WO2018062054A1

WO2018062054A1 - Refrigeration cycle device

Info

Publication number: WO2018062054A1
Application number: PCT/JP2017/034381
Authority: WO
Inventors: 馨松下; 裕昭渡邉
Original assignee: 東芝キヤリア株式会社
Priority date: 2016-09-27
Filing date: 2017-09-22
Publication date: 2018-04-05
Also published as: JPWO2018062054A1

Abstract

This refrigeration cycle device is provided with: a water heat exchanger which is accommodated in a machine chamber of a case and performs heat exchange between water flowing through a water flow passage and a refrigerant flowing through a refrigerant flow passage; and a volute pump which is accommodated in the machine chamber and supplies water to the water flow passage of the water heat exchanger. The volute pump includes a casing having an inlet port and a discharge port which are open at right angles to each other, and a driving power part for rotating an impeller in the casing, and is installed on the bottom of the machine chamber such that the rotating axis line of the driving power part is horizontal, thereby ensuring that the discharge port is upwardly open in the machine chamber. The water heat exchanger has water inlet ports lined up on an upstream end of the water flow passage and positioned higher than the discharge port of the volute pump, and the discharge port of the volute pump and the water inlet ports of the water heat exchanger are connected by water piping.

Description

Refrigeration cycle equipment

Embodiment of this invention is related with the refrigerating-cycle apparatus provided with the spiral pump which supplies water to a water heat exchanger.

An air-cooled heat pump chilling unit that generates cold water or hot water includes a housing having a machine room. The machine room has an elongated shape extending in the depth direction of the chilling unit, and various refrigeration cycle components including a water heat exchanger are accommodated in the machine room.

The water heat exchanger is connected to a utilization device such as an air conditioner through a water circuit having a spiral pump. The spiral pump is an element that supplies water returning from the utilization device side to the water flow path of the water heat exchanger, and is disposed at one end portion along the longitudinal direction of the machine room.

The spiral pump is provided with a casing in which a suction port and a discharge port are opened, and a motor that rotates an impeller in the casing. Generally, the centrifugal pump housed in the chilling unit housing is fixed to the bottom of the machine room with the motor rotation axis placed vertically, and between the lower end of the motor and the bottom of the machine room. The casing is located on the top.

JP 2014-178113 A Japanese Unexamined Patent Publication No. 2016-90083

In the conventional chilling unit, in order to enhance the heat exchange performance of the water heat exchanger, a water inlet connected to the water flow path is generally opened at the upper end of the water heat exchanger. On the other hand, the centrifugal pump is arranged in the machine room with the motor rotation axis placed vertically, so that the discharge port of the casing is located near the bottom of the machine room far from the water inlet of the water heat exchanger. Opened sideways.

As a result, the water pipe connecting the discharge port and the water inlet needs to be pulled out sideways from the discharge port and then set up toward the top of the machine room through the side of the motor. Therefore, the route for routing the water pipe becomes complicated and the length of the pipe cannot be denied.

In addition, it is necessary to secure a dedicated space to set up the water piping beside the motor, which is one factor that leads to an increase in the size of the machine room.

An object of the present invention is to obtain a refrigeration cycle apparatus in which water pipes connecting between a centrifugal pump and a water heat exchanger can be arranged in a compact manner, and the water piping route can be simplified.

According to the embodiment, the refrigeration cycle apparatus includes a housing having a machine room and a water heat exchanger that is accommodated in the machine room and performs heat exchange between water flowing through the water flow path and refrigerant flowing through the refrigerant flow path. And a centrifugal pump that is housed in the machine room and supplies water to the water flow path of the water heat exchanger.
The spiral pump includes a casing having a suction port and a discharge port opened in directions orthogonal to each other, and a power unit that rotates an impeller in the casing, and the discharge port opens upward in the machine room As described above, the centrifugal pump is installed on the bottom of the machine room in a posture in which the rotation axis of the power unit is placed horizontally. The water heat exchanger has a water inlet connected to an upstream end of the water flow path at a position higher than the discharge port of the spiral pump, and the discharge port of the spiral pump and the water inlet of the water heat exchanger Is connected by a water pipe.

FIG. 1 is a perspective view of an air-cooled heat pump chilling unit according to an embodiment. FIG. 2 is a side view of the air-cooled heat pump chilling unit according to the embodiment. FIG. 3 is a perspective view showing the positional relationship between the machine room containing the first refrigeration cycle unit, the second refrigeration cycle unit, the water circuit and the electrical unit and the drain pan. FIG. 4 is a plan view showing the positional relationship between the first refrigeration cycle unit, the second refrigeration cycle unit, the water circuit, and the electrical unit housed in the machine room. FIG. 5 is a circuit diagram showing a refrigeration cycle of the air-cooled heat pump chilling unit according to the embodiment. FIG. 6 is an exploded perspective view showing an air heat exchange unit used in the air-cooled heat pump chilling unit according to the embodiment. FIG. 7 is a rear view of the air-cooled heat pump chilling unit as seen from the direction of arrow F7 in FIG. FIG. 8A is a plan view showing a spiral pump used in the air-cooled heat pump chilling unit and a water piping routing path according to the embodiment. FIG. 8B is an arrow view seen from the direction of the arrow F8 in FIG. 8A. FIG. 9A is a plan view showing another spiral pump and water pipe routing route selectively used in the air-cooled heat pump chilling unit according to the embodiment. FIG. 9B is an arrow view seen from the direction of arrow F9 in FIG. 9A. FIG. 10A is a plan view showing still another spiral pump and water pipe routing route selectively used in the air-cooled heat pump chilling unit according to the embodiment. FIG. 10B is an arrow view seen from the direction of the arrow F10 in FIG. 10A.

Hereinafter, embodiments will be described with reference to the drawings.

FIG. 1 is a perspective view of an air-cooled heat pump chilling unit 1 that generates, for example, cold water or hot water, and FIG. 2 is a side view of the air-cooled heat pump chilling unit 1.

The air-cooled heat pump chilling unit 1 is an example of a refrigeration cycle apparatus that can be operated in a cooling mode and a heating mode, for example, and can be rephrased as an air-cooled heat pump heat source machine. In the following description, the air-cooled heat pump chilling unit 1 is simply referred to as a chilling unit 1.

As shown in FIGS. 1 to 4, the chilling unit 1 includes a housing 2, a first refrigeration cycle unit 3, a second refrigeration cycle unit 4, a water circuit 5, and an electrical unit 6 as main elements. . Here, FIGS. 1 to 3 show a state in which the panels covering the front, back, right side, and left side of the housing 2 are removed.

The housing 2 is installed on a horizontal installation surface G such as the roof of a building. The casing 2 is formed in an elongated hollow box shape whose depth dimension is much larger than the width dimension.

As shown in FIGS. 2 to 4, the housing 2 includes a main frame 7. The main frame 7 includes a lower frame 8, an upper frame 9 and a plurality of vertical bars 10. The lower frame 8 and the upper frame 9 are elongated rectangular shapes extending in the depth direction of the housing 2. The length L1 of the lower frame 8 along the depth direction of the housing 2 is shorter than the length L2 of the upper frame 9 along the depth direction of the housing 2. Further, the length L3 of the upper frame 9 along the width direction of the housing 2 is shorter than the length L4 of the lower frame 8 along the width direction of the housing 2.

The vertical beam 10 is an element that connects the lower frame 8 and the upper frame 9, and is arranged at intervals in the depth direction of the housing 2. The vertical rails 10 facing the width direction of the housing 2 are inclined so as to approach each other as they proceed from the lower frame 8 to the upper frame 9.

For this reason, as shown in FIGS. 1 and 3, when the housing 2 is viewed from the front direction F and the back direction R, the main frame 7 moves from the lower frame 8 toward the upper frame 9. It is formed in a tapered shape such that the dimension along the width direction is gradually narrowed.

The bottom plate 13 is fixed on the lower frame 8. The bottom plate 13 defines a machine room 14 inside the housing 2 in cooperation with a plurality of panels (not shown) that cover the right side, left side, front, and back of the main frame 7. The bottom plate 13 constitutes the bottom of the machine room 14. The machine room 14 extends over the entire length along the depth direction of the housing 2.

According to the present embodiment, the front end of the lower frame 8 and the front end of the upper frame 9 positioned on the front side of the housing 2 are positioned along the depth direction of the housing 2 so as to be aligned in the height direction of the housing 2. Are aligned with each other. On the back side of the housing 2, the upper frame 9 projects horizontally beyond the lower frame 8 toward the back of the housing 2. The depth direction of the housing 2 can be restated as the longitudinal direction of the housing 2.

As shown in FIG. 5, the first refrigeration cycle unit 3 includes a first refrigerant circuit RA and a second refrigerant circuit RB that are independent of each other. Similarly, the second refrigeration cycle unit 4 includes a third refrigerant circuit RC and a fourth refrigerant circuit RD that are independent of each other.

Since the first to fourth refrigerant circuits RA, RB, RC, and RD have a common configuration, the first refrigerant circuit RA will be described as a representative, and the second to fourth refrigerant circuits RB, RC, RD, About RD, the same referential mark is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 5, the first refrigerant circuit RA includes a variable capacity hermetic compressor 20, a four-way valve 21, an air heat exchange unit 22, a pair of

expansion valves

23a and 23b, a receiver 24, and a water heat exchanger. 25 and the gas-liquid separator 26 are provided as main elements. The plurality of elements are examples of refrigeration cycle components and are connected via a circulation circuit 27 in which the refrigerant circulates.

More specifically, the discharge port of the hermetic compressor 20 is connected to the first port 21 a of the four-way valve 21. The second port 21 b of the four-way valve 21 is connected to the air heat exchange unit 22. As shown in FIG. 6, the air heat exchange unit 22 of the present embodiment includes a pair of

air heat exchangers

29 a and 29 b and a fan 30.

The

air heat exchangers

29a and 29b include a plurality of plate fins and a plurality of refrigerant pipes penetrating the plate fins. The

air heat exchangers

29a and 29b are erected so as to face each other with a gap in the width direction of the housing 2, and are inclined to move away from each other as they move upward.

Further, both end portions of the

air heat exchangers

29a and 29b along the depth direction of the casing 2 are bent in the width direction of the casing 2 so as to face each other. A gap between both ends of the

air heat exchangers

29a and 29b is closed by a pair of shielding

plates

32a and 32b. A cylindrical space surrounded by the

air heat exchangers

29a and 29b and the

shielding plates

32a and 32b defines an exhaust passage 33 extending in the vertical direction.

The fan 30 of the air heat exchanger 22 includes a fan motor 35 that rotates the impeller 34 and a fan cover 37 that surrounds the impeller 34. The fan motor 35 is supported by a fan base 36 straddling between the upper ends of the

air heat exchangers

29a and 29b. The fan cover 37 has a cylindrical exhaust port 38 facing the impeller 34.

When the fan 30 is driven, the air around the chilling unit 1 passes through the

air heat exchangers

29a and 29b and is sucked into the exhaust passage 33. The air sucked into the exhaust passage 33 is sucked up toward the exhaust port 38 and discharged from the exhaust port 38 toward the upper side of the

air heat exchangers

29a and 29b.

Since the chilling unit 1 of the present embodiment includes the first to fourth refrigerant circuits RA, RB, RC, and RD, there are four sets of air heat exchange units 22. The four air heat exchange units 22 are fixed in an upright posture on the upper frame 9 of the main frame 7 and are arranged in a line along the depth direction of the housing 2. Therefore, in this embodiment, the four sets of air heat exchange units 22 are located directly above the machine room 14.

The air heat exchanging portion 22 is formed in a V shape that expands in the width direction of the casing 2 as it goes upward of the casing 2 when the casing 2 is viewed from the front direction F and the rear direction R. Has been. Therefore, the chilling unit 1 in which the air heat exchanging part 22 is positioned on the housing 2 has a drum-shaped shape in which an intermediate part along the height direction is constricted.

Further, in the air heat exchange unit 22 positioned on the front end along the depth direction of the housing 2, one bent end of the

air heat exchangers

29 a and 29 b is in the direction F on the front surface of the housing 2. Exposed. Similarly, in the air heat exchanger 22 positioned on the rear end along the depth direction of the housing 2, the bent one ends of the

air heat exchangers

29 a and 29 b are in the direction of the back surface of the housing 2. Exposed to R.

In other words, one end of the two sets of

air heat exchangers

29a and 29b positioned at both ends along the arrangement direction of the plurality of air heat exchange units 22 is a heat exchange surface exposed around the chilling unit 1. It has become.

By adopting this configuration, the two air heat exchange units 22 positioned on the front end portion and the rear end portion of the casing 2 can be used in addition to the air sucked from the width direction of the chilling unit 1, respectively. Heat exchange can be performed using the air sucked from the front direction F and the rear direction R of the body 2.

As best shown in FIG. 2, the upper frame 9 of the main frame 7 projects horizontally toward the back of the housing 2 rather than the lower frame 8. Of the four sets of air heat exchanging units 22, the rearmost air heat exchanging unit 22 located at the rear end of the housing 2 protrudes from the rear end of the housing 2 in the depth direction of the housing 2. Yes. Therefore, the total length along the depth direction of the housing 2 is shorter than the total length along the alignment direction of the four air heat exchange units 22.

As a result, a stepped portion 43 that is recessed from the rearmost air heat exchanging portion 22 is formed behind the housing 2. The stepped portion 43 defines a space S1 that is continuously open to the side and the back of the housing 2, and the rearmost air heat exchanging portion 22 projects over the space S1.

In the present embodiment, the vertical beam 10 disposed at the rear end of the housing 2 is located at the center along the depth direction of the

air heat exchangers

29a and 29b constituting the rearmost air heat exchange unit 22 or at the center rather than the center. Located behind the body 2. Thereby, the

air heat exchangers

29a and 29b, which are heavy objects, can be stably supported by the main frame 7.

As shown in FIG. 5, the inlets of the

air heat exchangers

29 a and 29 b are connected in parallel to the second port 21 b of the four-way valve 21. The outlets of the

air heat exchangers

29a and 29b are connected to the third port 21c of the four-way valve 21 via the

expansion valves

23a and 23b, the receiver 24, and the water heat exchanger 25. The fourth port 21 d of the four-way valve 21 is connected to the suction side of the hermetic compressor 20 via a gas-liquid separator 26.

Furthermore, the outlet of the gas-liquid separator 26 is connected to the first port 21a of the four-way valve 21 via the bypass pipe 40. A normally closed solenoid valve 41 is provided in the middle of the bypass pipe 40.

As shown in FIG. 5, the water heat exchanger 25 includes a first refrigerant channel 25a, a second refrigerant channel 25b, and a water channel 25c. The first refrigerant flow path 25 a of the water heat exchanger 25 is connected to the receiver 24 of the first refrigerant circuit RA and the third port 21 c of the four-way valve 21. The second refrigerant flow path 25b is connected to the receiver 24 of the second refrigerant circuit RB and the third port 21c of the four-way valve 21. Therefore, in the first refrigeration cycle unit 3, the first refrigerant circuit RA and the second refrigerant circuit RB share one water heat exchanger 25.

Similarly, in the second refrigeration cycle unit 4, the third refrigerant circuit RC and the fourth refrigerant circuit RD are connected in parallel to one water heat exchanger 25 so as to share one water heat exchanger 25. Has been. Therefore, the chilling unit 1 is equipped with two water heat exchangers 25.

As shown in FIGS. 1 to 4, the various elements of the first refrigeration cycle unit 3 and the second refrigeration cycle unit 4 except for the four air heat exchange units 22 are the machine room of the housing 2. 14.

As best shown in FIG. 4, the first refrigeration cycle unit 3 including the first refrigerant circuit RA and the second refrigerant circuit RB includes, for example, a machine room 14 when the housing 2 is viewed in a plan view. It is arranged in the latter half along the depth direction. Similarly, the second refrigeration cycle unit 4 including the third refrigerant circuit RC and the fourth refrigerant circuit RD is, for example, a front half portion along the depth direction of the machine room 14 when the housing 2 is viewed in a plan view. Is arranged.

More specifically, the two hermetic compressors 20, the two receivers 24, and the two gas-liquid separators 26 constituting the first refrigerant circuit RA and the second refrigerant circuit RB are each in a machine room. 14 is installed on the bottom plate 13 so as to be aligned in the depth direction of the machine room 14. Further, the two hermetic compressors 20 and the two gas-liquid separators 26 are arranged adjacent to each other in the width direction of the machine chamber 14.

One water heat exchanger 25 shared by the first refrigerant circuit RA and the second refrigerant circuit RB is installed on the bottom plate 13 so as to be located behind the two gas-liquid separators 26. Therefore, the water heat exchanger 25 is located at the rearmost part of the first refrigeration cycle unit 3.

The two hermetic compressors 20, the two receivers 24, and the two gas-liquid separators 26 constituting the third refrigerant circuit RC and the fourth refrigerant circuit RD are respectively in the first half of the machine room 14, It is installed on the bottom plate 13 so as to line up in the depth direction of the machine room 14. Further, the two hermetic compressors 20 and the two gas-liquid separators 26 are arranged adjacent to each other in the width direction of the machine chamber 14.

One water heat exchanger 25 shared by the third refrigerant circuit RC and the fourth refrigerant circuit RD is installed on the bottom plate 13 so as to be located behind the two gas-liquid separators 26. Therefore, the water heat exchanger 25 is located at the rearmost part of the second refrigeration cycle unit 4.

For this reason, the first refrigeration cycle unit 3 and the second refrigeration cycle unit 4 are arranged in the depth direction of the machine room 14. At the same time, the two water heat exchangers 25 are separated from each other in the depth direction of the machine room 14.

As shown in FIGS. 1 to 3, the water heat exchanger 25 has a square box shape and is erected from the bottom plate 13 of the housing 2 in the height direction of the machine room 14. Each water heat exchanger 25 has a water inlet 28a and a water outlet 28b. The water inlet 28 a and the water outlet 28 b are located on the left side surface of the water heat exchanger 25 when the housing 2 is viewed from the front direction F.

The water inlet 28a is connected to the upstream end of the water passage 25c at the upper end of the left side surface of the water heat exchanger 25. The water outlet 28b is connected to the downstream end of the water flow path 25c at the lower end of the left side surface of the water heat exchanger 25. Therefore, the water inlet 28 a is located at the upper end portion of the machine room 14. The water that has flowed into the water channel 25c from the water inlet 28a flows from the top to the bottom along the direction of gravity in the water channel 25c.

As shown in FIGS. 1 to 4, the water circuit 5 is housed in the machine room 14 together with the first refrigeration cycle unit 3 and the second refrigeration cycle unit 4. The water circuit 5 includes a variable capacity centrifugal pump 45 and first to

fourth water pipes

46a, 46b, 46c, and 46d as main elements.

The centrifugal pump 45 is installed on the bottom plate 13 so as to be located at the rear end of the machine room 14. The centrifugal pump 45 is adjacent to one water heat exchanger 25 shared by the first refrigerant circuit RA and the second refrigerant circuit RB at the rear end of the machine chamber 14.

As shown in FIG. 7, FIG. 8A and FIG. 8B, the centrifugal pump 45 includes a pedestal 48, a casing 49 and a motor 50. The pedestal 48 is a square plate-like element having a predetermined thickness, and is fixed directly on the bottom plate 13 of the housing 2 via fasteners such as a plurality of bolts.

The casing 49 is fixed to the upper surface of the pedestal 48. The casing 49 has a suction port 51 and a discharge port 52 and houses an impeller 53. The suction port 51 and the discharge port 52 are opened in a direction orthogonal to the casing 49.

The motor 50 is an example of a power unit, and is fixed to the upper surface of the base 48 so as to be adjacent to the casing 49. The rotating shaft 54 of the motor 50 passes through the casing 49 and is coaxially connected to the impeller 53.

The spiral pump 45 has a rotation axis O <b> 1 that passes through the center of the rotation shaft 54 of the motor 50. The spiral pump 45 is housed in the machine room 14 in a horizontal posture such that the rotation axis O1 is horizontal. According to the present embodiment, the rotation axis O <b> 1 of the centrifugal pump 45 extends in the width direction of the housing 2.

The suction port 51 of the casing 49 is located on the axis of the rotation axis O1. As shown in FIG. 7, the suction port 51 is opened toward the left side of the casing 2 in the machine room 14 when the casing 2 is viewed from the rear direction R. The discharge port 52 that is in a positional relationship orthogonal to the suction port 51 is opened upward at the upper end portion of the casing 49 so as to be along the vertical direction. Further, the water inlet 28 a of the water heat exchanger 25 adjacent to the spiral pump 45 is located above the discharge port 52.

As shown in FIGS. 8A and 8B, the vortex pump 45 has a horizontal first central axis C1 lying in the width direction of the housing 2 through the center of the suction port 51 and a housing through the center of the discharge port 52. And a vertical second central axis C2 standing in the height direction of the body 2. In the spiral pump 45 of the present embodiment, the base 48 of the spiral pump 45 is such that the intersection P1 where the central axis C1 and the second central axis C2 intersect with a reference point defined in advance inside the machine chamber 14. Is fixed on the bottom plate 13 of the housing 2 so that the position of the housing 2 can be adjusted in the depth direction and the width direction.

Specifically, the bottom plate 13 of the housing 2 has a plurality of screw holes into which bolts are screwed at positions where the pedestals 48 are placed, and the screw holes are respectively predetermined in the depth direction and the width direction of the housing 2. Multiple arrays are arranged with an interval of. Therefore, by selecting the screw hole into which the bolt passing through the base 48 is screwed, the fixing position of the spiral pump 45 with respect to the bottom plate 13 is set to the depth of the housing 2 so that the intersection point P1 of the spiral pump 45 matches the reference point. It can be shifted in the direction and width direction.

Furthermore, the outer diameter of the motor 50 of the centrifugal pump 45 is smaller than the full length. Therefore, by setting the centrifugal pump 45 horizontally in the machine room 14, the area above the motor 50 is widely opened, and this area functions as the piping space S2.

As shown in FIG. 8A, the first water pipe 46 a of the water circuit 5 is connected to the suction port 51 of the centrifugal pump 45. The first water pipe 46 a is drawn to the left side of the casing 49 and then bent at a right angle toward the rear of the machine room 14. A strainer 56 is connected to the rear end of the first water pipe 46a.

The rear end of the first water pipe 46a and the strainer 56 protrude from the rear end portion of the machine room 14 to the stepped portion 43 behind the housing 2, and are accommodated in the space S1 defined by the stepped portion 43. Yes. For this reason, most of the strainer 56 is positioned directly below the rearmost air heat exchange unit 22.

Further, the strainer 56 is connected to a water outlet on the side of a utilization device such as an air conditioner through accessories such as various valves and flexible joints and a field pipe laid on the installation surface G. .

As shown in FIG. 7, FIG. 8A and FIG. 8B, the second water pipe 46 b is formed between the discharge port 52 of the centrifugal pump 45 and the water inlet 28 a of the water heat exchanger 25 corresponding to the first refrigeration cycle unit 3. Are connected. The second water pipe 46 b is led right above the casing 49 and then bent at a right angle toward the water heat exchanger 25 in front of the centrifugal pump 45. The second water pipe 46 b is routed horizontally in the depth direction of the housing 2 through a pipe space generated on the motor 50.

As shown in FIGS. 2 to 5, the third water pipe 46 c includes water outlets 28 b of the water heat exchanger 25 corresponding to the first refrigeration cycle unit 3 and water heat corresponding to the second refrigeration cycle unit 4. The water inlet 28a of the exchanger 25 is connected in series. The third water pipe 46 c is routed in the depth direction of the housing 2 through the sides of the two gas-liquid separators 26 of the first refrigeration cycle unit 3.

The fourth water pipe 46d is connected to the water outlet 28b of the water heat exchanger 25 corresponding to the second refrigeration cycle unit 4. The fourth water pipe 46 d is routed horizontally toward the rear of the water heat exchanger 25 so as to be along the bottom plate 13 of the housing 2, and the pipe above the motor 50 just before the motor 50. Launched for space.

A discharge pipe 58 having a check valve 57 is connected to the rear end of the fourth water pipe 46d. The check valve 57 and the discharge pipe 58 are arranged in the pipe space S2. The rear end of the discharge pipe 58 protrudes from the rear end portion of the machine room 14 to the stepped portion 43 behind the housing 2, and includes accessories such as various valves and flexible joints, and the installation surface G. For example, it is connected to a water inlet on the side of a utilization device such as an air conditioner through another on-site piping.

As shown in FIG. 3, a drain pan 60 is disposed between the machine room 14 of the housing 2 and the four air heat exchange units 22. The drain pan 60 is an element that receives dew condensation water or the like dripping from the

air heat exchangers

29 a and 29 b of the air heat exchanger 22, and includes a pair of

troughs

61 a and 61 b and a drain collection board 62.

The

casings

61a and 61b extend straight along the arrangement direction of the four sets of air heat exchangers 22, and are positioned directly below the

air heat exchangers

29a and 29b of the air heat exchangers 22. 2 is supported by the upper frame 9.

The

cages

61a and 61b are arranged on the machine room 14 in parallel with each other in the width direction of the housing 2. The machine room 14 is communicated with the exhaust passages 33 of the four air heat exchange units 22 through a gap between the

flanges

61a and 61b.

The drain collection board 62 is supported by the upper frame 9 so as to straddle between the rear ends of the

flanges

61a and 61b. The drain collection board 62 is located immediately above the centrifugal pump 45. In other words, the drain collection board 62 defines the ceiling of the piping space S2. In the present embodiment, the discharge pipe 58 having the upstream end of the second water pipe 46 b connected to the discharge port 52 and the check valve 57 is positioned between the drain collection board 62 and the spiral pump 45.

As shown in FIGS. 2 and 3, the rear end portion of the drain collection board 62 protrudes above the stepped portion 43 behind the housing 2. Furthermore, the drain collection board 62 has a drain pipe connection port 64 disposed near the center in the width direction. The drain pipe connection port 64 is opened downward so as to protrude from the bottom of the drain collection board 62 to the upper end of the space S <b> 1 defined by the stepped portion 43, and a drain pipe (not shown) is connected to the drain pipe connection port 64. It has become so.

排水 Opening the drain pipe connection port 64 downward from the bottom of the drain collection board 62 improves the drainage of the condensed water received by the drain collection board 62. At the same time, by arranging the drain pipe connection port 64 at the center in the width direction of the drain collection board 62, good drainage can be secured even if there is only one drain pipe connection port 64.

In addition, in the present embodiment, since the drain pipe connection port 64 protrudes from the upper end of the space S1, the work for connecting the drain pipe to the drain pipe connection port 64 can be easily performed.

As shown in FIGS. 1 to 4, the electrical unit 6 is installed at the front end of the machine room 14 on the front side of the housing 2. The electrical unit 6 of this embodiment includes an electrical box 70 and a fan device 71. The electrical box 70 is fixed on the bottom plate 13 of the housing 2 and has the same height as the machine room 14.

The electrical box 70 accommodates various electrical components that control the operation of the first refrigeration cycle unit 3 and the second refrigeration cycle unit 4. An example of the electrical component includes a plurality of control boards that control the voltage and frequency applied to the hermetic compressor 20, a plurality of power modules such as an inverter and a converter, a plurality of smoothing capacitors, a plurality of reactors for power factor improvement, A plurality of filter substrates, a plurality of terminal blocks, a plurality of electromagnetic contactors, and the like.

Among various electrical components, for example, a plurality of control boards and a plurality of power modules can be rephrased as heat generating components that generate a large amount of heat during operation. Since the heat-generating component requires active heat dissipation, it is thermally connected to a plurality of heat sinks (not shown). The heat sink is exposed to an air passage (not shown) inside the electrical box 70. The air passage is located at the center of the electrical box 70 and is erected so as to penetrate the electrical box 70 in the height direction.

3 and 4, the fan device 71 is attached to the upper surface of the electrical box 70. The fan device 71 includes an elongated box-shaped fan case 72 and a plurality of

electric fans

73 a, 73 b, 73 c accommodated in the fan case 72.

The fan case 72 is attached to the center of the upper surface of the electrical box 70. The fan case 72 extends in the depth direction of the housing 2 so as to surround the upper end of the air passage opened in the upper surface of the electrical box 70. Further, the fan case 72 protrudes upward from the upper surface of the electrical box 70. The upper end portion of the fann case 72 enters the exhaust passage 33 of the foremost air heat exchange unit 22 located at the front end portion of the housing 2 through the space between the

flanges

61a and 61b.

The

electric fans

73a, 73b, 73c are arranged in a line at intervals in the depth direction of the housing 2. The

electric fans

73a, 73b, and 73c are incorporated in the fan case 72 in a posture in which the rotation axis is placed vertically so as to be positioned immediately above the air passage of the electrical box 70. The

electric fans

73a, 73b, 73c all exhaust toward the upper side of the fan case 72.

When the

electric fans

73a, 73b, 73c operate, negative pressure acts on the air passage of the electrical box 70. Thereby, the air around the housing 2 is sucked into the air passage from the bottom plate 13 side of the housing 2. The sucked air flows through the air passage from the bottom to the top and is guided to the fan case 72.

¡The heat sink that receives the heat from the heat generating parts is directly exposed to the air flowing through the air passage. Thereby, the heat of the heat generating component transmitted to the heat sink is released by multiplying the air flow, and the heat generating component is forcibly cooled.

The air that has passed through the air passage is sucked up by the

electric fans

73a, 73b, and 73c and discharged from the upper end of the fan case 72 to the exhaust passage 33 of the foremost air heat exchange section 26.

The air discharged into the exhaust passage 33 is sucked up together with the air that has passed through the

air heat exchangers

29a and 29b by the operation of the fan 30, and is discharged from the exhaust port 38 to the upper side of the chilling unit 1. Therefore, the air after cooling the heat-generating component does not stay in the machine room 14, and the temperature rise of the machine room 14 can be avoided.

On the other hand, in the chilling unit 1 of the present embodiment, for example, a standard centrifugal pump 45 disclosed in FIGS. 8A and 8B can be selected as appropriate so that a centrifugal pump that can provide the maximum flow rate and maximum head of water required by the unit can be selected. In addition, two types of other

centrifugal pumps

80 and 90 having different capacities from the centrifugal pump 45 are prepared. Since the configuration of the other

centrifugal pumps

80 and 90 is the same as that of the standard centrifugal pump 45 disclosed in FIGS. 8A and 8B, the same components are denoted by the same reference numerals and description thereof is omitted. To do.

The other centrifugal pump 80 disclosed in FIGS. 9A and 9B has a smaller capacity than the standard centrifugal pump 45. Specifically, the sizes of the casing 49 and the motor 50 are slightly smaller than the standard centrifugal pump 45.

The other centrifugal pump 90 disclosed in FIGS. 10A and 10B has a smaller capacity than the centrifugal pump 80 disclosed in FIGS. 9A and 9B, and the size of the casing 49 and the motor 50 is smaller than that of the centrifugal pump 80. Small around.

As a result, in each of the other

centrifugal pumps

80 and 90, the distance along the width direction of the housing 2 from the intersection P1 between the first central axis C1 and the second central axis C2 to the center of the suction port 51 is defined as Y1. When the distance along the height direction of the housing 2 from the intersection P1 to the center of the discharge port 52 is Z1, and the distance along the height direction of the housing 2 from the intersection P1 to the lower surface of the pedestal 48 is Z2, the spiral Between the

pumps

80 and 90, Y1 is equal and Z1 and Z2 are different.

Furthermore, Y1, Z1, and Z2 of the other

centrifugal pumps

80, 90 are all different from Y1, Z1, and Z2 of the standard centrifugal pump 45.

From this, when another

spiral pump

80 or 90 is directly mounted on the bottom plate 13 of the machine chamber 14 instead of the standard spiral pump 45, the intersection P1 is the machine chamber in each of the other spiral pumps 80 or 90. 14 in the X direction along the depth direction of the housing 2, the Y direction along the width direction of the housing 2, and the Z direction along the height direction of the housing 2.

Therefore, in this embodiment, when the other centrifugal pump 80 disclosed in FIGS. 9A and 9B is installed in the machine chamber 14 instead of the standard centrifugal pump 45, a dedicated first bracket 81 is used. The first bracket 81 is a plate-like element interposed between the pedestal 48 and the bottom plate 13 of another centrifugal pump 80, and has a predetermined thickness t1 along the Z direction.

The first bracket 81 is fixed on the bottom plate 13 with a plurality of bolts together with a pedestal 48 of another spiral pump 80. At this time, by selecting the screw hole on the side of the bottom plate 13 into which the bolt passing through the pedestal 48 and the first bracket 81 is screwed, the bottom plate 13 so that the intersection point P1 of the vortex pump 80 matches the reference point. The swivel pump 80 can be fixed in the depth direction (X direction) and the width direction (Y direction) of the housing 2. At the same time, the fixed position of the centrifugal pump 80 with respect to the bottom plate 13 can be pushed up in the height direction (Z direction) of the housing 2 by the thickness t1 of the first bracket 81.

Therefore, by using the first bracket 81, the intersection point P1 of the other centrifugal pump 80 can be matched with the reference point in the machine room 14.

On the other hand, when the other centrifugal pump 90 disclosed in FIGS. 10A and 10B is installed in the machine room 14 instead of the standard centrifugal pump 45, a dedicated second bracket 91 is used. The second bracket 91 is a plate-like element interposed between the pedestal 48 and the bottom plate 13 of another spiral pump 90, and has a predetermined thickness t2 along the Z direction. The thickness t2 of the second bracket 91 is larger than the thickness t1 of the first bracket 81.

The second bracket 91 is fixed on the bottom plate 13 with a plurality of bolts together with the pedestal 48 of the other centrifugal pump 90. At this time, by selecting a screw hole on the side of the bottom plate 13 into which the bolt passing through the pedestal 48 and the second bracket 91 is screwed, the bottom plate 13 so that the intersection point P1 of the spiral pump 90 matches the reference point. The swivel pump 90 can be fixed in the depth direction (X direction) and the width direction (Y direction) of the housing 2. At the same time, the fixed position of the centrifugal pump 90 with respect to the bottom plate 13 can be pushed up in the height direction (Z direction) of the housing 2 by the thickness t2 of the second bracket 91.

Therefore, by using the second bracket 91, the intersection point P1 of the other centrifugal pump 90 can be matched with the reference point in the machine room 14.

In the chilling unit 1, even when the pump capacity is changed, the position of the water heat exchanger 25 and the position of the strainer 56 connected to the on-site piping are generally the same. In the present embodiment, the fixing position of the spiral pumps 45, 80, 90 relative to the machine chamber 14 is changed so that the intersection P1 of the three types of spiral pumps 45, 80, 90 matches the reference point in the machine chamber 14. Can do.

For this reason, for example, when the standard centrifugal pump 45 is replaced with another

centrifugal pump

80 or 90 having a different capacity, the length of the first water pipe 46a connected to the suction port 51 and the discharge port 52 are connected. It is only necessary to adjust the length of the second water pipe 46b.

Particularly, in the other spiral pumps 80 and 90, since the distance Y1 from the intersection P1 to the center of the suction port 51 is equal, the first water pipe 26a can be shared. As a result, the shapes of the first water pipe 46a and the second water pipe 46b for each of the three types of

centrifugal pumps

45, 80, 90 can be prevented from greatly changing or becoming complicated.

Therefore, it is not necessary to significantly change the routing route of the first water pipe 46a and the second water pipe 46b in accordance with the pump capacity, and there is an advantage that the pressure loss can be suppressed and the space can be saved. .

Next, the operation of the chilling unit 1 will be described.

When the first refrigeration cycle unit 3 and the second refrigeration cycle unit 4 start operation in the cooling mode, the four-way valves 21 of the first to fourth refrigerant circuits RA, RB, RC, RD are shown by solid lines in FIG. As shown, the first port 21a is switched to communicate with the second port 21b, and the third port 21c is switched to communicate with the fourth port 21d.

Furthermore, high-temperature and high-pressure gas-phase refrigerant is discharged from the first to fourth refrigerant circuits RA, RB, RC, and RD into the circulation circuit 27. The high-temperature and high-pressure gas-phase refrigerant discharged from the hermetic compressor 20 is guided to the

air heat exchangers

29a and 29b via the four-way valve 21.

The gas-phase refrigerant guided to the

air heat exchangers

29a and 29b is condensed by heat exchange with the air passing through the

air heat exchangers

29a and 29b, and is changed into a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is depressurized in the process of passing through the

expansion valves

23a and 23b, and changes to an intermediate-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the water heat exchanger 25 via the receiver 24.

In the present embodiment, the first refrigerant circuit RA and the second refrigerant circuit RB share one water heat exchanger 25, and the third refrigerant circuit RC and the fourth refrigerant circuit RD share one other water heat. The exchanger 25 is shared. For this reason, in the first refrigerant circuit RA and the second refrigerant circuit RB, a gas-liquid two-phase refrigerant having an intermediate pressure is supplied to the first refrigerant channel 25a and the second refrigerant channel 25b of the water heat exchanger 25, respectively. It is guided and exchanges heat with water flowing through the water flow path 25c.

As a result, the gas-liquid two-phase refrigerant flowing in the first refrigerant flow path 25a and the second refrigerant flow path 25b evaporates and receives heat from the water in the water flow path 25c, and the low-temperature and low-pressure gas-liquid is generated by latent heat of evaporation. Change to two-phase refrigerant. The water in the water flow path 25c becomes cold water by removing latent heat.

The water flow path 25c of the water heat exchanger 25 shared by the first refrigerant circuit RA and the second refrigerant circuit RB is connected to the third refrigerant circuit RC and the fourth refrigerant circuit RD via the third water pipe 46c. The other water heat exchanger 25 to be shared is connected in series to the water flow path 25c.

Therefore, the water cooled in the water heat exchanger 25 shared by the first refrigerant circuit RA and the second refrigerant circuit RB is the other water shared by the third refrigerant circuit RC and the fourth refrigerant circuit RD. In the process of passing through the water flow path 25c of the heat exchanger 25, it is cooled again by heat exchange with the gas-liquid two-phase refrigerant flowing through the first refrigerant flow path 25a and the second refrigerant flow path 25b of the water heat exchanger 25. It is. The water cooled in two stages is supplied from the fourth water pipe 46d to the utilization equipment side via the on-site pipe.

The low-temperature and low-pressure gas-liquid two-phase refrigerant that has passed through each water heat exchanger 25 is guided to the gas-liquid separator 26 via the four-way valve 21, where it is separated into a liquid-phase refrigerant and a gas-phase refrigerant. . The gas-phase refrigerant separated from the liquid-phase refrigerant is sucked into the hermetic compressor 20 and is again discharged as a high-temperature / high-pressure gas-phase refrigerant from the hermetic compressor 20 to the circulation circuit 27.

On the other hand, when the first refrigeration cycle unit 3 and the second refrigeration cycle unit 4 start operation in the heating mode, the four-way valves 21 of the first to fourth refrigerant circuits RA, RB, RC, RD are shown in FIG. As indicated by a broken line, the first port 21a is switched to communicate with the third port 21c, and the second port 21b is switched to communicate with the fourth port 21d.

In the heating mode, the high-temperature and high-pressure gas-phase refrigerant compressed by the hermetic compressor 20 is guided to the water heat exchanger 25 via the four-way valve 21. Even in the heating mode, the water flow path 25c of one water heat exchanger 25 shared by the first refrigerant circuit RA and the second refrigerant circuit RB, and the third refrigerant circuit RC and the fourth refrigerant circuit RD are shared. Since the water flow path 25c of the other one water heat exchanger 25 is connected in series, the water flowing through the water flow path 25c is the gas phase flowing through the first refrigerant flow path 25a and the second refrigerant flow path 25b. It is heated in two stages by heat exchange with the refrigerant. The water heated by receiving the heat of the gas-phase refrigerant is supplied from the fourth water pipe 46d to the utilization equipment side via the on-site pipe.

The high-pressure liquid-phase refrigerant that has passed through the water heat exchanger 25 is changed to an intermediate-pressure gas-liquid two-phase refrigerant in the process of passing through the receiver 24 and the

expansion valves

23a and 23b, and is also introduced into the

air heat exchangers

29a and 29b. It is burned. The gas-liquid two-phase refrigerant guided to the

air heat exchangers

29a and 29b evaporates by heat exchange with the air passing through the

air heat exchangers

29a and 29b, and changes to a low-temperature and low-pressure gas-liquid two-phase refrigerant.

The low-temperature and low-pressure gas-liquid two-phase refrigerant that has passed through the

air heat exchangers

29a and 29b is guided to the gas-liquid separator 26 via the four-way valve 21, where it is separated into a liquid-phase refrigerant and a gas-phase refrigerant. The The gas-phase refrigerant separated from the liquid-phase refrigerant is sucked into the hermetic compressor 20 and is again discharged as a high-temperature / high-pressure gas-phase refrigerant from the hermetic compressor 20 to the circulation circuit 27.

According to the chilling unit 1 of the present embodiment, the spiral pump 45 that supplies water to the water heat exchanger 25 shared by the first refrigerant circuit RA and the second refrigerant circuit RB has a rotation axis that passes through the center of the rotation shaft 54. The O 1 is fixed on the bottom plate 13 of the machine room 14 in a horizontal posture along the width direction of the casing 2. As a result, the casing 49 housing the impeller 53 and the motor 50 lie on the bottom plate 13 so as to be aligned in the width direction of the housing 2.

Therefore, it is possible to avoid the swirl pump 45 from projecting greatly above the bottom plate 13 and to effectively utilize the limited space in the machine room 14. At the same time, the overall height of the chilling unit 1 including the air heat exchange units 22 arranged on the machine room 14 can be suppressed as low as possible.

Furthermore, since the spiral pump 45 is placed horizontally, a sufficient piping space S2 can be secured between the motor 50 and the drain collection board 62, and the first water piping 46a is utilized using the piping space S2. And a check valve 57 can be arranged.

Moreover, since the discharge port 52 of the spiral pump 45 is opened upward at the upper end portion of the casing 49 so as to be along the vertical direction, the discharge port 52 is connected to the water inlet 28a of the water heat exchanger 25. The second water pipe 46 b can be routed over the centrifugal pump 45.

In other words, it is not necessary to raise the second water pipe 46b through the side of the centrifugal pump 45, and the discharge port 52 and the water inlet 28a can be connected at the shortest distance. Therefore, there is an advantage that the routing route of the second water pipe 46b can be simplified, the piping work can be easily performed, and the pressure loss can be reduced.

The configuration as described above is particularly useful in a heat pump device that performs large-capacity heat transport such as a chilling unit. In other words, the larger the amount of heat required on the user equipment side, the larger the volume of the centrifugal pump, the water heat exchanger, and the air heat exchanger. It is desirable to increase the amount of heat transport.

As in the chilling unit 1 of the present embodiment, the

air heat exchangers

29a and 29b are arranged on the housing 2 in which the spiral pump 45 and the water heat exchanger 25 are accommodated, so that the spiral pump 45 and the water heat exchange are arranged. The space efficiency in the machine chamber 14 can be improved while increasing the volume of the vessel 25 and the heat exchange area of the

air heat exchangers

29a and 29b. Therefore, it is possible to transport a large volume of heat while reducing the size of the heat pump device.

Although several embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

For example, the rotation axis of the motor of the spiral pump is not limited to be placed horizontally so as to be along the width direction of the housing, but may be placed horizontally so as to be along the depth direction of the housing. That is, the casing and the motor may be arranged side by side in the depth direction of the housing so that the casing is located behind the motor, and the suction port of the casing may be opened toward the rear of the machine room.

According to this configuration, the first water pipe connected to the suction port can be drawn straight out toward the rear of the machine room. Therefore, the shape of the first water pipe can be simplified and the pressure loss can be kept low.

Furthermore, in the said embodiment, although the discharge port of the casing was opened upward so that the vertical direction might be followed, the opening direction of a discharge port may incline a little with respect to a perpendicular line.

DESCRIPTION OF SYMBOLS 2 ... Housing | casing, 14 ... Machine room, 25 ... Water heat exchanger, 25a, 25b ... Refrigerant flow path (1st refrigerant flow path, 2nd refrigerant flow path), 25c ... Water flow path, 28a ... Water inlet, 45, 80, 90 ... spiral pump, 46b ... water piping (second water piping), 49 ... casing, 50 ... power section (motor), 51 ... suction port, 52 ... discharge port, 53 ... impeller, O1 ... rotation Axis.

Claims

A housing having a machine room;
A water heat exchanger housed in the machine room, having a water channel and a refrigerant channel, and performing heat exchange between water flowing through the water channel and a refrigerant flowing through the refrigerant channel;
A swirl pump housed in the machine room for supplying water to the water flow path of the water heat exchanger,
The centrifugal pump includes a casing having a suction port and a discharge port opened in directions orthogonal to each other, and a power unit that rotates an impeller in the casing, and the discharge port opens upward in the machine room Installed on the bottom of the machine room in a posture in which the rotational axis of the power unit is placed horizontally,
The water heat exchanger has a water inlet connected to an upstream end of the water flow path at a position higher than the discharge port of the spiral pump,
A refrigeration cycle apparatus in which the discharge port of the spiral pump and the water inlet of the water heat exchanger are connected by a water pipe.
The casing has an elongated shape whose depth dimension is larger than the width dimension, and the spiral pump is installed in the machine room in a horizontal posture in which the rotation axis of the power unit is along the width direction of the casing. The refrigeration cycle apparatus according to claim 1 installed at the bottom of the refrigeration.
A discharge pipe through which water heat-exchanged by the water heat exchanger flows is further provided, and the discharge pipe protrudes out of the casing from the end of the machine room through the power unit. The refrigeration cycle apparatus described.
And a plurality of air heat exchange units arranged in at least one row on the housing, and the swirl below one air heat exchange unit located at the end of the air heat exchange units arranged in a row. The refrigeration cycle apparatus according to claim 2 or 3, wherein the pump is located.
5. At least a part of the air heat exchanging portion located at the end of the air heat exchanging portions arranged in a row protrudes from the end portion of the machine room in the depth direction of the housing. The refrigeration cycle apparatus described.
A drain collection board for receiving dew condensation water dripping from the air heat exchange unit is arranged between the air heat exchange unit located at the end of the air heat exchange units arranged in a row and the spiral pump. Item 5. The refrigeration cycle apparatus according to Item 4.
The refrigeration cycle apparatus according to claim 6, wherein a piping space is formed between the drain recovery board and the power unit of the centrifugal pump, and the discharge piping is arranged in the piping space.
The spiral pump includes a first central axis extending in the lateral direction through the center of the suction port, a second central axis extending in the vertical direction through the center of the discharge port, and the first central axis. An intersecting point intersecting the second central axis, and the spiral pump is arranged in the depth direction and width of the casing so that the intersecting point matches a reference point defined in the machine room in advance. The refrigeration cycle apparatus according to claim 2, wherein the refrigeration cycle apparatus is installed at the bottom of the machine room so as to be positionally adjustable in a direction.
The centrifugal pump has a size different from that of the centrifugal pump, and further includes at least one other centrifugal pump that is selectively installed on the bottom of the machine chamber instead of the centrifugal pump. A first central axis that extends laterally through the center, a second central axis that extends longitudinally through the center of the discharge port, and the first central axis and the second central axis intersect. And the position of the other spiral pump can be adjusted in the depth direction, width direction and height direction of the housing via a dedicated bracket so that the intersection point matches the reference point. The refrigeration cycle apparatus according to claim 8, installed at the bottom of the machine room.