JP2002372343A - Refrigeration cycle unit and pump unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance lubrication at a sliding part of a pump unit without causing a refrigerant to be influenced by heat of a motor section in the pump unit conveying liquid refrigerant or the like of an air conditioner or the like. SOLUTION: A rotor 21 comprising a permanent magnet is provided in a sealed container 12, and a drive side magnet 10 for transmitting torque to the rotor is provided outside of the container so that a pump system 14 is rotated. The pump system 14 is constituted of a casing 15 and a pump rotor 16, and a passage for allowing a carrier liquid to flow to the shaft-sliding part is provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a configuration of a pump device mainly used for transporting a liquid refrigerant of an air conditioner and a refrigerant cycle device using the pump device.

[0002]

2. Description of the Related Art At present, a general air conditioner is operated in a heat pump cycle in which a gas refrigerant is compressed by a compressor to obtain a transfer power, and heat is drawn from a low-temperature side heat source to a high-temperature side heat source. In order to transfer heat to the outside air temperature, which is a heat source higher than the temperature of the room to be cooled, the refrigerant is condensed at a higher pressure than the outside air at a high pressure, and then evaporated at a lower pressure to a lower temperature than the room. However, in systems that transfer heat from the high-temperature side to the low-temperature side, such as when using the heat storage of a heat storage type air conditioner or a burner heating type air conditioner, there is no need to make a difference between the condensation temperature and the evaporation temperature of the refrigerant. Therefore, if only the transfer power of the refrigerant can be increased, the operation becomes possible. Therefore, a pump device for transporting the liquid refrigerant for increasing the pressure of the liquid refrigerant has been considered.

FIG. 15 is a sectional view showing a conventional pump device disclosed in Japanese Patent No. 2977228, for example. In the figure, a stator 44 is arranged outside the sealed case 12 and a rotor 43 is arranged inside the sealed case 12 to constitute a motor unit. The orbiting scroll 61 is connected to the other end of the rotating shaft 17 to which the rotor 43 is connected to one end, and the scroll pump 63 is configured by meshing with the fixed scroll 62.

The flow of the liquid refrigerant will be described. The liquid refrigerant sucked from the suction pipe 29 is pressurized by the scroll pump 63 and discharged to the discharge chamber 64. The discharged liquid refrigerant flows through the through hole 65 to the back pressure chamber 66. Further, it flows into the sealed case 12 through the case communication hole 67, and is discharged from the discharge pipe 31 through the communication groove 68 and the passage 69 on the outer periphery of the sealed case.

On the other hand, the liquid refrigerant for lubrication is guided from the discharge chamber 64 through the spiral groove 70 to the thrust receiving portion 71, and from the thrust receiving portion 71 to the space 72.
Are provided to supply the liquid to the bearing surface 74. With such a configuration, the liquid refrigerant is guided to the sliding portion of rotation, and lubrication and cooling are obtained. When the liquid refrigerant passes through the inner wall surface of the closed casing 12, the heat of the stator 44 is transferred by the refrigerant. Upon receipt, the stator 44 is cooled.

[0006]

Since the conventional pump device used for transporting the liquid refrigerant in the refrigeration cycle of an air conditioner or the like is constructed as described above, the structure in which the heat generated in the stator 44 of the motor unit is removed by the liquid refrigerant. Therefore, when the degree of supercooling of the liquid refrigerant is small, gasification occurs in the closed case, and there is a problem that a stable flow rate of the refrigerant cannot be obtained.

In addition, since the fixed scroll 62 and the orbiting scroll 61 are in contact with each other because of the positive displacement pump, the high pressure portion and the low pressure portion are sealed, and the sliding condition is severe in the case of a liquid refrigerant without lubricating oil, resulting in wear. There is a problem that the pump performance may be accelerated and the pump performance may be reduced.

Further, when the pressure loss of the main passage of the liquid refrigerant is small, there is no pressure difference between the inlet and the outlet of the lubrication passage to the rotary sliding portion such as the bearing surface 74, so that the flow of the lubrication refrigerant hardly occurs. The liquid refrigerant gasifies due to the heat generated by the frictional heat, which may cause insufficient lubrication.On the contrary, if the pressure loss in the main flow path is increased to secure the flow rate in the lubrication flow path, the pump There was a problem that the efficiency was reduced.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems. A first object of the present invention is to enable an energy-saving operation using only the power for transporting a liquid refrigerant and to simplify the structure of a pump mechanism. It is an object of the present invention to provide a pump device that can simplify the configuration of a refrigerant cycle and a pump mechanism.

It is a second object of the present invention to provide a pump device capable of obtaining a stable flow rate of a liquid such as a refrigerant.

A third object of the present invention is to provide a pump device capable of surely lubricating by reliably supplying a carrier fluid to a rotary sliding portion of a pump mechanism of a pump device for carrying a liquid carrier fluid such as a refrigerant. The purpose is to gain.

It is a fourth object of the present invention to provide a pump device capable of preventing a rotary sliding portion of a pump mechanism of a pump device from being worn.

[0013]

According to a first aspect of the present invention, there is provided a refrigerant cycle apparatus comprising: a heat source side heat exchanger for condensing refrigerant and recovering heat of a heat source; and a pump for conveying the condensed refrigerant to a load side. In a refrigerant cycle in which a device, a throttle device that adjusts the flow rate of the refrigerant, and a load-side heat exchanger that evaporates the refrigerant and supplies heat from the heat source to a load are sequentially connected by piping and convey heat, A pump mechanism that is provided in the closed vessel of the pump device and that boosts the pressure of the refrigerant from the heat source side heat exchanger by rotating a pump rotor, and the refrigerant that is provided in the pump mechanism and supports the rotation of the pump rotor. And a discharge chamber which is provided around the pump mechanism in the closed container and stores the pressurized refrigerant so as to be able to be filled therein. Is obtained as storing in the liquid state in the discharge chamber with circulating said refrigerant cycle at a gaseous state by evaporation the liquid state by condensation as iodine.

According to a second aspect of the present invention, there is provided a refrigerant cycle device provided with a backflow preventing means for preventing a backflow on the discharge side of the pump device.

According to a third aspect of the present invention, there is provided a pump apparatus having an inlet and an outlet for a carrier fluid, a sealed container capable of being filled with the carrier fluid, and a pump rotating body provided in the sealed container and arranged inside. A pump mechanism that is driven to rotate and pressurizes the carrier fluid guided from the inlet, a rotor of a driving device having a permanent magnet that is directly connected to the pump rotor and rotates in the closed container, and a permanent magnet of the rotor. A drive unit for transmitting a rotational force from the outside to the permanent magnet with the closed container interposed therebetween, wherein the carrier fluid discharged from the pump mechanism fills the closed container and is discharged from the outlet. .

According to a fourth aspect of the present invention, there is provided a pump apparatus according to the present invention, wherein a rotating force is transmitted to the permanent magnet of the rotor which is directly connected to the pump rotating body and rotates in the closed container and the permanent magnet with the closed container interposed therebetween. The driving device main body includes a motor that generates a driving force, and a driving-side magnet that is directly connected to the motor and that is disposed to face the permanent magnet and the closed container via the closed container and that transmits a rotating force to the permanent magnet. It is a thing.

According to a fifth aspect of the present invention, there is provided a pump device wherein the pump mechanism is directly connected to a rotor of the driving device, and is rotatably supported by a bearing portion on a casing constituting an outer shell of the pump mechanism. A hollow hole into which the carrier fluid in the closed container flows is provided therein, and the carrier fluid flows from one surface side to the other surface side of the casing through the hollow hole.

According to a sixth aspect of the present invention, there is provided a pump device wherein the pump mechanism is directly connected to a rotor of the driving device, and is rotatably supported by a bearing portion on a casing constituting an outer shell of the pump mechanism. A hollow hole into which the carrier fluid in the closed container flows is provided, and a through hole is formed in the shaft from the hollow hole to a sliding surface of the bearing portion.

According to a seventh aspect of the present invention, in the pump apparatus, the pump mechanism is provided around a shaft directly connected to a rotor of the driving device, and the blade of the pump rotating body that rotates and covers the blade. The vortex pump has a casing that forms a compression chamber on the outer periphery of the blade as described above, and a suction port and a discharge port that are provided in the casing and suck and discharge the carrier fluid.

According to an eighth aspect of the present invention, in the pump device, the pump mechanism includes a cylinder eccentric from a center of a shaft directly connected to a rotor of the driving device, and an outer peripheral portion of the cylinder so as to cover the cylinder. A rotary pump having a casing forming a compression chamber, and a suction port and a discharge port provided in the casing for sucking and discharging the carrier fluid.

According to a ninth aspect of the present invention, in the pump device of the present invention, the pump mechanism of the vortex pump is a uniform space portion in which a gap with the casing is provided at a substantially central portion of the front and rear surfaces of the pump rotating body. A pressure chamber, an inflow passage through which a part of the carrier fluid in the closed vessel flows into the pressure equalizing chamber from before and after the casing, and the pump rotor between the pressure equalizing chamber and the compression chamber. A seal portion before and after partitioning with a slight gap through which a fluid passes between the casing and the casing, wherein the carrier fluid flowing into the pressure equalizing chamber of the pump rotor from the inflow passage passes through the seal portion, and It is designed to flow into the compression chamber.

According to a tenth aspect of the present invention, there is provided a pump device wherein the inflow passage of the carrier fluid flowing into the pressure equalizing chamber from the front and rear of the casing is provided between the front and rear of the pump rotor which rotatably supports the pump rotor. The bearing portion is provided with a bearing, and a groove is provided on a sliding surface of the bearing.

According to an eleventh aspect of the present invention, there is provided a pump apparatus in which a pressure equalizing hole for flowing the carrier fluid in the pressure equalizing chamber on the front and rear surfaces of the pump rotating body is provided.

In a twelfth aspect of the present invention, the pressure equalizing hole is penetrated through the front and rear surfaces of the pump rotating body.

According to a thirteenth aspect of the present invention, in the pump device, the seal portion before and after the partition between the pump rotating body and the casing with a slight gap through which the carrier fluid passes has a small gap. From the pressure equalizing chamber side.

In a fourteenth aspect of the present invention, the pump mechanism is formed of a resin.

According to a fifteenth aspect of the present invention, there is provided a pump device, wherein a discharge chamber for discharging the carrier fluid from the pump mechanism is provided in the closed container, and a predetermined pressure is applied from the discharge chamber to the suction port side of the pump mechanism. A relief valve that opens at the end is provided.

A pump device according to a sixteenth aspect of the present invention is provided with a suction flash detecting means for detecting whether or not bubbles are generated in the suction liquid, in a suction pipe of the closed container which is an inlet of the carrier fluid. The operation of the pump device is controlled by suction flash detection means.

A pump device according to a seventeenth aspect of the present invention uses the carrier fluid as a refrigerant of a refrigeration cycle.

In the pump apparatus according to the present invention, the pump rotating body is fitted with a gap inclined at a predetermined angle with respect to the shaft.

According to a nineteenth aspect of the present invention, the inside of the closed container is formed by a suction chamber in which the carrier fluid flows and is filled, and a discharge chamber in which the carrier fluid is filled after being pressurized by the pump mechanism. It was done.

According to a twentieth aspect of the present invention, the pump device is configured such that the sealed container can be detached from the driving device in a state where the space in contact with the carrier fluid is sealed.

[0033]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 1 to 7 show a refrigerant cycle and a pump device according to a first embodiment of the present invention. FIG. 1 is a schematic diagram of a refrigeration cycle of a regenerative air conditioner to which the pump device is applied, and FIG. 3 is a sectional view taken along line III-III of FIG. 2, FIG. 4 is a sectional view taken along line IV-IV of FIG. 2, FIG. 5 is a sectional view taken along line VV of FIG. 3, and FIG. FIG. 7 is a cross-sectional view corresponding to FIG. 5 for explaining the operation when moving in the direction, and FIG. 7 is a characteristic diagram of the flow rate and the head according to the rotation speed of the pump device. In the figure, reference numeral 1 denotes a refrigerant cycle which is a refrigeration cycle of a heat storage type air conditioner. In this example, an example in which cooling air conditioning by ice storage is performed is shown. Reference numeral 2 denotes a pump device that conveys the liquid refrigerant of the refrigerant cycle 1 to the load side. Reference numeral 3 denotes a check valve which is a backflow prevention means for preventing a backflow of the refrigerant to the discharge side of the pump device 2. The load-side heat exchangers 4 as a plurality of use-side heat exchangers arranged indoors or the like each have a refrigerant. Is connected via a throttle device 4a for adjusting the flow rate of the liquid crystal. Reference numeral 5 denotes a heat source side heat exchanger provided in a heat storage tank 6 for storing a heat storage medium, which condenses a refrigerant and recovers heat of the heat source. In this embodiment, cold heat by ice is used as a heat source. . Note that a pure refrigerant (R407C) having no refrigerating machine oil is used as the refrigerant.

The check valve 3, the throttle device 4a, the load side heat exchanger 4, and the heat source side heat exchanger 5 are connected to the pump device 2 via the refrigerant circulation path 7, and the heat source side heat exchanger 5 A circuit for transferring heat to the side heat exchanger 4 is configured. When a heat source such as cold heat is used, there is almost no difference between the condensing temperature and the evaporating temperature of the refrigerant, so that the conveying force of the refrigerant circulation is smaller than that of a refrigerant cycle using a general compressor (not shown). Since it is small, the pump device 2 can be used, and an energy-saving operation using only the transfer power of the liquid refrigerant can be performed.

Next, the configuration of the pump device 2 will be described. Reference numeral 8 denotes a driving device main body of the driving device for driving the pump device 2 to rotate. The driving device main body 8 includes a motor 9 which is a motor for generating a driving force and a driving magnet 10 directly connected to a rotating shaft 9a. An unnecessary permanent magnet such as an excitation power supply is used for 10. Reference numeral 11 denotes a pump section for increasing the pressure of the liquid refrigerant.
The closed container 12 is made of 2b, and is configured to withstand a pressure of about 5 [MPa]. Then, this closed container 12 is mounted on the bracket 1.
The motor 3 is fixed to the motor 9 via a screw 3 (not shown). The rear container 12b is made of a non-magnetic material such as stainless steel in order to transmit the pressure resistance and the magnetic force of the driving magnet 10 into the closed container 12.

Numeral 14 denotes a vortex type pump mechanism provided inside the closed vessel 12, which increases the pressure in order to convey the liquid refrigerant. The pump 14 comprises a front casing 15a and a rear casing 15b fixed to each other by fitting or the like. It comprises a casing 15 forming the outer shell of the mechanism 14 and a substantially disk-shaped impeller 16 as a pump rotating body rotatably provided between the front casing 15a and the rear casing 15b. And since this pump mechanism 14 is provided in the closed container 12 which can be filled with the liquid refrigerant,
Since it can be configured with a pressure resistance of about 1 [MPa], which is a pressure smaller than that of the sealed container 12, it can be formed even with a resin such as an engineering plastic which is easy to mold, and is much easier to form than when a metal material is cut. And cost reduction can be achieved.

In this example, the casing 15 is made of a polyphenylene sulfide resin and the impeller 16 is made of a polyether ether ketone resin as a plastic resin material having a refrigerant resistance so as not to be deteriorated by the refrigerant. ing. The pump mechanism 14 is arranged and fixed so as to partition the front container 12a and the rear container 12b. In addition, this impeller 1
As an example, when the diameter is about 9 cm and the thickness is about 6 mm, it is possible to produce a liquid having a liquid conveyance force of about 14 liters per minute at a head of 1 [MPa].

Reference numeral 17 denotes a rotary shaft (hereinafter, referred to as a shaft) having a hollow hole 18 extending over the entire length of the shaft. The rotary shaft 17 rotates the impeller 16. The casing 1 is provided by bearings 19 and 20 which are bearing portions provided in the casing 15.
5 is supported rotatably in the radial direction. Also,
The front side container 12a and the rear side container 12b of the closed container 12 divided by the casing 15 by the hollow hole 18 are circulated.

Reference numeral 21 denotes a rotor of the driving device which rotates in the sealed container 12 directly connected to the other shaft of the shaft 17, and is composed of an unnecessary permanent magnet such as an excitation power supply.
2 is provided on the side of the rear side container 12b and is disposed at a position opposite to the driving side magnet 10 with the closed side container 12 interposed therebetween, and is provided so as to be rotated by the rotation of the driving side magnet 10;
And a magnet coupling that transmits torque inside and outside via the. 4, a gap 21a is provided between the rotor 21 and the shaft 17, and a key 17a is provided on the shaft 17 side so as to be connected in the rotational direction, so that the shaft 21 can move within a certain range in the axial direction. Thus, the shaft 17 does not move even if the rotor 21 moves due to the axial position of the drive-side magnet 10 being slightly displaced, so that the impeller 16 is not subjected to a load in the thrust direction of the shaft.

Next, the configuration of the pump mechanism 14 will be described. Reference numeral 22 denotes a plurality of blades formed on the periphery of the impeller 16, which rotate at high speed to pressurize the fluid by a frictional force and convey the fluid. A substantially annular compression chamber 2 is formed so as to be substantially divided by an outer peripheral portion of the impeller 16 and the casing 15 so as to cover and accommodate the blade 22 portion.
3 is formed. In addition, a part of the compression chamber 23 is provided with a partition part 24 that narrows a gap between the casing 15 and the blades 22 of the impeller 16 from other parts to partition the refrigerant inflow side and outflow side.

Reference numeral 25 denotes a pressure equalizing chamber which is a space formed by recessing the casing 15 at the center of the front and rear surfaces of the impeller 16 to form a wide gap between the impeller 16 and the casing 15. Reference numerals 26 denote respective seal portions which partition between the impeller 16 and the casing 15 with a small gap through which the liquid refrigerant passes between the equalizing chamber 25 and the compression chamber 23, and extend from the compression chamber 23 to the equalizing chamber 25. And casing 1
5 is formed so as to be inclined so that the gap between the impeller 16 and the impeller 16 becomes wide. Reference numerals 27 and 28 denote suction ports and discharge ports respectively arranged on both sides of the partition part 24 communicating with the compression chamber 23 provided on the front casing 15a side of the casing 15. The suction ports 27 are hermetically sealed to the closed container 12. Container 12
A suction pipe 29 serving as an inlet of the liquid to be transported is connected to the suction port 29, and the discharge port 28 is defined by the front container 12a side of the closed container 12 and the casing 15, and is provided around the pump mechanism 14 to increase the pressure of the refrigerant. Is opened to the discharge chamber 30 which stores the liquid in a fillable manner.

In FIG. 2, the structures of the suction port 27 and the discharge port 28 are shown at positions vertically separated from each other for easy understanding, but actually, the pressure of the liquid refrigerant is increased efficiently as shown in FIG. Therefore, they are arranged near both sides of the partition 24.
Reference numeral 31 denotes a discharge pipe which is an outlet of a carrier liquid fluid for discharging the liquid refrigerant from the discharge chamber 30 to the outside of the closed container 12, and is welded to the closed container 12.

Next, the lubricating structure of the bearings 19 and 20 by the refrigerant will be described. 32 and 33 are bearings 1
The spiral grooves formed on the inner surfaces of the bearings 19 and 2
The discharge chamber 30 and the pressure equalizing chamber 2 on the front casing 15a side are formed over the entire length, which is a sliding portion with the shaft 17 of the first casing 15a.
5 and the side of the rear side container 12b accommodating the driven side magnet 21 and the pressure equalizing chamber 25 on the rear casing 15b side, and the high-pressure liquid refrigerant flows into the pressure equalizing chamber 25 through the grooves 32 and 33. Thus, the inflow passage of the carrier fluid is formed.
The grooves 32 and 33 have the same effect even if they are provided on the shaft 17 side or on both the bearings 19 and 20 and the shaft 17. However, when the grooves 32 and 33 are provided on the shaft 17 side, the shaft must be thickened for the sake of strength. That is, the bearings 19 and 20 can be processed more easily and can be formed at low cost.

Numeral 34 denotes a pressure equalizing hole formed in the impeller 16 in the pressure equalizing chamber 25. The refrigerant flows through the pressure equalizing hole 34 to further balance the pressure in the pressure equalizing chambers 25 on the front casing 15a side and the rear casing 15b side. In this embodiment, four holes are provided at 90-degree intervals. In addition,
The shape, number, and arrangement of the pressure equalizing holes 34 may be appropriately set according to the capacity of the pump device 2. The grooves 32 and 33 and the pressure equalizing holes 34 constitute pressure equalizing means for equalizing the pressure equalizing chambers 25 on the front and rear surfaces of the impeller 16.

Reference numerals 35 and 36 denote through holes formed at positions corresponding to the sliding portions of the bearings 19 and 20 so as to reach the sliding surfaces of the bearings 19 and 20 and the shaft 17 from the hollow hole 18 of the shaft 17, respectively. The coolant that has flowed into the hollow hole 18 is guided through the through holes 35 and 36 to the sliding surfaces of the bearings 19 and 20 serving as bearings for lubrication. In this example, one coolant is provided in each case. It may be.

Next, characteristics of the vortex pump mechanism 14 will be described. A large number of blades 22 around the periphery of the impeller 16 rotate the annular compression chamber 23 at a high speed to increase the pressure of the fluid by frictional force with the fluid. Although it changes depending on the viscosity, there is almost no difference in performance between the liquid refrigerant for the air conditioner and water, and as shown in the characteristic diagram of FIG. 7, the characteristics of this vortex pump are different from those of the positive displacement pump. The flow rate decreases with increasing head. Further, when the number of revolutions becomes low, the amount of fluid leaking in the compression chamber 23 in the reverse direction increases, and the discharge flow rate decreases.

Next, the operation of the refrigerant cycle 1 will be described. The refrigerant flows from the heat source side heat exchanger 5 to the pump device 2,
In a cycle in which the check valve 3, the expansion device 4a, and the load-side heat exchanger 4 are returned to the heat source-side heat exchanger 5 in this order, the load-side heat exchanger 4 and the expansion device 4a become evaporators, and take away indoor heat. Cooling is performed by evaporating and gasifying the refrigerant. The heat-source-side heat exchanger 5 is a condenser, and by flowing into the condenser and recovering cold from a heat source (heat-stored ice), the vaporized gas refrigerant is condensed, returns to a liquid state, and re-constitutes the liquid again. The cycle of sending to the load side heat exchanger 4 by the pump device 2 is repeated. In other words, since there is a heat source, there is almost no difference between the condensation temperature and the evaporation temperature of the refrigerant. Since there is no need to create a low pressure, energy-saving operation using only the pumping power of the liquid refrigerant by the pump device 2 can be performed.

Although the check valve 3 is not always necessary, in the case of such a cycle of the pump device 2 using the liquid refrigerant, suction from the heat source side heat exchanger 5 (condenser) to the pump device 2 is performed. Has the lowest temperature and the lowest pressure, and therefore has the function of alleviating the accumulation of refrigerant on the condenser side when the pump device 2 is stopped.

Next, the detailed flow operation of the liquid refrigerant will be described. The rotation of the drive-side magnet 10 accompanying the rotation of the motor 9 causes the rotation force to be transmitted across the sealed container 12 to rotate the rotor 21, and the impeller 16, which is a pump rotating body fixed to the shaft 17, interlocks with the casing. Rotate within 15. Since a large number of blades 22 at the periphery rotate the annular compression chamber 23 at high speed to increase the pressure of the fluid by frictional force with the fluid, the fluid flows through the suction pipe 29 from the suction port 27 to the carrier fluid of the refrigerant cycle 1. A certain liquid refrigerant flows into the discharge port 2 on the opposite side which is pressurized and partitioned by the partition section 24.
8 and is discharged into the discharge chamber 30 as a high-pressure liquid refrigerant, and is discharged from the discharge pipe 31 to the refrigerant cycle 1.

Next, the flow of the lubricating liquid refrigerant, which is the flow of the liquid refrigerant in the closed container 12, will be described. The liquid refrigerant discharged into the discharge chamber 30 in the front-side container 12a flows into the rear-side container 12b through the hollow hole 18 of the shaft 17, and also fills the rear-side closed container 12b with the high-pressure liquid refrigerant. The high-pressure liquid refrigerant filled on both sides of the front casing 15a and the rear casing 15b of the casing 15 is supplied to the spiral groove 32 of the bearing 19 from the discharge chamber 30 side and to the bearing 20.
Flows into the spiral groove 33 from the rear container 12b side, and passes through the sliding portion of the bearing portion between the shaft 17 and the bearings 19 and 20 while lubricating. 25, the pressure equalizing chamber 25 is filled with the liquid refrigerant, and the impeller 16 is hard to move back and forth, and further, the liquid flows through the pressure equalizing hole 34 formed in the impeller 16,
Since the pressures in the pressure equalizing chambers 25 before and after the impeller 16 are further balanced and become equal, the impeller 16 is more difficult to move back and forth, and the position with the casing 15 is maintained. Therefore, the impeller 16 which is one of the sliding parts and the casing 1
5 is prevented, and wear is prevented. Also, the high pressure liquid refrigerant having a large degree of supercooling flows reliably in the sliding portion between the shaft 17 and the bearings 19 and 20, and the lubrication and cooling are performed stably without gasifying the liquid refrigerant in contact with the sliding portion.
Wear and seizure are prevented, and the pump device 2 can be improved in reliability.

Then, the high-pressure liquid refrigerant filled in the pressure equalizing chamber 25 finally passes through the gap of the seal portion 26 and is closed.
Flows to the suction side of the compression chamber 23 which is the only low pressure in the
The pressure is increased and flows out to the discharge port 28.

As shown in FIG. 6, a seal portion 26 for sealing between the compression chamber 23 and the pressure equalizing chamber 25 has a larger gap between the impeller 16 and the casing 15 from the compression chamber 23 toward the pressure equalizing chamber 25. For example, when the impeller 16 moves to and comes into contact with one of the seal portions 26b, the one seal portion 26a remains at a high pressure, but the other seal portion 26b has the compression chamber 23. The gap becomes larger, and the communication is established, so that the pressure in the compression chamber 23, that is, a low pressure state in the compression process is established. As a result, as shown by the arrow in FIG. 6, a force for automatically pulling the impeller 16 back to the center is generated, and the impeller 16 is returned to the original position, so that the position of the impeller 16 does not move back and forth between the casings 15. Maintained, and furthermore, the contact between the impeller 16 and the casing 15,
What can prevent wear and improve reliability can be obtained.

The liquid refrigerant flows from the hollow hole 18 in the shaft 17 to the through holes 35 and 36 by centrifugal force, and the liquid refrigerant is further directly supplied to the sliding surfaces of the bearings 19 and 20 as lubrication. Therefore, the high-pressure liquid refrigerant flows more reliably in the sliding portion, and the liquid refrigerant in contact with the sliding portion is stably lubricated and cooled without being gasified, and wear and seizure are prevented. 2 improves the reliability. Further, since the liquid of the carrier fluid flows from one surface side of the casing 15 to the other surface side through the hollow hole 18, the sealed container 12 has a simple configuration and does not require a special space for making a hole. Can be filled with the transport liquid. Although the rotation of the impeller 16 may be a predetermined one, the motor 9 is controlled by an inverter or the like in accordance with the load of the refrigerant cycle, and the rotation is controlled so that the pump device 2 has an optimum conveyance force. You may enable it to convey efficiently. As in this embodiment, the refrigerant circulates in the refrigerant cycle 1 in a liquid state by condensation and a gas state by evaporation, such as Freon or hydrocarbon containing no chlorine, and in the liquid state, the discharge chamber 30 That is why they are stored.

The reason why the vortex pump is used as the refrigerant pump device 2 is that the sliding portion of the pump mechanism 14 has a less slidable condition than the conventional positive displacement pump. The contact between the side surface of the casing 15 and the rotating portion of the shaft 17 and the bearing portions 19 and 20 can be formed with a simple configuration by the wear preventing effect of the sliding portion shown in the above configuration. The tip of the blade 22 and the casing 15 are spaced from each other by a distance of several millimeters [mm] and do not contact each other. It is prevented from contacting with a gap of several tens of microns [μ]. Also,
The rotor 21 is a permanent magnet, and the driving device main body 8 that transmits the rotational force to the rotor 21 is composed of the motor 9 and the driving magnet 10.
And the heat generation in the closed container 12 is small,
Since the influence of heat on the refrigerant is small, energy-saving operation can be performed, and there is also an effect that a simple configuration of the driving device can be obtained.

The state and control of the refrigerant in the pump device 2 will be described. Since mixing of gas into the suction of the refrigerant into the pump device 2 causes a decrease in the transport flow rate, in order to maximize the capacity of the pump device 2, the degree of supercooling of the suction liquid should be ensured. Heat source side heat exchanger 5
It controls the amount of heat transfer on the (condenser) side. In other words, when the suction refrigerant is in a liquid state, the discharge liquid pressurized by the pump device 2 is surely supercooled, and the liquid surface is not formed in the discharge chamber 30. The refrigerant amount and operation control are performed to ensure that the liquid refrigerant is supplied to the suction so that the liquid hardly disappears. As an example of this operation control, in this embodiment, the heat source side heat This is performed by controlling the heat exchange amount of the exchanger 5. Specifically, a device (not shown) for generating bubbles is provided in the heat storage tank 6, and the amount of the bubbles hitting the heat source side heat exchanger 5 is provided. By adjusting the temperature, the amount of cold heat recovered from the ice is adjusted, so that the refrigerant becomes a liquid refrigerant without fail.

As described above, the refrigerant in the discharge chamber 30 becomes a supercooled liquid and does not coexist with the gas. For example, even if the liquid surface exists when the pump device 2 is started, the gas is lost if the supercooled liquid is supplied. The discharge chamber 30 is filled with the liquid refrigerant. Further, for example, even if a small amount of gas enters the suction refrigerant, the discharge liquid is controlled to be a supercooled liquid.
4 is filled with the discharge liquid so as not to affect the lubrication of the sliding portion of the pump mechanism 14.

Embodiment 2 FIG. 8 is a sectional view corresponding to FIG. 3 showing the second embodiment of the present invention. The same or corresponding parts as in the first embodiment are denoted by the same reference numerals, and detailed description is omitted. In the first embodiment, the suction port 27 and the discharge port 28 of the casing 15 are opened on the front side of the casing 15, but as shown in FIG.
And the discharge port 28 may be provided along the rotation direction of the impeller 16. With this configuration, the inflow and outflow of the liquid refrigerant can be performed more smoothly, and the influence of the inflow and outflow in the front-rear direction of the impeller 16 is less likely to occur, that is, twisting is less likely to occur. In this embodiment, the casing 15 has a square shape, and three equalizing holes 34 are provided.

Embodiment 3 FIG. FIG. 9 is a cross-sectional view of a main part of a pump device according to a third embodiment of the present invention. Note that the same or corresponding parts as those in Embodiments 1 and 2 are denoted by the same reference numerals,
Detailed description is omitted. As shown in FIG. 9, reference numeral 37 denotes a relief valve formed inside the pump mechanism 14, which comprises a sphere 38 made of steel or the like and a spring 39. As described above, when an abnormal high-lift operation state occurs, the relief valve 3
A mechanism may be added for the relief 7 from the discharge chamber 30 to the suction side. That is, when the discharge chamber 30 becomes too high with respect to the suction pressure, the spring 39 contracts, and the steel ball 38 opens the valve to communicate from the discharge chamber 30 to the suction side of the pump mechanism 14 which is the suction pipe 29. It is a mechanism to do. By providing the relief valve 37 in this way, it is possible to prevent the operation from becoming too high in the head, and to improve the reliability of the pump device.

Embodiment 4 FIG. FIG. 10 is a plan view of a suction gasification sensor provided in a pump device according to Embodiment 4 of the present invention. The same or corresponding parts as those in the first to third embodiments are denoted by the same reference numerals, and detailed description is omitted.
The suction gasification sensor 40 as shown in FIG. 10 is connected to the suction pipe 29 as in the first embodiment so that air bubbles are not mixed in the suction into the pump section 11 and the lubrication of the sliding section does not occur. And a function of controlling the operation and stop of the pump device 2 when gasification occurs. In the figure, a suction gasification sensor 40 includes a sight glass 41, a light receiving element, and a light emitting element.
2 is comprised. Then, when the inhaled liquid flashes and becomes cloudy, the reflectance of light in the sight glass 41 changes. Therefore, this is detected by the flash sensor 42 and the power of the pump device 2 is turned off. The lubrication may be controlled so that the sliding portion of the pump mechanism 14 can be favorably lubricated, and the reliability of the pump device 2 can be further improved.

Embodiment 5 FIG. FIG. 11 is a longitudinal sectional view of a pump device corresponding to FIG. 2 showing a fifth embodiment of the present invention. The same or corresponding parts as in the first embodiment are denoted by the same reference numerals, and detailed description is omitted. In the first embodiment, the transmission of torque into the closed container 12 is performed by magnetic coupling using the driving magnet 10 and the rotor 21.
As shown in FIG.
May be provided in place of the rotor 43, and a stator 44 for rotating the rotor 43 may be provided outside the closed casing 12 to constitute an electric motor. For example, an AC induction motor is formed by using the rotor 43 as an iron core and the stator 44. May be. In this case, the point that the liquid refrigerant absorbs the heat of the stator 44 is the same as the conventional case, but the lubricating effect of the sliding portion between the other shaft 17 and the bearings 19 and 20 and the impeller 16
The effect similar to that of the first embodiment can be obtained in the prevention of the movement.

Embodiment 6 FIG. In the above embodiment, the pump device 2 is applied to a heat storage type air conditioner as an application example, but may be provided to the air conditioner 1 as shown in FIG. 12 as another application. The same or corresponding parts as in the first embodiment are denoted by the same reference numerals, and detailed description is omitted. An outdoor unit 46 having a compressor (not shown) placed on the roof of a building 45; an indoor heat exchanger 47;
The air conditioner 1 is constituted by the indoor unit 49 constituted by 8, the gas pipe 50, the liquid pipe 51, and the pump device 2. In the air conditioner 1, at the time of heating, gas having a higher temperature than the outdoor unit 46 is sent to the indoor unit 49 through the gas pipe 50. The high-temperature gas is liquefied in the indoor heat exchanger 47 and returns to the outdoor unit 46 through the liquid pipe 51. At this time, in the indoor unit 49 on the lowest floor, in order to send the liquid to the roof, even if the expansion device 48 is fully opened, the low pressure may be too low due to the head loss. At this time, the pumping of the liquid refrigerant in the refrigerant cycle 1 by the compressor by the pump device 2 to increase the pressure of the liquid refrigerant solves this problem, and as a result, the installation height difference of the air conditioner 1 can be increased. Also, application to various refrigeration cycles is possible.

Embodiment 7 In the above-described embodiment, an example of the vortex pump is shown as the pump mechanism 14. However, a rotary pump (not shown) may be used, and the effects of lubricating the bearings 19 and 20 and simplifying the pump mechanism 14 are similarly obtained. . That is, the pump mechanism 14 is compressed by a cylinder (not shown) eccentric from the center of a shaft (axis) 17 directly connected to the rotor 21 of the driving device and an outer peripheral portion of the cylinder so as to cover the cylinder. A casing 15 forming a chamber 23, and a suction port 27 and a discharge port 28 provided in the casing 15 for sucking and discharging a carrier fluid.
And a rotary pump having:

Embodiment 8 FIG. FIG. 13 is a sectional view of a pump device according to Embodiment 8 of the present invention. In the first embodiment, the suction pipe 29 is directly connected to the compression chamber 23. However, in the embodiment shown in FIG.
2 is divided into two chambers by a front casing 15a, one chamber is a suction chamber 52, and the other chamber is a discharge chamber 30. This eliminates the need to insert the suction pipe 29 through the airtight container 12 to the compression chamber 23 and seal it with the discharge chamber 30, thereby simplifying manufacturing. Also,
Since the suction portion 52a to the compression chamber 23 is provided near the lowermost portion of the suction chamber 52, even if gas mixes with the suction liquid during operation, the gas remains in the compression chamber 23 until the liquid in the suction chamber 52 runs out. Without mixing, it is possible to improve the discharge flow rate stability with respect to the suction gasification.

Further, in this embodiment, as shown in FIG. 13, the closed container 12 fixes the front container 12a and the rear container 12b to the center plate 12c, and seals the space that comes in contact with the liquid. It is configured to be assembled. With such a configuration, in the pressure resistance test and the leak test of the sealed container 12, it becomes possible to visually check only the sealed container 12 for a leak test by immersion in water, so that the safety and reliability are improved and the test time is improved. Is also shortened.

FIG. 14 is a sectional view when the shaft 17 is slightly inclined with respect to the casing 15. In this embodiment, the impeller 16 and the shaft 17
A fitting gap 53 is provided at the fitting portion between the first and second members so as to interlock only in the rotation direction. In the vortex pump mechanism, the gap between the impeller 16 and the casing 15 (seal portion 26) has a very narrow clearance on the order of several tens of microns, so that the processing accuracy of the impeller 16 or the casing 15
It is conceivable that the impeller 16 and the casing 15 may interfere with each other due to poor assembly accuracy, or the shaft 17 may be gradually inclined with respect to the casing 15 due to the progress of bearing wear. so,
Since the impeller 16 can be slightly tilted with respect to the shaft 17, even if the shaft 17 is tilted as shown in the figure, the impeller 16 maintains the proper position, and abnormalities due to dimensional interference between the impeller 16 and the casing 15. No pressing load is generated, and the reliability can be improved.

It is also conceivable that the impeller 16 vibrates with a small width in the thrust direction by the provision of the above-mentioned fitting gap 53, causing large damage to the fitting portion. As described above, in the eighth embodiment, a combination of square holes is used instead of torque transmission by a key. This torque transmission method is not limited to the square hole shape, and the same effect can be obtained by using a pentagonal or hexagonal polygonal hole shape, or a method such as spline or serration (not shown).

In the first to seventh embodiments, the pump device 2 is applied to a refrigeration cycle of an air conditioner.
It can be applied to various refrigeration cycles such as freezing and refrigeration equipment, and the same effect can be obtained. In particular, in the case of a refrigeration cycle, it is necessary to efficiently control the capacity, and since the liquid refrigerant has a property of being gasified, the effects of the above-described embodiment such as the lubricating structure of the sliding portion of the pump device 2 are particularly advantageous. The pump device 2 is notable not only for the refrigerating cycle, but also for transporting other liquids that need to be transported, such as water, for example. It can be applied as a fluid pump, and the same effect can be obtained.

In the first to third embodiments, the pressure equalizing holes 3 are used.
4 can be easily constructed by directly drilling the impeller 16 into the impeller 16, but the shaft 17 and the impeller 1 are not shown.
A gap is provided in a part of the shaft stop portion of No. 6, and a hole is formed in a portion of the shaft 17 facing the front and rear pressure equalizing chambers 25 so as to communicate with the hollow hole 18 so as to communicate with each other. Means may be formed.

The dimensions, materials, and shapes of the pump device, such as the sealed container 12, the casing 15, the impeller 16, and the shaft 17, are not limited to those in the above embodiment, but can be changed as appropriate.

In the first embodiment, the driving magnet 1
Although the rotating shaft 9a of the motor 9 is directly connected as a means for rotating the motor 0, a device for rotating the motor 9 or the like is arranged at another place, and the rotation is transmitted by a belt or a gear, and the driving side is rotated. The magnet 10 may be rotated.

In the first embodiment, the shaft 17
While the lubrication between the bearings 19 and 20 is lubricated by both the inflow path by the grooves 32 and 33 and the through holes 35 and 36, the inflow path by the grooves 32 and 33 or
The lubrication effect may be obtained by lubricating either one of the through holes 35 and 36. The lubricating effect is similarly obtained although the performance is slightly lower than in both cases.
3 and the size and quantity of the through holes 35 and 36 and the pump device 2
That can obtain a sufficient effect depending on the ability, application conditions, and the like.

In the first embodiment, the bearings 19 and 20 of the bearing portion are provided separately from the casing 15. However, the casing 15 is made of a material having good wear resistance. It may be provided integrally with the casing 15. Further, although a configuration in which one impeller 16 is disposed in the casing 15 is shown, a plurality of impellers may be used.

In the first embodiment, the closed container 12
To provide pressure resistance to the outside of the container, and to eliminate the need for a large pressure resistance in the pump mechanism 14, thereby making the pump mechanism 14 of the vortex pump use.
Is formed of a plastic resin material, but if the closed container 12 is provided with pressure resistance as described above, the pump mechanism disposed therein may have another configuration, for example, even if it is a rotary pump. Therefore, an effect that a pump mechanism can be easily formed can be obtained.

[0074]

As described above, the refrigerant cycle according to the first invention comprises a heat source side heat exchanger for condensing refrigerant and recovering heat of a heat source, and a pump device for conveying the condensed refrigerant to the load side. In a refrigerant cycle in which a throttle device for adjusting the flow rate of the refrigerant and a load-side heat exchanger that evaporates the refrigerant and supplies heat from the heat source to a load are sequentially connected by piping and conveys the heat, the pump is A pump mechanism provided in a closed vessel of the apparatus and configured to increase the pressure of the refrigerant from the heat source side heat exchanger by rotating a pump rotor, and the refrigerant provided in the pump mechanism and supporting the rotation of the pump rotor. A bearing portion to be lubricated, and a discharge chamber provided around the pump mechanism in the closed vessel and storing the pressurized refrigerant so as to be able to be filled therein, wherein the refrigerant is made of chlorine-free Freon or hydrocarbon. Since the sea urchin the refrigerant cycle was as reserved in the discharge chamber at a liquid state while circulating in the gas state by evaporation the liquid state by condensation, it can be energy saving operation only conveying power of the liquid refrigerant, also,
Since the discharge chamber is provided around the pump mechanism in the closed container, the pressure resistance of the pump mechanism can be reduced and the structure of the pump device can be simplified.

In the refrigerant cycle according to the second aspect of the present invention, the backflow preventing means for preventing the backflow is provided on the discharge side of the pump device, so that the refrigerant pools on the heat source side heat exchanger side when the pump device is stopped. This has the effect of preventing spillage.

According to a third aspect of the present invention, there is provided a pump apparatus having an inlet and an outlet for a carrier fluid, and a closed vessel capable of being filled with the carrier fluid, and a pump rotating body provided in the closed vessel and arranged inside. A pump mechanism that is driven to rotate and pressurizes the carrier fluid guided from the inlet, a rotor of a driving device having a permanent magnet that is directly connected to the pump rotor and rotates in the closed container, and a permanent magnet of the rotor. A driving device main body that transmits a rotational force from the outside to the permanent magnet with the closed container interposed therebetween, and the carrier fluid discharged from the pump mechanism filled the inside of the closed container and was discharged from the outlet, Since the carrier fluid exists around the pump mechanism in the closed container, the pressure resistance of the pump mechanism can be reduced, and the structure of the pump device can be simplified.

According to a fourth aspect of the present invention, there is provided a pump apparatus according to the present invention, wherein a rotational force is transmitted to the permanent magnet of the rotor, which is directly connected to the pump rotating body and rotates in the closed container, and the permanent magnet with the closed container interposed therebetween. The driving device main body includes a motor that generates a driving force, and a driving-side magnet that is directly connected to the motor and that is disposed to face the permanent magnet and the closed container via the closed container and that transmits a rotating force to the permanent magnet. So
There is an effect that energy-saving operation can be performed with less heat generation in the closed container and a drive device having a simple structure can be obtained.

According to a fifth aspect of the present invention, there is provided a pump device wherein the pump mechanism is directly connected to a rotor of the driving device, and is rotatably supported by a bearing portion on a casing constituting an outer shell of the pump mechanism. A hollow hole into which the carrier fluid in the closed vessel flows is provided therein, and the carrier fluid flows from one surface side to the other surface side of the casing through the hollow hole. There is an effect that the carrier fluid can be caused to flow into both sides.

According to a sixth aspect of the present invention, there is provided a pump device, wherein the pump mechanism is directly connected to a rotor of the driving device, and is rotatably supported by a bearing portion on a casing constituting an outer shell of the pump mechanism. A hollow hole through which the carrier fluid in the closed vessel flows is provided therein, and a through hole is formed in the shaft from the hollow hole to the sliding surface of the bearing portion. Since the moving fluid is reliably supplied to the moving surface and lubricated, there is an effect that a material capable of preventing wear can be obtained.

According to a seventh aspect of the present invention, in the pump device, the pump mechanism is provided around a shaft directly connected to a rotor of the driving device, and the blade of the pump rotating body that rotates and covers the blade. As described above, the vortex pump has a casing that forms a compression chamber on the outer periphery of the blade, and a suction port and a discharge port that are provided in the casing and that suck and discharge the carrier fluid. There is an effect that a condition in which conditions are not strict and a pump mechanism can be easily configured can be obtained.

In the pump device according to the present invention, the pump mechanism may include a cylinder eccentric from a center of a shaft directly connected to a rotor of the driving device, and an outer peripheral portion of the cylinder so as to cover the cylinder. The rotary pump has a casing that forms a compression chamber, and a suction port and a discharge port that are provided in the casing and suck and discharge the carrier fluid. There is.

According to a ninth aspect of the present invention, there is provided a pump apparatus wherein the pump mechanism of the vortex pump is a space portion in which a gap with the casing is provided substantially at a substantially central portion of the front and rear surfaces of the pump rotating body. A pressure chamber, an inflow passage through which a part of the carrier fluid in the closed vessel flows into the pressure equalizing chamber from before and after the casing, and the pump rotor between the pressure equalizing chamber and the compression chamber. A seal portion before and after partitioning with a slight gap through which a fluid passes between the casing and the casing, wherein the carrier fluid flowing into the pressure equalizing chamber of the pump rotor from the inflow passage passes through the seal portion, and Since it is made to flow into the compression chamber, there is an effect that a contact between the pump rotating body and the casing can be reduced and wear can be prevented.

According to a tenth aspect of the present invention, there is provided a pump device according to the present invention, wherein the inflow passage of the carrier fluid flowing into the pressure equalizing chamber from the front and rear of the casing is provided between the front and rear of the pump rotor for rotatably supporting the pump rotor. A bearing is provided in each bearing part of the bearing and a groove is provided in the sliding surface of this bearing, so the carrier liquid is reliably supplied from the groove to the sliding surface of the bearing part and lubricated, preventing wear There is an effect that what can be obtained is obtained.

According to the eleventh aspect of the present invention, since the pressure equalizing holes for circulating the carrier fluid in the pressure equalizing chambers on the front and rear surfaces of the pump rotor are provided, the pressure equalizing chambers in the front and rear are further equalized. As a result, the pump rotator is less likely to move in the front-rear direction, and the effect of further reducing contact between the pump rotator and the casing to prevent wear can be obtained.

According to a twelfth aspect of the present invention, since the pressure equalizing hole penetrates through the front and rear surfaces of the pump rotating body, the pressure equalizing hole can be obtained simply and inexpensively.

According to a thirteenth aspect of the present invention, in the pump apparatus, the seal portion before and after the partition between the pump rotating body and the casing with a slight gap through which the carrier fluid passes has the compression chamber side. From the pressure equalizing chamber side, the pressure difference is generated when the pump rotating body moves back and forth, and the pump rotating body is automatically returned to the original position. This has the effect of reducing contact between the body and the casing to prevent wear.

According to the pump device of the present invention, since the pump mechanism is made of resin, there is an effect that the molding is easy and the pump device can be manufactured at low cost.

A pump device according to a fifteenth aspect of the present invention is provided with a discharge chamber in which the carrier fluid is discharged from the pump mechanism in the closed container, and a predetermined pressure is applied from the discharge chamber to the suction port side of the pump mechanism. Since the relief valve which opens at the end is provided, there is an effect that a high head operation can be prevented and the reliability can be improved.

A pump device according to a sixteenth aspect of the present invention is provided with a suction flash detecting means for detecting whether or not air bubbles are generated in the suction liquid in a suction pipe of the closed container which is an inlet of the carrier fluid. Since the operation of the pump device is controlled by the suction flash detection means,
The sliding portion of the pump mechanism can be lubricated favorably, and an effect of further improving reliability can be obtained.

In the pump device according to the present invention, since the carrier fluid is a refrigerant of a refrigeration cycle, there is an effect that a liquid refrigerant of the refrigeration cycle can be efficiently transported.

In the pump apparatus according to the present invention, the pump rotating body is fitted with a gap inclined at a predetermined angle with respect to the shaft, so that the pump rotating body is subject to aging due to initial dimensional errors and wear. In contrast, an abnormal pressing load due to dimensional interference between the impeller and the casing does not occur, and the reliability can be improved.

A pump device according to a nineteenth aspect of the present invention is directed to the pump apparatus, wherein the inside of the closed container is filled with a carrier fluid by flowing in and a discharge chamber is filled after the carrier fluid is pressurized by the pump mechanism. Therefore, there is no need to penetrate the suction pipe to the compression chamber, and the pump mechanism can be manufactured more easily. Further, even if gas is mixed into the suction liquid during operation, no gas is mixed into the compression chamber until the liquid in the suction chamber runs out, so that the discharge flow rate stability against suction gasification can be improved.

In the pump device according to the present invention, the sealed container can be detached from the driving device in a state where the space in contact with the carrier fluid is sealed. In the test, only the closed container can be visually checked for leak inspection by submersion, so that there is an effect that safety and reliability can be improved and the test time can be reduced.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of a refrigeration cycle of a regenerative air conditioner to which a pump device according to a first embodiment of the present invention is applied.

FIG. 2 is a longitudinal sectional view of the pump device according to the first embodiment of the present invention.

FIG. 3 is a sectional view taken along line III-III of FIG. 2;

FIG. 4 is a sectional view taken along line IV-IV of FIG. 2;

FIG. 5 is a sectional view taken along line VV of FIG. 3;

FIG. 6 is a cross-sectional view corresponding to FIG. 5, illustrating an operation when the impeller moves in the axial direction according to the first embodiment of the present invention.

FIG. 7 is a characteristic diagram of a flow rate and a head according to the rotation speed of the pump device according to the first embodiment of the present invention.

FIG. 8 is a cross-sectional view corresponding to FIG. 3 showing the second embodiment of the present invention.

FIG. 9 is a sectional view of a main part of a pump device according to a third embodiment of the present invention.

FIG. 10 is a plan view of a suction gasification sensor provided in a pump device according to Embodiment 4 of the present invention.

FIG. 11 is a sectional view of a pump device according to a fifth embodiment of the present invention, corresponding to FIG. 2;

FIG. 12 is a schematic configuration diagram of a refrigeration cycle of an air conditioner to which a pump device according to a sixth embodiment of the present invention is applied.

FIG. 13 is a sectional view of a pump device according to an eighth embodiment of the present invention, corresponding to FIG. 2;

FIG. 14 is a sectional view of a pump mechanism according to an eighth embodiment of the present invention.

FIG. 15 is a sectional view showing a conventional pump device.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Refrigerant cycle, 2 pump device, 3 check valve (backflow prevention means), 4 load side heat exchanger, 4a expansion device, 5
Heat source side heat exchanger, 6 heat storage tank, 7 refrigerant circulation path, 8
Drive device body, 9 motor, 9a rotating shaft, 10 drive side magnet, 11 pump unit, 12 sealed container, 12a front container, 12b rear container, 13 bracket, 14 pump mechanism, 15 casing, 15a front casing, 15b rear Casing, 16 impeller (rotating pump), 17 shaft, 17a
Key, 18 hollow hole, 19, 20 bearing (bearing part),
21 rotor, 21a gap, 22 blades, 23 compression chamber, 24 partition, 25 pressure equalization chamber (space), 26 seal, 27 suction port, 28 discharge port, 29 suction pipe (inlet), 30 discharge chamber, 31 discharge pipe (outlet), 32, 3
3 groove (inflow passage), 34 pressure equalizing hole, 35, 36 through hole, 37 relief valve, 38 sphere, 39 spring, 40
Inhalation gasification sensor, 41 sight glass, 42 flash sensor, 43 rotor, 44 stator, 4
5 buildings, 46 outdoor units, 47 indoor heat exchangers,
48 throttle device, 49 indoor unit, 50 gas pipe,
51 liquid pipe, 52 suction chamber, 53 fitting gap.

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) // F24F 5/00 102 F24F 5/00 102K (72) Inventor Toshiyuki Nakamura 2-2 Marunouchi, Chiyoda-ku, Tokyo No. 3 Mitsubishi Electric Co., Ltd. (72) Inventor Moriya Miyamoto 2-3-2 Marunouchi, Chiyoda-ku, Tokyo F-term (reference) 3H020 AA01 AA07 BA21 CA00 DA02

Claims (20)

[Claims] 1. A heat source side heat exchanger that condenses a refrigerant to recover heat of a heat source, a pump device that conveys the condensed refrigerant to a load side, a throttling device that adjusts a flow rate of the refrigerant, In a refrigerant cycle in which a load-side heat exchanger that supplies heat from the heat source to a load by evaporating and sequentially transferring the heat through a pipe is provided, the heat source-side heat exchanger provided in the closed vessel of the pump device is provided in the closed vessel of the pump device. A pump mechanism that rotates the pump rotor to raise the pressure of the refrigerant, a bearing portion provided in the pump mechanism and lubricated by the refrigerant that supports the rotation of the pump rotor, and a pump mechanism in the sealed container. A discharge chamber which is provided in the surroundings and stores the pressurized refrigerant so as to be able to fill the refrigerant, wherein the refrigerant is a liquid state by condensation and a gas by evaporation in the refrigerant cycle, such as chlorofluorocarbon or hydrocarbon. A refrigerant cycle device circulating in a state and being stored in the discharge chamber in a liquid state. 2. The refrigerant cycle device according to claim 1, further comprising a backflow prevention means for preventing a backflow on a discharge side of the pump device. 3. A sealed container having an inlet and an outlet for a carrier fluid and capable of being filled with the carrier fluid, and a carrier guided in the inlet by a pump rotating body provided in the closed container and arranged inside the container. A pump mechanism for increasing the pressure of the fluid, a rotor of a driving device having a permanent magnet directly connected to the pump rotating body and rotating in the sealed container, and a permanent magnet externally sandwiching the permanent magnet of the rotor and the sealed container. A pump body for transmitting a rotational force to a magnet, wherein the carrier fluid discharged from the pump mechanism fills the inside of the closed container and is discharged from the outlet. 4. A drive device main body that is directly connected to the pump rotor and rotates in the closed container and transmits a rotational force to the permanent magnet with the closed container interposed therebetween generates a driving force. And a driving magnet that is directly connected to the motor and that is disposed to face the permanent magnet via the closed container and that transmits a rotational force to the permanent magnet. A pump device as described. 5. The carrier fluid in the closed container in a shaft directly connected to a rotor of the driving device and rotatably supported by a bearing in a casing constituting an outer shell of the pump mechanism. 5. A hollow hole into which the carrier fluid flows is provided, and the carrier fluid flows from one surface side of the casing to the other surface side through the hollow hole. Pumping equipment. 6. The carrier fluid in the closed container in a shaft which is directly connected to a rotor of the driving device and is rotatably supported by a bearing in a casing constituting an outer shell of the pump mechanism. The pump according to any one of claims 3 to 5, wherein a hollow hole into which the fluid flows is provided, and a through hole extending from the hollow hole to a sliding surface of the bearing portion is formed in the shaft. apparatus. 7. The pump mechanism is provided around a shaft that is directly connected to a rotor of the driving device, and a rotating blade of the pump rotor is provided on an outer peripheral portion of the blade so as to cover the blade. 7. A vortex pump comprising: a casing that forms a pump; and a suction port and a discharge port provided in the casing for sucking and discharging the carrier fluid. Pumping equipment. 8. The pump mechanism includes: a cylinder eccentric from a center of a shaft directly connected to a rotor of the driving device; a casing forming a compression chamber on an outer peripheral portion of the cylinder so as to cover the cylinder; The pump device according to any one of claims 3 to 6, wherein the pump device is a rotary pump provided in a casing and having a suction port and a discharge port for sucking and discharging the carrier fluid. 9. The pump mechanism of the vortex pump includes a pressure equalizing chamber which is a space portion provided with a wide gap between the casing and a substantially central portion of a front and rear surface of the pump rotating body. An inflow passage through which a part of the carrier fluid in the closed vessel flows into the pressure equalizing chamber, and a slight passage of fluid between the pump rotating body and the casing between the pressure equalizing chamber and the compression chamber. And a seal portion before and after the partition having a gap, wherein the carrier fluid flowing from the inflow passage into the pressure equalizing chamber of the pump rotating body flows through the seal portion to the compression chamber. The pump device according to claim 7, wherein 10. A bearing is provided for each of the inflow passages of the carrier fluid flowing into the pressure equalizing chamber from the front and rear of the casing, at bearing portions before and after a pump rotating body that rotatably supports the pump rotating body, The pump device according to claim 9, wherein a groove is provided on a sliding surface of the bearing. 11. The pump device according to claim 9, wherein a pressure equalizing hole for circulating the carrier fluid in the pressure equalizing chamber on the front and rear surfaces of the pump rotor is provided. 12. The pump device according to claim 11, wherein the pressure equalizing hole is penetrated through front and rear surfaces of the pump rotating body. 13. The seal portion before and after partitioning the pump rotating body and the casing with a small gap through which the carrier fluid passes, from the compression chamber side to the pressure equalization chamber side, respectively. The pump device according to any one of claims 9 to 12, wherein the pump device is inclined to be wider. 14. The pump device according to claim 3, wherein the pump mechanism is formed of a resin. 15. A discharge chamber for discharging the carrier fluid from the pump mechanism in the closed container, and a relief valve that opens at a predetermined pressure from the discharge chamber to a suction port side of the pump mechanism is provided. The pump device according to any one of claims 3 to 14, wherein 16. A suction pipe, which is an inlet of the carrier fluid, of the closed container, which is provided with suction flash detection means for detecting whether or not bubbles are generated in the suction liquid, and which operates the pump device by the suction flash detection means. The pump device according to any one of claims 3 to 15, wherein the pump device is controlled. 17. The pump device according to claim 3, wherein the carrier fluid is a refrigerant of a refrigeration cycle. 18. The pump device according to claim 7, wherein the pump rotating body is fitted with a gap inclined at a predetermined angle with respect to a shaft. 19. The inside of the closed container is formed by a suction chamber filled with a carrier fluid flowing therein and a discharge chamber filled after the carrier fluid is pressurized by the pump mechanism. The pump device according to any one of claims 3 to 18. 20. The pump according to claim 3, wherein the closed container is configured to be detachable from a driving device in a state where a space in contact with a carrier fluid is sealed. apparatus.