JP6846702B2 - Heat pump device - Google Patents

Description

The present invention relates to a heat pump device, and more particularly to a heat pump device suitable for energy saving and low environmental load using all heat sources related thereto in the field of heat utilization technology of renewable energy.

A heat pump generally refers to a technique for transferring heat from a place where the temperature is low to a place where the temperature is high. Some of these technical methods have been known in the past, but the mainstream is a combination of gas compression / expansion and heat exchange, and its application products include refrigerators and refrigerators, air conditioners, and water heaters found in ordinary households. Known as.
This heat pump has a structure in which a low boiling point refrigerant (for example, CFC substitute) circulates as a heat transfer medium inside the medium circulation system.

In this type of heat pump, for example, during heating, a low-temperature liquid refrigerant obtains heat from a low-temperature heat source (a liquid that has been heat-exchanged in the ground) at a place of an evaporator (heat exchanger) and vaporizes. Next, the vaporized refrigerant is pressurized and heated by a compressor. Then, the heated gaseous refrigerant moves to a heat exchanger, where the external water is heat-exchanged to become hot water, which is used for indoor heating.
Then, the refrigerant deprived of heat by heat exchange is liquefied from the gaseous state, depressurized at the expansion valve, and returns to the first evaporator again.
On the other hand, during cooling, the cycle is opposite to that during heating, and external water is heat-exchanged by a heat exchanger to become cold water, which is used for indoor cooling.

FIG. 15 shows a system diagram of a conventionally known steam compression type heat pump device.
In this case, as the low-temperature heat source 001 on the heat collecting side, renewable energy such as outside air 005, solar radiation 004, underground / geothermal 003, and various waste heat 002 are used.
Then, the heat obtained from the low-temperature heat source 001 evaporates and vaporizes the refrigerant RV, which is the working medium, in the evaporator 101 portion.

The vaporized refrigerant (working medium) RV is guided by the compressor 102 to be compressed, and the compressed refrigerant RV is guided to the condenser 103 that dissipates heat to a high-temperature heat source on the heat utilization side at a temperature higher than the heat collection temperature. It is condensed here in a compressed state. Subsequently, the condensed refrigerant RV is guided to the expansion valve 104 to expand and depressurize, and the expanded and decompressed and reduced pressure refrigerant RV is again guided to the above-mentioned evaporator 101.

A heat exchanger 106 is attached to the condenser 103, and the heat energy of the medium RV is taken out through the heat exchanger 106. Reference numeral 105 indicates a heat medium pump, reference numeral 009 indicates heat dissipation taken out by the heat exchanger 106, and reference numeral 107 indicates a heat utilization system that effectively utilizes the heat dissipation 009.

Here, in order to reduce the size of the heat pump device described above, a high-pressure, positive displacement compressor 102 capable of processing a small volumetric flow rate is used as the compressor, and the required weight flow rate of the refrigerant is secured. ing.

On the other hand, in the small reciprocating compressor 130 shown in FIG. 12, when the compressed refrigerant reaches a predetermined pressure, the spring-shaped blow-out valve installed on the upper part of the cylinder is opened to compress the compressed refrigerant 103 ( (See FIG. 15).

Further, the rotary compressor 140 shown in FIG. 13 has a blow-out valve structure similar to that of the small reciprocating positive displacement compressor.

Further, in the scroll type compressor 150 shown in FIG. 14, the refrigerant RV is compressed by the refrigerant compression cylinder portion composed of the swivel scroll and the fixed scroll, and the compressed refrigerant RV is discharged from the discharge hole at the center of the fixed scroll. It is guided to the condenser 103 (see FIG. 15).

Each of the compressors described above is a positive displacement type, and the volume at which the start and end of compression of the refrigerant RV is determined by design, so that the compression ratio of the refrigerant RV is constant. When the compression ratio of the refrigerant RV is constant by the compressor, the heat dissipation temperature is determined by the heat collection temperature.

Heat pump devices equipped with these positive displacement steam compressors often use a low boiling point, high-density refrigerant RV, but the refrigerant RV generally has a large global warming potential, and when it is discharged to the outside world, it warms the world. This is not a preferable state because the conversion will proceed.

Here, FIG. 12 shows a main part of the above-mentioned reciprocating positive displacement compressor 130.
In this reciprocating positive displacement compressor 130, the power generated by the stator 131 and the rotor 132, which are a part of the drive motor, is connected to the rotary shaft 134 supported by the rotary shaft support unit 133 and the rotary shaft 134. It is transmitted to the disk 135, and this disk 135 makes a rotary motion.

The piston rod 136 is connected at a position offset outward along the radial direction from the center of the disk 135, and the end of the piston rod 136 on the opposite side of the connection between the disk 135 and the piston rod 136 (upper end side in FIG. 13). The piston 137 is connected to. Since both connecting ends of the piston rod 136 are of a swing type, the piston 137 moves up and down in the cylinder 138 to realize a compression process of the refrigerant RV which is an operating medium.

On the other hand, in the compression process of the operating medium RV, a sealing portion 139 is provided so that the operating medium RV does not leak from the boundary between the piston 137 and the cylinder 138.

Here, the rotary shaft support portion 133 uses a contact type bearing, and is forcibly lubricated with oil or coated with lubricating grease in order to suppress seizure and fretting due to heat generation. Things are being used.

The contact type bearing referred to here is a rolling bearing in which a plurality of spherical or cylindrical bearings made of ceramic or iron-based material are provided on a plurality of sliding surfaces, or a slide that forms an oil film on a flat or pad-shaped surface. Refers to bearings.

Further, an electric motor cooling unit 130A is provided on the outer periphery of the stator 131, and forced liquid cooling using a chiller or the like or forced air cooling using a blower or the like is performed.

Next, an outline of the rotary type positive displacement compressor 140 is shown in FIG.
In FIG. 13, in the rotary positive displacement compressor 140, the power generated by the stator 141 and the rotor 142, which are a part of the drive motor, is supported by the rotary shaft 144 and the rotary shaft 144, and the rotary shaft 144. It is transmitted to a roller 145 connected to it, whereby the roller 145 performs a rotary motion.

Here, since the roller 145 of the drive motor portion in the compressor 140 is eccentrically connected from the center of the rotating shaft 144, the wall surface of the stationary portion 146 in which the roller 145 is stored has a wide gap and a narrow gap. Will be mixed.

Then, in the narrow portion of the gap, the roller 145 is compressed by pressing the working medium RV against the stationary portion 146, whereby the compression portion (compression space) 147 is formed. At the same time, the working medium RV is not compressed in the portion where the gap is wide, and an uncompressed portion 148 is formed. Then, under such a state, the compression process of the working medium RV is realized by forming the compression unit (compression space) 147.

In the compression process of the working medium RV, although not shown in the figure, a leak sealing mechanism for sealing the leakage of the working medium RV from the boundary between the roller 145 and the stationary portion 146 is separately installed.

Here, the rotating shaft support portion 143 uses a contact type bearing as in the case of the reciprocating type of FIG. 12 described above, and is forcibly lubricated with oil in order to suppress seizure and fretting due to heat generation. Or a product coated with lubricating grease is used.

Further, as for the contact type bearing referred to here, as in the case of the reciprocating type of FIG. 12 described above, a rolling bearing in which a spherical or cylindrical bearing using a ceramic or iron-based material is provided on a plurality of sliding surfaces. Or, it refers to a slide bearing that forms an oil film on a flat or pad-shaped surface.

Further, the stator 141 is also provided with an electric motor cooling unit 149 on the outer periphery thereof, and is subjected to forced liquid cooling using a chiller or the like, or forced air cooling using a blower or the like.

FIG. 14 shows a part of the basic configuration of the scroll type positive displacement compressor 150.
In this scroll type positive displacement compressor 150, the power generated by the stator 151 and the rotor 152 which are a part of the drive electric motor is connected to the rotary shaft 154 supported by the rotary shaft support portion 153 and the rotary shaft 154 and the rotary shaft 154. It is transmitted to the swirling spiral 156, which causes the swirling spiral 156 to make a circular motion around the fixed swirl 157.

Here, since the fixed spiral 157 is fixed, it is relatively oscillating, and the space between the swirling spiral 156 and the fixed spiral 157 becomes a compression portion, whereby the compression process of the working medium RV is realized. Will be done.

Further, between the swirl spiral 156 and the fixed spiral 157, there is a mechanical contact portion to suppress leakage of the working medium, and a lubricating oil is used or wear resistance is used to suppress wear of the contact portion. It is in a state where a property coating or the like is applied.

The rotary shaft support portion 153 uses a contact type bearing, and is forcibly lubricated with oil or coated with lubricating grease in order to suppress seizure and fretting due to heat generation. Has been done.

Here, the contact type bearing is a rolling bearing in which a plurality of spherical or cylindrical bearings made of ceramic or iron-based material are provided on a plurality of sliding surfaces, or an oil film is formed on a flat or pad-shaped surface. A slide bearing.

Further, an electric motor cooling unit 155 is provided on the outer periphery of the stator 151 so that forced liquid cooling using a chiller or the like or forced air cooling using a blower or the like is performed.

The following Patent Documents 1 and 2 are known as known examples of the above-mentioned compressor and a refrigerating apparatus using the compressor.
Of these, Patent Document 1 (Japanese Patent Application Laid-Open No. 2013-122331) describes a refrigerating apparatus provided with a refrigerant compression mechanism, and Patent Document 2 (Patent Publication No. 2809346) describes a compressor for a refrigerator. , Each is disclosed.

Japanese Unexamined Patent Publication No. 2013-122331 Patent Gazette No. 2809346

In each of the conventionally known heat pump devices of the steam compression type described above, in each of the compressors described above, the compression ratio of the refrigerant RV is a constant volume type, the compression ratio of the refrigerant RV is constant, and heat is dissipated when the heat collection temperature is determined. When the temperature is fixed and, as a result, the heat collection temperature fluctuates, there is a disadvantage that heat of a desired temperature level cannot be obtained.

Further, in each of the above-mentioned steam compression type heat pump devices, in order to obtain heat at a desired temperature level regardless of the temperature of the heat source, a compressor capable of changing the compression ratio is required in operation. There are requirements, and the system, which uses electricity and power obtained from the energy obtained by burning fossil fuels, has the problem of global warming due to carbon dioxide emissions.

A heat pump device that uses renewable energy or waste heat as a low-temperature heat source to improve the temperature level and dissipate heat to use it is different from a heat pump device that collects heat at the temperature of an environment such as normal outside air, and has the same temperature level. It has the feature that the compression power required to obtain the heat of the above can be reduced and the amount of carbon dioxide gas emission can be reduced.

However, in this type of heat pump device, the refrigerant that is the operating medium, especially the operating medium RV that transmits the heat taken in, often has a high global warming potential at present, and when it is discharged to the environment, it warms the world. It has a defect that contributes to global warming.

On the other hand, new working refrigerants RVs with a small global warming potential are attracting attention, but these new working media RVs are concentrated in the low-pressure and high-temperature regions, and are required as working media in the practical capacity range of positive displacement compressors. There were few suitable high-density ones, and there was a limit to their use in positive displacement compressors.

Further, the rotary shaft support portion 133 in the reciprocating positive displacement compressor 130 shown in FIG. 12, the rotary shaft support portion 143 in the rotary positive displacement compressor 140 shown in FIG. 13, and the scroll type positive displacement compression shown in FIG. Since contact-type bearings are used in all of the rotating shaft support portions 153 of the machine 150, there is an inconvenience in these conventional techniques that there is a mechanical loss in each of the contact portions and the system efficiency is lowered. there were.

Further, since the rotating shaft support portions 133, 143, and 153 of the above-mentioned positive displacement compressors 130, 140, and 150 are all in contact with each other and rotate, they are easily worn or damaged in the long term. There was an inconvenience, and there was a need for regular inspections and replacement of the rotating shaft support itself. This has the disadvantage that it takes time and effort to maintain the compressor body in terms of maintenance cost and continuous operation because it requires periodic disassembly work.

Furthermore, since the rotating shaft support portions 133, 143, and 153 use lubricating oil and lubricating grease, these supply devices and control / monitoring / protection devices for monitoring the supply status are provided. This is necessary, and there is a problem that the device configuration becomes complicated. Especially when forcibly supplying lubricating oil, a refueling pump (and a drainage pump in some cases) is required, and depending on the temperature environment, a heat exchanger to maintain the viscosity of the lubricating oil is also required, which consumes power. There was an inconvenience that it led to an increase in.

In particular, in this case, the grease is also very sensitive to changes in viscosity due to the temperature environment, which causes a problem of shortening the life of the rotating shaft support portions 133, 143, 153.
At the same time, regular maintenance such as regular replacement of lubricating oil and refilling of grease has also been a problem. When grease is used, it is difficult to monitor it for protection. Therefore, there is a disadvantage that the safety factor is set to be fairly high, regular replacement work is required, and the frequency of regular maintenance is particularly high.

In addition, the above-mentioned lubricating oil and grease may be mixed into the working medium side with the passage of time (aging), which lowers the purity of the working medium, lowers the performance of the working medium, and lowers the system efficiency. It was also the cause.

In addition, by providing a sealing part to prevent the lubricating oil and grease from being mixed into the working medium, the cost increases due to the increase in the number of parts, and the sealing part also has a finite life, so periodic inspections and periodic inspections are performed. There was also a problem that regular maintenance of the compressor body was required, such as replacement work.

Further, in the scroll type positive displacement compressor 150, there is a mechanical contact portion between the swirl spiral 156 and the fixed spiral 157 in order to suppress leakage of the working medium, and in order to suppress wear of the contact portion, Lubricating oil is used, but there is also the inconvenience that this lubricating oil affects the deterioration of the purity of the working medium.

Further, the sealing portion 139 in the reciprocating positive displacement compressor 130, the sealing portion of the rotary positive displacement compressor 140, and the working medium between the swirling swirl 156 and the fixed swirl 157 in the scrolling positive displacement compressor 150. In all cases, such as when a coating is applied to the mechanical contact part in order to suppress leakage, the sealing part is in contact with the rocking part and the stationary part, causing slight daily wear. Therefore, materials around the sealing portion such as contamination are scattered and mixed with the working refrigerant, which causes a problem of purity deterioration as described above.

Furthermore, the stator and rotor that make up the drive motor are parasitic on iron loss and copper loss, which generate heat depending on the rotation speed and load, leading to a reduction in the life of the motor.
Therefore, in the above, the electric motor cooling units 130A, 149, and 155 are forcibly cooled by using a chiller or a blower, but all of them require power and have an inconvenience that power consumption increases.

Further, in each of the above compressors, the device configuration is complicated, the control and monitoring / protection functions are complicated, and even in the continuous cooling operation, in each of the above methods, the rotor to be cooled most is desired. There is a disadvantage that the 132, 142, 152 and the rotating shafts 134, 144, 154 cannot be effectively cooled without increasing the power consumption.
(Purpose of Invention)

An object of the present invention is to provide a heat pump device capable of continuous operation for a long period of time by improving the inconvenience in the above-mentioned conventional example, particularly aiming at energy saving and durability improvement.

In order to achieve the above object, the heat pump device according to the present invention has an evaporator, a compressor, a condenser, and an expansion valve sequentially installed in the medium circulation path, and is used for a medium circulating in the medium circulation path. It is a heat pump device having a structure that uses renewable energy and outside air as a low-temperature heat source, and has a configuration in which a turbo compressor is provided as the compressor. Then, in the process of being on the flow path of the circulation medium on the upstream side of the suction portion of the circulation medium in the impeller provided with the turbo compressor until the circulation medium is sucked into the impeller. A conical guide mechanism for suppressing the separation of the flow of the circulating medium is provided, and a smoothing guide mechanism for smoothing the flow of the circulating medium is provided on the outer periphery of the stator of the drive motor mounted in the turbo compressor. It is characterized by being deployed.

Further, as the refrigerant circulating in the medium circulation path, a low-pressure refrigerant having a value in which the ozone depletion potential and the global warming potential are remarkably small is used.
Further, the turbo compressor is characterized in that its heat insulating efficiency is set to a high value in a wide operating range and is a distributed type having a miniaturized energy-saving structure.

Thereby, in the present invention, the turbo compressor can obtain a wide range of working medium flow rate and compression ratio while maintaining high heat insulation efficiency by variously changing the rotation speed.
Therefore, the vapor compression type heat pump device equipped with a turbo compressor having this characteristic can obtain a wide range of temperature levels and a wide amount of energy for heat collection in which the temperature fluctuates over a wide range.

In addition, since the turbo compressor can have a significantly higher rotation speed than the positive displacement compressor, it is possible to obtain a large weight flow rate by using a low-pressure, low-density operating medium within the operating range of the heat pump device. It becomes.

Recently, new working refrigerants with a small global warming potential have been attracting attention, but as mentioned above, these new working media have low vapor pressure at low pressure, resulting in low density and could not be used in positive displacement compressors, but turbo. It can be utilized by adopting a compressor.

Further, the turbo compressor in the present invention has an impeller, a diffuser, and a spiral ring for performing compression work, and the drive motor for driving the impeller is supported by a non-contact rotating shaft support portion. It has a structure with a shaft.

In this case, in the flow of the working medium, the opposite side of the rotating shaft to which the impeller is attached is provided on the upstream side, and the working medium is smoothed without peeling and supplied to the suction port of the impeller. The flow path is configured to flow both outside the stator of the drive motor and inside the drive motor and then merge at the suction port of the steam impeller, while having no fluid sealing portion.

Therefore, according to the above configuration, the contact type rotary shaft support portion unlike the conventional positive displacement compressor becomes unnecessary, and lubricating oil and lubricating grease are not used. Therefore, efficiency is reduced due to mechanical loss of the contact part, efficiency is reduced due to mixing of lubricating oil or lubricating grease and working medium, periodic replacement and maintenance of the rotating shaft support and lubricating oil, equipment configuration, and control / monitoring protection functions are complicated. , The problem of increased electricity consumption is solved.

Further, according to the present invention, the working medium is smoothed without peeling and the suction port of the impeller is supplied, which leads to stabilization of the pressure at the suction port of the impeller and improves the heat insulation efficiency as a turbo compressor. Can be made to.

That is, the heat insulation efficiency of a turbo compressor is generally determined by the amount of compression work with respect to the temperature difference between the inlet and outlet of the compressor. In the flow of the working medium, a static pressure part in which pressure is applied and a dynamic pressure part in which pressure is converted into kinetic energy are mixed. By performing the above smoothing, the kinetic energy of the dynamic pressure portion can be recovered in pressure, and all the working media at the impeller inlet can be regarded as the static pressure portion.

Flowing the working medium both outside and inside the drive motor also leads to cooling of the entire motor. This does not require forced cooling from the outside because it flows inside and outside the drive motor only by the suction force of the impeller of the turbo compressor. In other words, external devices such as chillers and blowers are no longer required, and the problems of device configuration, complicated control / monitoring protection functions, and increased electricity consumption are solved. Further, the cooling effect of the rotor and the rotating shaft, which is most important in cooling the drive motor, is improved, and the problem of reduced efficiency of the drive motor can be solved.

Since the working medium that has passed through the inside of the drive compressor is configured to merge with the working medium that flows outside the drive motor at the suction port of the impeller, the fluid sealing part is not required, and the parts by the sealing part are used. It is possible to solve the problems of contamination and purity deterioration due to increase in points, leakage of working medium, and wear. Since the entire flow rate can be sent to the impeller, the working medium can carry the total amount of heat input from the heat source, and further improvement in system efficiency can be expected.

As described above, the present invention has a structure having an evaporator, a compressor, a condenser, and an expansion valve sequentially installed in the medium circulation path, and using renewable energy, outside air, or the like as a low-temperature heat source for the circulation medium. Since this heat pump device is equipped with a turbo compressor as the compressor, the turbo compressor functions effectively, energy saving and durability improvement of the entire device can be achieved, and for a long period of time. It is possible to obtain an excellent heat pump device that has never existed before and enables continuous operation.

It is an overall block diagram which shows the embodiment of the heat pump device which concerns on this invention. It is sectional drawing which shows the turbo compressor which forms the main part of the heat pump apparatus disclosed in FIG. It is a diagram which shows the characteristic (temperature-pressure characteristic) of the circulating refrigerant used in the heat pump apparatus disclosed in FIG. FIG. 5 is a diagram showing the relationship between the pressure ratio and the flow rate, which are the actual working characteristics of the circulating refrigerant used in the heat pump device disclosed in FIG. 2. It is schematic cross-sectional view which shows another example of the turbo compressor mounted on the heat pump apparatus disclosed in FIG. It is a refrigerant flow state explanatory diagram which shows the flow state of the circulating refrigerant in a turbo compressor at the time of operation of a heat pump apparatus. FIG. 6 is an external view showing an example of a smoothing guide mechanism that constitutes a part of the heat pump device disclosed in FIG. FIG. 6 is an external view showing another example of the smoothing guide mechanism that constitutes a part of the heat pump device disclosed in FIG. It is sectional drawing which shows the specific example of the turbo compressor disclosed in FIG. It is sectional drawing which shows the modification of the turbo compressor disclosed in FIG. It is explanatory drawing which shows the flow state in the refrigerant discharge part in the refrigerant discharge part of the turbo compressor disclosed in FIG. Another example of the turbo compressor disclosed in FIG. 2 is an explanatory diagram showing a schematic configuration of a reciprocating positive displacement compressor and an example of its operation. It is explanatory drawing which shows an example of the schematic structure and operation of the rotary type positive displacement compressor in another example of the turbo compressor disclosed in FIG. It is explanatory drawing which shows the schematic structure of the scroll type positive displacement compressor in another example of the turbo compressor disclosed in FIG. It is an overall block diagram which shows the conventional example of a heat pump apparatus.

[First Embodiment]
Hereinafter, the first embodiment of the heat pump device according to the present invention will be described with reference to the drawings.
FIG. 1 is a block diagram showing a system including a heat pump device according to the present invention. In FIG. 1, the heat pump device includes an evaporator 8, a compressor 9, a condenser 11, and an expansion valve 12 which are sequentially installed on the medium circulation path BR.
Then, as the low-temperature heat source 001 for the medium circulating in the medium circulation path BR, in the present embodiment, the structure is such that renewable energy, outside air, or the like is used.
Of these, as the compressor 9, a turbo compressor is used in the present embodiment.

Further, as the medium (refrigerant) B circulating in the medium circulation path BR, in the present embodiment, a low-pressure medium having an extremely small ozone depletion potential and global warming potential is used in the sense of selecting an earth-friendly refrigerant. ing

Here, in the present embodiment, the turbo compressor 9 has a structure in which the heat insulating efficiency is set to a high value in a wide operating range, and a miniaturized distributed structure having an energy saving structure is used. There is. FIG. 2 shows an example of a specific structure of the turbo compressor 9.

Renewable energy such as facility waste heat 002, geothermal heat 003, solar radiation 004, or outside air heat 005, which is a low-temperature heat source 001, is collected by the evaporator 8 as shown in FIG. The refrigerant B, which is the working medium, evaporates and flows into the turbo compressor 9.
Then, the refrigerant vapor is guided to the blade 17 of the turbo compressor 9 which is driven at high speed by the motor unit (driving electric mechanism unit) 8 in the turbo compressor 9, is compressed here, and is discharged from the turbo compressor 9. , It is guided to the condenser 11, where it heats the heat medium, radiates and condenses itself, and sends it to the expansion valve 12. The expansion valve 12 expands and depressurizes the refrigerant B, and returns to the above-mentioned evaporator 8. A heat pump cycle is formed in this process.

The heat obtained by the above heat dissipation is circulated on the heat medium by the heat medium pump 13 and radiated through the heat exchanger 14, and is used for heating air conditioning, hot water supply, etc. and other various devices by the heat utilization system 15. Used.

Here, in the heat pump device equipped with the turbo compressor 9, as described above, a low-pressure medium having a significantly small ozone depletion potential and global warming potential is used as the circulating refrigerant.

Since the turbo compressor 9 can increase the rotation speed to about 80,000 rotations as compared with the positive displacement compressor at 1,000 rotations per minute, the density is low at low pressure in the operating range of the heat pump device. It is possible to obtain a large weight flow rate using the working medium.

As shown in the saturated steam diagram of the refrigerant in FIG. 3, the refrigerants (“C001HFC32” and “C002HFC134a”) used in general air conditioners and car air conditioners have global warming potentials (GWP) of “677” and “1300”, respectively. Although large, new working refrigerants (low pressure mediums) such as next-generation refrigerant HFO / 1234ze (E) C003, next-generation refrigerant HFO / 1234ze (Z) C004, and next-generation refrigerant HFO / 1233zd (E) C005 are global warming. The value of the coefficient is extremely small, 1 or less and 1, 1 respectively.

These refrigerants are concentrated in the low-pressure high-temperature medium region, and the turbo compressor 9 capable of transporting a large volume flow rate by high-speed rotation can compress the refrigerant, and a heat pump device that does not contribute to global warming can be formed.

FIG. 4 shows the operating characteristics of the turbo compressor 9 used in the heat pump device described above. As shown in FIG. 4, by changing the rotation speed to 75 [%] to 150 [%] (D005 to D002) of the design point, the heat insulation efficiency D007 of 90 [%] or more of the maximum value is maintained. A heat pump is formed in which the working medium flow rate is in the range of 50 [%] to 125 [%] of the design point D001, and a compression ratio of 1.25 to 3.0 can be obtained.

As a result, in addition to making the heat insulation efficiency of the turbo compressor 9 a high value in a wide flow rate range and a compressor operating range, it is possible to achieve that it can be used as an energy-saving distributed device by downsizing.

FIG. 5 shows another specific example of the turbo compressor.
The turbo compressor 10 shown in FIG. 5 is a schematic cross-sectional view of a turbo compressor main body having a magnetic bearing on a rotating shaft support portion in a vertical cross section as viewed from the front direction.
The basic function of this turbo compressor 10 is almost the same as that of the turbo compressor 9 of FIG. 2 described above, but the configurations and combinations forming the inside are diversified according to the application, and FIG. 5 and the following It is not necessarily limited to what is described in.

In FIG. 5, the turbo compressor 10 has a stator 52, a rotor 54, a rotating shaft 55, magnetic bearings 56, 57, 58, 59, and a fluid sealing portion 68 in a housing 53. It includes a stored drive motor unit 50. Further, the turbo compressor 10 includes an impeller 63 and a compression mechanism section 51 in which the diffuser 65 is housed in the spiral ring 64.
Each of the magnetic bearings 56 to 59 is configured so that the entire rotating body can be floated and rotated in an ideal state by a magnetic force, and a mechanical contact portion is provided between the rotating body and the stationary body. It has a structure that does not have any. Each part will be described below.

[Drive motor section]
The drive electric motor unit 50 is a rotational power unit for causing the above-mentioned compression mechanism unit 51 to perform compression work by rotation. As the rotational power, a force that moves in the rotational direction is generated from the magnetic field and the current generated in the stator 52 and the rotor 54, and the rotor 54 starts a rotational movement. The rotation speed of the rotor 54 is determined by the voltage and frequency applied to the stator 52.

The rotor 54 is provided with a rotating shaft 55. The rotating shaft 55 is connected to the inner hole portion of the rotor 54, and even if the inner hole portion of the rotor 54 is deformed in the centrifugal direction due to centrifugal force during rotation, the rotating shaft 55 is still between the rotating shaft 55 and the rotating shaft 55. They are connected so that no gap is generated and the connection phases of each are not shifted.
Further, the rotating shaft 55 is equipped with an axial ring 60 for holding an axial load, which will be described later.

[Magnetic bearing (radial bearing)]
The rotating shaft 55 provided with the rotor 50 and the axial ring 60 is provided with radial magnetic bearings 56 and 57 at both ends thereof. Each of the radial magnetic bearings 56 and 57 has an electromagnet structure on the fixed side that does not rotate. A magnetic field is generated between each of the radial bearings 56 and 57 and the rotor 54, and the rotor 54 floats due to the magnetic force. A silicon steel plate is provided on the rotating shaft 55 around each magnetic bearing portion. Each of the radial bearings 56 and 57 receives a static load and a dynamic load acting in the vertical direction of the rotating shaft 55, and functions as a rotating shaft support portion so that the entire rotating body can stably rotate.

Axial bearings 58 and 59 are arranged around the axial ring 60 described above. Each of the axial bearings 58 and 59 receives the axial load because an aerodynamic thrust is generated as an axial load in the direction of the rotating shaft when the impeller 63 connected to the rotating shaft 55 performs the compression work. , The entire rotating body has the function of maintaining the correct magnetic levitation position. The axial bearings 58 and 59 also have an electromagnet structure like the radial bearings 56 and 57 described above.

Touchdown bearings 61 and 62 are arranged around both ends of the rotating shaft 55. Each touchdown bearing 61, 62 is provided for emergency use, usually has no cage, uses a non-lubricated rolling bearing, and has a rotating shaft 55 and a rotating shaft during magnetic levitation and rotation. It is completely non-contact with all rotating bodies.

The magnetic bearings 56 and 57 use some electricity to generate a magnetic force, but when the power supply is cut off, the rotating shaft 55 cannot be levitated. Further, if an emergency situation such as over-rotation or overload occurs during normal rotation operation and the control range of the magnetic bearing is exceeded, there is a risk that the rotor 54 comes into contact with the stationary body. Only used as a temporary auxiliary bearing in such emergencies.
Since the rotation is stopped in such a situation, the purpose is to safely protect the rotating body until the rotation is stopped.

The touchdown bearings 61 and 62 are not limited to rolling bearings, and other methods may be used as long as they are non-lubricating and have a low coefficient of friction. For example, a plain bearing having a coating having a low friction coefficient and a seizure resistance may be used.

Although not shown, each of the above radial bearings and axial bearings has a built-in pulse sensor and displacement sensor, and feeds back signals from each sensor to perform optimum control of floating and rotational states.

[Cooling mechanism]
The entire rotating body and the stationary parts around the rotating body are housed in the housing 53. The housing 53 is structurally designed so as not to resonate with the rotating body and peripheral devices, and is also provided with a cooling mechanism for cooling the stator 52.

[Compression mechanism]
An impeller 63 is attached to the rotating shaft 55. The impeller 63 rotates by transmitting rotational power by the rotating shaft 55. The impeller 63 is covered with a spiral ring 64, and a diffuser 65 is provided between the discharge side of the impeller 63 and the inlet of the spiral ring 64.

The impeller 63 rotated by the rotating shaft 55 sucks the operating medium B from the operating medium suction port P016, and compresses the operating medium while the operating medium passes through the rotor blades provided on the impeller 63.
There is a gap called chip clearance at the inner interface between the rotor blade of the impeller 63 and the spiral ring 64, and when the working medium passes through the rotor blade of the impeller 63, leakage from this gap is caused by the compressor. It is desirable to make this gap as small as possible because it leads to a decrease in heat insulation efficiency, but it is possible to optimize this gap by applying feedback control to the floating position in the axial direction on each of the above axial bearings.

The working medium B that has passed through the impeller 63 and is compressed passes through the diffuser 65 after being discharged from the impeller 63. The fluid velocity of the working medium B compressed by the impeller 63 is increasing, and the pressure is in a state where the static pressure portion and the dynamic pressure portion are mixed. The diffuser 65 aims to recover the pressure of the dynamic pressure portion converted into kinetic energy by decelerating the working medium having a high fluid velocity discharged from the impeller 63. After that, the pressure-recovered working medium passes through the spiral ring 64 and is discharged from the working medium discharge port P017.

[Fluid sealing mechanism]
A fluid sealing mechanism 67 is provided between the discharge portion of the impeller 63 and the drive motor in order to suppress leakage of the working medium B from the compression mechanism portion 51 to the drive motor portion 50.

In the present embodiment, a configuration including each magnetic bearing 56, 57, 58, 59 as a non-contact type rotary shaft support mechanism has been illustrated, but the present invention is not particularly limited to this, and the non-contact type rotary shaft supports the rotary shaft. Other configurations may be used to support. For example, a fluid bearing using gas, gas, or the like may be used.

(Effect of the first embodiment)
As described above, the turbo compressor 10 includes each magnetic bearing 56 to 59 as a non-contact type rotary shaft support mechanism, and does not use lubricating oil or lubricating grease. Therefore, the mechanical loss can be reduced to zero and the mechanical efficiency of the turbo compressor 10 can be improved. Further, the lubricating oil and the lubricating grease are not mixed into the working medium B, and the deterioration of the purity of the working medium B is suppressed, whereby the system efficiency can be improved.

Further, bearing replacement, lubricating oil replacement, grease filling, etc. are not required, and maintenance can be made free. In addition, a lubricating oil supply pump and an oil drainage pump are no longer required, which can reduce electricity consumption and eliminate the complexity of equipment configuration and control / monitoring protection functions. Further, the feedback control of the magnetic levitation position enables optimum control of the gap in the chip clearance portion, and can improve the heat insulation efficiency of the compressor.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS. 6 to 8.
Here, the same reference numerals are used for the same components as those in the first embodiment described above.
FIG. 6 shows a turbo compressor 200 incorporated in the second embodiment.
The turbo compressor 200 includes a conical guide mechanism 203 that has a magnetic bearing on a rotating shaft support portion and suppresses separation of the flow of the working medium, and a smoothing guide mechanism (smoothing mechanism) 68 that smoothes the flow. And have. FIG. 6 is a schematic cross-sectional view of the turbo compressor 200 in a vertical cross section viewed from the front direction.
In FIG. 6, Q016 indicates an operating medium suction port, and Q017 indicates an operating medium discharge port.

The turbo compressor 200 has substantially the same configuration as the first embodiment described above as a basic configuration. Then, in the flow path of the operating medium B, since the flow flows from the opposite direction to the first embodiment, that is, from the drive motor side, the mounting directions of the impeller 63 and the spiral ring 64 are opposite to each other. There is.
A smoothing guide mechanism 68 is installed on the outside of the stator 52, and a conical guide mechanism 203 is installed near the rotation shaft 55 on the opposite side of the place where the impeller 63 is arranged.
Therefore, as shown by the arrow in FIG. 6, the working medium B is sucked from the working medium suction port Q016 on the drive motor side, passes through the surface of the conical guide mechanism 203 and the smoothing guide mechanism 68 as a flow path, and the blades. It is supplied to the car 63. Each part will be described below.

[Conical guide mechanism]
When the operating medium B is sucked from the drive motor side, the shape is not necessarily smooth due to the shape of the drive motor portion. Rather, it has a flat shape in the direction perpendicular to the flow direction of the working medium B due to the ease of mechanical manufacturing and various constraint conditions. A conical guide mechanism 203 is provided so that the working medium B sucked from the working medium suction port Q016 flows to the downstream side without peeling of the flow, and the secondary flow caused by the peeling is prevented.

[Smoothing guide mechanism]
Next, the smoothing guide mechanism 68 will be described.
The working medium B that has passed through the conical guide mechanism 203 without peeling is provided on the outside of the stator 52 as a housing, and as described above, the working medium B becomes static pressure before the suction of the impeller 63. It passes through the smoothing guide mechanism 68 as a flow path.

FIG. 7 shows an example of the shape of the smoothing guide mechanism 68 described above for smoothing the working medium B. The smoothing guide mechanism 68 includes a plurality of uniform fins 68a along the central axis on the circumference of the flow path, and the working medium B flows through the space between the fins 68a as the flow path to smooth the flow. It becomes possible to change.

FIG. 8 shows yet another example of the shape of the other smoothing guide mechanism 69 for smoothing the working medium B. The smoothing guide mechanism 69 is provided with uniform honeycombs 69a on the circumference of the flow path, and the working medium B flows as a flow path in each honeycomb 69a to enable smoothing of the flow.

In the second embodiment, the case where the conical guide mechanism 203 is provided as a shape to prevent the flow from peeling off, and the fins 68a and the honeycomb 69a are provided as shapes to smooth the flow, but the present invention is not necessarily limited to this. Other shapes may be used as long as they do not have the effect of smoothing the flow.
Other configurations and their operations are the same as those in the first embodiment described above.

(Effect of the second embodiment)
As described above, in the second embodiment, the turbo compressor 200 includes magnetic bearings 56 to 59 as a non-contact type rotary shaft support mechanism, and is in the middle of the flow of the operating medium B. A conical guide mechanism 203 and a flow smoothing guide mechanism 68 are provided on the upstream side of the impeller 63. The conical guide mechanism 203 prevents the flow from peeling off when sucking the working medium B, and solves the loss problem due to the occurrence of the secondary flow. The smoothing guide mechanism 68 smoothes the flow up to the front of the inlet of the impeller 63 and recovers the kinetic energy of the dynamic pressure portion, thereby contributing to the improvement of the heat insulation efficiency of the compressor. Therefore, each component functions effectively in these, and the above-mentioned object can be sufficiently achieved.

Further, since the smoothing guide mechanism 68 is provided on the outside of the stator 52, a cooling effect of the stator 52 is expected as a result, which contributes to improvement of motor efficiency, reliability and life. All of these functions are provided inside the turbo compressor, which simplifies the machine and makes it easier to maintain as a self-function that does not require an external device, compared to similar compressors that were conventionally installed externally. Has a great effect.

[Third Embodiment]
Next, the third embodiment will be described with reference to FIGS. 9 to 10.
First, in FIG. 9, reference numeral 300 indicates a turbo compressor. The turbo compressor 300 is provided with a magnetic bearing on the rotating shaft support portion, and further includes a conical guide mechanism 303 that suppresses the separation of the flow of the working medium, and a smoothing guide mechanism 318 that smoothes the flow. The conical guide mechanism 303 is provided with a through hole 319, and the rotating shaft 305 is provided with a ejection nozzle 320.
The turbo compressor 300 in FIG. 9 shows a schematic cross-sectional view in a vertical cross section seen from the front direction thereof. Further, in FIG. 9, reference numeral R016 indicates an operating medium suction port, and reference numeral R017 indicates an operating medium discharge port.

The turbo compressor 300 is formed as a basic configuration substantially the same as the turbo compressor 200 in the second embodiment described above.

The working medium B sucked from the working medium suction port R016 has two systems, a flow path that flows along the surface of the conical guide mechanism 303 and a flow path that flows through the through hole 319 provided in the conical guide mechanism 303. The flow is distributed to.
Further, a ejection nozzle 320 is provided in the rotating shaft 305, and the working medium B flowing through the through hole 319 enters the ejecting nozzle 320 in the rotating shaft 305 in a non-contact manner with a gap.

The ejection nozzle 320 has a hole (not shown) so as to be discharged to the outside of the rotary shaft 305 on the front side of the rotor 304 attached to the rotary shaft 305, and the working refrigerant that has entered the ejection nozzle 320 from the hole. B is discharged and further flows in the air gap 321 which is a gap between the stator 302 and the rotor 304.

FIG. 10 shows a modification of the turbo compressor 300 disclosed in FIG. 9, in which the position of the hole for discharging the working refrigerant B from the ejection nozzle 360 provided in the rotating shaft 355 is located behind the rotor 304. The working medium B does not flow through the air gap 321 but mainly flows through a through hole (not shown) provided in the central shaft portion of the rotating shaft 355.

In the third embodiment, the ejection nozzles 320 and 320A illustrated in FIGS. 9 and 10 may be provided at the same time.
Other configurations and their operations are the same as in the case of the second embodiment shown in FIG. 6 described above.

[Effect of Third Embodiment]
As described above, the turbo compressor 300 that has been revitalized is provided with magnetic bearings 306, 307, 308, and 309 as non-contact type rotary shaft support mechanisms, and in the flow of the working medium B, A conical guide mechanism 303 and a smoothing guide mechanism 318 are provided on the upstream side of the impeller 313. A part of the working refrigerant B sucked from the working refrigerant suction port R016 flows into the through hole 319 formed in the input portion of the conical guide mechanism 303, and passes through the ejection nozzle 320A provided in the rotating shaft 355. By flowing through the air gap 321 which is the gap between the stator 302 and the rotor 304, the heat generated by the iron loss and the copper loss of the stator 302 and the rotor 304 can be cooled. In particular, cooling the heat generated by the rotor 304 has been a major problem in terms of reducing the reliability and life of the drive motor and the efficiency of the motor, but this configuration solves the problem.

Further, depending on the application, it may be more effective to cool the rotating shaft 305, and the configuration illustrated in FIG. 10 (see the rotating shaft 355) is also effective in that case. All of these functions are provided inside the turbo compressor 300, and compared to similar compressors that were conventionally installed outside, the machine is simplified and self-functions that do not require external installation, resulting in cost reduction and maintainability. It has a great effect.

[Fourth Embodiment]
Next, a fourth embodiment according to the present invention will be described with reference to FIG.
FIG. 11 shows a schematic cross-sectional view of the turbo compressor 400 in a vertical cross section seen from the front direction of the periphery of the impeller inlet 413.

The basic configuration of the turbo compressor 400 is almost the same as that of the third embodiment described above. In this case, the working medium B flowing through the smoothing guide mechanism 418 flows toward the impeller inlet 413A after passing through the smoothing guide mechanism 418. Further, the working medium B that has cooled the rotating body in the drive motor and flows through the ejection nozzle has a gap 414 on the surface of the rotating shaft 455 as a flow path, and flows through the gap 414 toward the impeller inlet 413A. I will go. The working medium B flowing through the smoothing guide mechanism 418 and the working medium B flowing through the ejection nozzle are configured to meet at the impeller inlet 413A.
Other configurations and their operations are the same as in the case of the third embodiment described above.

[Effect of Fourth Embodiment]
As described above, in the turbo compressor 400, in the turbo compressor 400, the operating medium B flowing through the smoothing guide mechanism 418 and the operating medium B flowing through the ejection nozzle are the impeller inlets. Since it is configured to merge at 413A, it is possible to supply the entire flow rate flowing in the system to the impeller 413. This makes it possible for the working medium B to carry the total amount of heat input from the heat source, which can contribute to system efficiency.
Further, by using the gap 414 on the surface of the rotating shaft 455 as the flow path for the operating medium B flowing through the ejection nozzle, the fluid sealing mechanism becomes unnecessary, the number of parts can be reduced, and maintenance can be made free. Become. The fact that the fluid sealing mechanism is unnecessary means that foreign substances such as contamination generated from the fluid sealing mechanism are not mixed into the working medium, maintenance such as replacement of the working medium is not required, and efficiency can be improved. ..

The heat pump device according to the present invention has an evaporator, a compressor, a condenser, and an expansion valve sequentially installed in the medium circulation path as described above, and has renewable energy, outside air, etc. as a low-temperature heat source for the circulation medium. Since the heat pump that uses the above is equipped with a turbo compressor as a compressor, the turbo compressor can function effectively to save energy and improve the durability of the entire device, and can be used continuously for a long period of time. It is possible, especially when collecting heat over a wide range, and it is possible to obtain energy with a wide range of temperature levels and heat quantities corresponding to this, and therefore, not only for home use but also for each heating and cooling and hot water supply for a wide area such as factories It can be used effectively and its application range is wide.

1 Low temperature heat source 8 Evaporator 9, 10, 200, 300, 300A, 400 Turbo compressor 11 Condenser 12 Expansion valve 13 Heat medium pump 14 Heat exchanger 15 Heat utilization system 17, 63, 313, 413 Impeller (compressor) Tsubasa)
18 Drive motor unit (drive electric mechanism)
25,55 Rotating shaft 63,313,413 Impeller 67 Fluid sealing mechanism 68,318,418 Smoothing guide mechanism 203,303 Conical guide mechanism BR Medium circulation path B Operating medium (circulation medium)

Claims (4)

A heat pump having an evaporator, a compressor, a condenser, and an expansion valve sequentially installed in the medium circulation path, and using renewable energy or outside air as a low-temperature heat source for the circulation medium circulating in the medium circulation path. It ’s a device,
Equipped with a turbo compressor as the compressor,
On the flow path of the circulation medium on the upstream side of the suction portion of the circulation medium in the impeller provided with the turbo compressor.
In the process until the circulation medium is sucked into the impeller, a conical guide mechanism for suppressing the separation of the flow of the circulation medium is provided, and a smoothing guide mechanism for smoothing the flow of the circulation medium is provided. A heat pump device characterized by being deployed on the outer periphery of the stator of a drive motor installed in a turbo compressor. In the heat pump device according to claim 1,
Supporting portion of the rotational shaft for rotation power transmission of the drive motor, equipped with a non-lubricated and non-contact of the support mechanism,
In all operating processes including the compression process when the impeller is stationary and rotating, when the circulation medium is filled in the turbo compressor including the flow path or passes through the flow, the circulation medium is supplied to the circulation medium. A heat pump device characterized in that the deterioration of the purity of the circulation medium due to the mixing of foreign matter is suppressed and the mechanical friction loss of the support portion of the rotating shaft is suppressed. In the heat pump device according to claim 1 or 2.
Wherein the conical guide mechanism, a through hole is formed for the circulation medium distribution,
Via the through hole, by which the circulating medium is supplied to the inside of the drive motor, a heat pump apparatus which is characterized in that a structure in which the rotor and its peripheral heating portion of the drive motor is cooled. In the heat pump device according to claim 3,
Wherein the circulating medium supplied to the inside of through holes the driving motor, through the gap of the rotary shaft and its adjacent stationary component for a rotary power transmission of the drive motor, the suction portion of the impeller merges with the circulation medium flowing not through the flow to and the through hole towards, a structure in which the total flow rate of the circulating medium is supplied to the impeller, thereby, the rotary shaft, the vane A heat pump device characterized in that a fluid sealing mechanism is not required for a car or the stationary component.

Images