.
The shape of the deflecting plate 13b has a triangular prism structure in which the deflecting plate 13b protrudes in a V shape from the outer peripheral portion toward the inside of the first duct 9b. That is, the deflection plate 13b has a shape having an inclined surface from the windward side to the leeward side.

  The deflecting plate 13b (V-shaped) employed in the fourth embodiment rectifies more smoothly than the deflecting plate 13a (I-shaped) described in the third embodiment, and the air is in the central portion inside the first duct 9b. It becomes easier to concentrate and flow. (It will be described later with reference to FIG. 19)

  Since the arrangement of the deflecting plate 13b can be changed in order from the position close to the evaporator 10 from the leeward side to the upstream side to the near side (A1), the center (A2), and the back side (A3), the description is omitted.

  Moreover, in this Embodiment 4 shown in FIG. 11, since it is the same about the wind speed distribution at the time of changing the position which arrange | positions the deflection plate 13b in the different position inside the 1st duct 9b, description is abbreviate | omitted.

  As described above, the refrigerating and air-conditioning apparatus 400 according to the fourth embodiment acts on the evaporator 10 by disposing the deflecting plate 13b having an inclined surface from the windward to the leeward in the first duct 9b. There is an effect that the flow velocity distribution can be made uniform.

Embodiment 5. FIG.
In the fifth embodiment, in the refrigerating and air-conditioning apparatus 100 having the first duct 9b in which the vertical width of the first duct 9b described in the first embodiment satisfies Ha <Hb, a flat plate shape is formed inside the first duct 9b. A refrigerating and air-conditioning apparatus 500 configured to additionally arrange the punching plate 13c will be described with reference to FIGS.
In the fifth embodiment, the punching plate 13c corresponds to the flow velocity equalizing means.
The same parts in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The outermost peripheral portion of the punching plate 13c is in contact with the inside of the first duct 9b at the upper and lower ends and the left and right ends inside the first duct 9b, and has a flat plate shape as shown in FIG.

FIG. 14 shows the punching plate 13c in FIG. 13 as seen from the front (downward-upward direction).
The deflection plate 13c is a flat plate provided on the inner surface inside the first duct 9b in parallel with the direction perpendicular to the leeward direction from the windward side.
The shape of the punching plate 13c is, for example, a shape having a plurality of openings by processing a plastic flat plate. In general, a material having moisture resistance and corrosion resistance such as plastic is used, but a metal member or the like may be arbitrarily changed.

  Further, in the above description, a plurality of punching plates 13c may be used or may be arranged in order to make the flow velocity distribution acting on the evaporator 10 uniform.

  In the fifth embodiment, since the entire air flow is blocked from the windward to the leeward direction, the air path resistance inside the first duct 9b is increased and the air volume is reduced as compared with the first and second embodiments. There is. However, the flow velocity distribution acting on the evaporator 10 inside the first duct 9b is greatly improved, and the best result in the embodiments so far can be obtained in terms of uniforming the wind velocity distribution. It is effective (shown in FIG. 20).

  Since the arrangement of the punching plate 13c can be changed from the position close to the evaporator 10 to the front (A1), the center (A2), and the back (A3) in the same manner, the description is omitted.

  As described above, the refrigerating and air-conditioning apparatus 500 of the fifth embodiment has an effect that the punching plate 13c having a plurality of openings is arranged inside the first duct 9b, and the flow velocity distribution acting on the evaporator 10 can be made uniform. is there.

Embodiment 6 FIG.
In the sixth embodiment, in the refrigerating and air-conditioning apparatus 100 according to the first embodiment, the first duct 9b near the portion 7b where the air introduced from the suction port 3 inside the first duct 9b collides with the upper portion of the first duct 9b. A refrigerating and air-conditioning apparatus 600 having a configuration in which pressure reducing means is applied to the upper right corner will be described with reference to FIGS. 15 and 16.
In the sixth embodiment, the processed portion 14a having a curved surface corresponds to a pressure reducing unit.

  In FIG. 15, the processing part 14a which has a curved surface is formed in the upper right corner part of the 1st duct 9b near the site | part 7b which the air sent from the fan 7 goes straight and collides in the 1st duct 9b.

16 is a D2-D2 cross section of the processed portion 14a in FIG. The processing portion 14 has an arc shape having a curved surface 14a having a radius r toward the outside of the first duct 9b.
The processing portion 14a smoothly deflects the wind direction and the wind speed while reducing the pressure acting on the upper right corner of the first duct 9b near the portion 7b that collides with the upper portion of the first duct 9b. The flow velocity distribution acting on the evaporator 10 can be made uniform.

  Since the processing portion 14a can reduce the pressure acting on the upper right corner of the first duct 9b in the vicinity of the portion 7b where the air blown from the air blowing port 7a of the fan 7 collides, the upper right of the first duct 9b. Since it is less necessary to increase the strength of the corners, the processing of the first duct 9b is facilitated. Further, the inside of the duct 9 can be maintained at an appropriate pressure as compared with the first embodiment.

  As described above, the refrigerating and air-conditioning apparatus 600 of the sixth embodiment has a curved surface at the upper right corner of the first duct 9b near the portion 7b where the air introduced from the suction port 3 collides inside the first duct 9b. There is an effect that the processing portion 14a having the above arrangement is arranged, and the flow velocity distribution acting on the evaporator 10 can be made uniform while suppressing the attenuation of the wind speed in the first duct 9b.

Embodiment 7 FIG.
In the seventh embodiment, in the refrigerating and air-conditioning apparatus 100 according to the first embodiment, the first duct 9b near the portion 7b where the air introduced from the suction port 3 inside the first duct 9b collides with the upper portion of the first duct 9b. A refrigerating and air-conditioning apparatus 700 having a structure in which pressure reducing means is applied to the upper right corner will be described with reference to FIGS. 17 and 18.
In the seventh embodiment, the processed portion 14b having a chamfer corresponds to the pressure reducing means.

  In FIG. 17, the processing part 14b which has a chamfering is formed in the upper right corner of the first duct 9b near the portion 7b where the air blown from the fan 7 goes straight and collides in the first duct 9b.

18 is a D3-D3 cross section of the processed portion 14b in FIG.
The processing portion 14b is rounded at the upper right corner of the first duct 9b.
The processing portion 14b can reduce the pressure acting on the upper right corner of the first duct 9b near the portion 7b that collides with the upper portion of the first duct 9b. For this reason, since the wind direction and the wind speed are smoothly deflected, the flow velocity distribution acting on the evaporator 10 can be made uniform while suppressing the attenuation of the wind speed. Further, there is an advantage that the shape processing is relatively easy as compared with the processed portion 14a having the curved surface described in the sixth embodiment.

  Since the process part 14b can reduce the pressure which acts on the upper right corner part of the 1st duct 9b of the vicinity of the site | part 7b where the air blown out from the ventilation opening 7a of the fan 7 collides, the upper right of the 1st duct 9b Since it is less necessary to increase the strength of the corners, the processing of the first duct 9b is facilitated. Further, the inside of the duct 9 can be maintained at an appropriate pressure as compared with the first embodiment.

  As described above, the refrigerating and air-conditioning apparatus 700 according to the seventh embodiment has a chamfered corner at the upper right corner of the first duct 9b near the portion 7b where the air introduced from the suction port 3 collides inside the first duct 9b. There is an effect that the processing portion 14b having the above can be arranged, and the flow velocity distribution acting on the evaporator 10 can be made uniform while suppressing the attenuation of the wind speed in the first duct 9b.

  The processing portions 14a and 14b described in the sixth to seventh embodiments can be additionally applied to the deflection plate 13a, the deflection plate 13b, and the punching plate 13c described in the third to fifth embodiments.

  FIG. 19 shows the flow velocity distribution on the windward side of the internal evaporator 10 of the first duct 9b with contour lines in the refrigeration air conditioners according to Embodiments 1 to 3 of the present invention. First, Embodiments 1 to 5 will be described for comparison.

FIG. 19 shows the wind speed distribution in the internal evaporator 10 of the first duct 9b shown in the first to third embodiments.
When nothing is installed inside the first duct 9b as in the first embodiment, the wind speed in the vicinity of the upper end and the left and right ends in the first duct 9b is as shown in FIG. 19 (a). Since it is larger than the wind speed at the center, the wind speed distribution is very poor overall.

  In the third embodiment, when the deflection plate 13a is installed in front (A1) inside the first duct 9b, the air volume varies by 101% and the wind speed distribution ± 6% as shown in FIG. 19B. The amount of air is much better than in the case of FIG. 19 (a), but the wind speed distribution is generally poor because the wind speed at the center is generally higher than the wind speed at the top, bottom, left and right ends.

  In the third embodiment, when the deflection plate 13a is installed in the back (A3) inside the first duct 9b, as shown in FIG. 19C, the air volume is 99% and the wind speed distribution is ± 0.3%. Become. Although the wind speed distribution is improved as compared with the case of FIGS. 19A and 19B, the air volume is reduced.

  Finally, in the third embodiment, when the deflection plate 13a is installed in the center (A2) in the first duct 9b, as shown in FIG. 19 (d), the air volume is 100% and the wind speed distribution is ± 0.2%. It becomes a variation. Compared with the case of FIGS. 19 (a) to 19 (c), the best results are obtained for both the balance of the air volume and the wind speed distribution.

  FIG. 20 shows the flow velocity distribution on the windward side of the internal evaporator 10 of the first duct 9b with contour lines in the refrigeration air conditioners according to Embodiments 4 to 5 of the present invention. Next, Embodiments 4 to 5 will be described for comparison.

FIG. 20 shows the wind speed distribution on the windward side of the internal evaporator 10 of the first duct 9b shown in the fourth to fifth embodiments.
When nothing is installed inside the first duct 9b as in the first embodiment, as shown in FIG. 20A (same as FIG. 19A), the wind speed distribution is deteriorated.

  FIG. 20B shows a case where the deflecting plate 13b (V-shaped) is installed inside the first duct 9b in the fourth embodiment. Compared with FIG. 20A, the wind speed distribution on the windward side of the evaporator 10 is improved at the upper end and the left and right ends inside the first duct 9b. In addition, air is more likely to flow through the central portion than when the deflection plate 13a is provided (FIG. 19D), but the wind speed distribution can be made uniform while suppressing a decrease in the air volume.

  Finally, FIG. 20 (c) shows a case where the punching plate 13c is installed inside the first duct 9b in the fifth embodiment. Compared with the cases of FIGS. 20A and 20B, the overall air volume is reduced, but the wind speed distribution can be made uniform.

In the above-described embodiment,
The method for controlling the flow velocity distribution inside the first duct 9b provided with a deflection plate, a punching plate, and the like for uniformizing the flow velocity distribution acting on the evaporator 10 inside the duct has been described.
The present invention is not limited to this, and can be applied to different applications as long as the shape inside the duct, the shape of the deflection plate, the punching plate, and the installation location are changed.

DESCRIPTION OF SYMBOLS 1 Machine room, 2 Fan room, 3 Suction port, 4 Filter, 5 Silencer, 6 Heater, 7 Fan, 8 Fan motor, 9 Duct, 9a Suction duct, 9b 1st duct, 9c 2nd duct, 10 Evaporator, DESCRIPTION OF SYMBOLS 11 Housing | casing, 12 Eliminator, 13a, 13b Deflection plate, 13c Punching plate, 14a Processing part which has a curved surface, 14b Processing part which has chamfering, 15 Control part, 16 Supply port, 17a, 17b Damper, 18 Atmospheric release port,
19 compressor, 20 bellows duct, 21 outlet, 31 condenser, 32 blower,
33 Blower outlet, 34 Expansion valve

Claims (8)

A housing having a suction port through which air is sucked;
A blower port is formed, and a fan that blows the air from the suction port to the blower port;
A duct through which the air flows from the air outlet;
An evaporator disposed in the duct at a distance larger than the diameter of the fan from the air blowing port to the leeward side,
The air blown into the duct from the air outlet passes through the evaporator after colliding with a portion facing the air outlet in the duct ,
The distance between the said part and the said evaporator is a refrigerating air conditioner characterized by being longer than the diameter of the said fan .   The refrigerating and air-conditioning apparatus according to claim 1, wherein the duct has a shape that increases in width from the windward to the leeward direction. On the windward side of the evaporator in the duct,
Provided with a flow velocity uniformizing means for uniformizing a flow velocity distribution acting on the evaporator;
The refrigerating and air-conditioning apparatus according to claim 1.   The refrigerating and air-conditioning apparatus according to claim 3, wherein the flow velocity equalizing means is a deflecting plate provided on an inner surface inside the duct along a direction perpendicular to the leeward direction from the windward side.   The refrigerating and air-conditioning apparatus according to claim 4, wherein the deflecting plate has an inclined surface from the windward side to the leeward side. The said flow velocity equalization means is a board which has a some opening and was provided in the inner surface inside the said duct in parallel with the direction perpendicular | vertical to the leeward direction from the windward. Refrigeration air conditioner. The refrigerating and air-conditioning apparatus according to any one of claims 1 to 6, wherein an end portion of the duct close to a portion where the air blown from the fan collides is curved. The refrigerating and air-conditioning apparatus according to any one of claims 1 to 6, wherein the duct has a chamfered end portion close to a portion where the air blown from the fan collides.

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