JP7650248B2 - Heat Pump System - Google Patents

Description

The present invention relates to a heat pump system.

Patent Document 1 describes an adsorption heat pump that includes an evaporator, an adsorber, and a heat storage reactor, in which the heat storage reactor stores heat and dissipates heat equal to or greater than the latent heat of vaporization of the heat medium to the adsorber, and regenerates the adsorber by applying heat equal to or greater than the regeneration temperature.

Electric heat pumps are also known. Hybrid systems that combine an adsorption heat pump with an electric heat pump are also known.

JP 2014-40959 A

In a conventional hybrid system, as shown in FIG. 11, an evaporator of an adsorption heat pump (AHP) and an evaporator of an electric heat pump (EHP) are connected in series in a cold water circulation system.

In addition, adsorption heat pumps have the problem that their output drops significantly at low temperatures, so in practical use, electric heat pumps are used as a backup for adsorption heat pumps. However, this simply increases costs.

The present invention was made in consideration of the above circumstances, and aims to reduce the power consumption of an electric heat pump with a simple configuration when the cold heat output of an adsorption heat pump is insufficient.

The heat pump system according to the present invention is a heat pump system including an adsorption heat pump and an electric heat pump. The adsorption heat pump includes a first evaporator, an adsorption mechanism including a plurality of adsorbers configured to adsorb the fluid evaporated by the first evaporator, a condenser configured to condense the fluid desorbed from the adsorption mechanism, and a load to which cold generated by the first evaporator is supplied. The electric heat pump includes a compressor configured to generate compressed refrigerant, an expansion valve configured to expand the refrigerant, and a second evaporator configured to evaporate the fluid using the compressed refrigerant and supply the refrigerant to the expansion valve. The adsorption mechanism is further configured to adsorb the fluid evaporated by the second evaporator. The first evaporator is configured to generate cold from the expanded refrigerant and supply the refrigerant to the compressor. The electric heat pump shares the evaporator with the electric heat pump.

In the heat pump system according to the present invention, the first evaporator is used as the evaporator of the electric heat pump, which is configured to generate cold heat from the expanded refrigerant and supply the refrigerant to the compressor. When the electric heat pump generates cold heat, the second evaporator evaporates the fluid using the refrigerant compressed by the compressor and supplies the refrigerant to the expansion valve. At this time, the adsorption mechanism of the adsorption heat pump adsorbs the fluid evaporated in the second evaporator. In this way, with a simple configuration, it is possible to reduce the power consumption of the electric heat pump when the cold heat output of the adsorption heat pump is insufficient.

The condenser according to the present invention may be further configured to condense the fluid evaporated in the second evaporator.

The second evaporator according to the present invention may be a plurality of evaporators that are arranged in series with the compressor and evaporate the fluid using the compressed refrigerant, and the evaporator closer to the compressor may be configured to supply the evaporated fluid to the condenser, and the evaporator farther from the compressor may be configured to supply the evaporated fluid to the adsorption mechanism.

The fluid may be water and the refrigerant may be fluorocarbon gas.

The present invention provides a heat pump system that has a simple configuration and can reduce the power consumption of an electric heat pump when the cold heat output of an adsorption heat pump is insufficient.

1 is a schematic diagram showing a configuration example of a heat pump system according to a first embodiment of the present invention. FIG. 4 is a diagram for explaining the operation of a high-efficiency mode in the heat pump system of the first embodiment of the present invention. FIG. 4 is a contour diagram showing a scatter diagram of the equilibrium adsorption amount of the adsorbent versus the adsorber temperature and the exhaust heat temperature. 1 is a graph showing the relationship between the actual power consumption of a compressor, the environmental temperature, and the cold temperature in an electric heat pump. FIG. 2 is a diagram for explaining operation in an AHP only mode in the heat pump system of the first embodiment of the present invention. FIG. 4 is a diagram for explaining the operation of the heat pump system of the first embodiment of the present invention in a parallel drive mode. FIG. 2 is a diagram for explaining the operation of the heat pump system according to the first embodiment of the present invention in an EHP only mode. FIG. 4 is a contour diagram showing a scatter diagram of the equilibrium adsorption amount of the adsorbent versus the adsorber temperature and the exhaust heat temperature. 5 is a flowchart showing a mode switching process performed by the control device. FIG. 11 is a diagram for explaining the operation of a high-efficiency mode in a heat pump system according to a second embodiment of the present invention. FIG. 1 is a schematic diagram showing the configuration of a heat pump system according to the prior art.

The following describes in detail an embodiment of the present invention with reference to the drawings.

(Overview of the embodiment of the present invention)
Adsorption heat pumps can be excellent heat pumps with very low power consumption when there is sufficient exhaust heat and the outside temperature is below a threshold. However, there is an issue that when the exhaust heat temperature becomes low or the environmental temperature reaches a threshold above which adsorption can be performed, the output at low temperatures drops significantly. For this reason, in practical use, an electric heat pump is often installed alongside the adsorption heat pump as a backup, which increases costs.

This is for the following reason. The output of an adsorption heat pump is determined by the adsorbent temperature, the desired cooling temperature, and the properties of the adsorbent, but no matter what kind of adsorbent is used, the lower the cooling temperature is and the higher the adsorbent temperature is, the lower the adsorption capacity is and the lower the performance is.

It is known that commonly used materials such as silica gel generate cold below 10°C, and that the cold drops significantly when the ambient temperature exceeds 35°C. For this reason, an electric heat pump is often installed alongside the adsorption heat pump as a backup, which simply increases costs.

In an embodiment of the present invention, an adsorption heat pump and an electric heat pump are integrated to share the piping of the condenser, evaporator, and heat transport system. In addition, when the output of the adsorption heat pump is insufficient to meet the required cold heat output, the output of the adsorption heat pump is used to assist the electric heat pump, thereby significantly improving the COP (Coefficient of Performance) of the electric heat pump.

Specifically, the heat pump system includes an electric heat pump in addition to an adsorption heat pump, and the cold energy from the adsorption heat pump is provided to the condenser of the electric heat pump, or the cold energy at the ambient temperature generated by the adsorption heat pump is provided to the condenser of the electric heat pump.

More specifically, by integrating the evaporator of the electric heat pump with the evaporator of the adsorption heat pump, it is possible to provide the cold energy of the adsorption heat pump to the condenser of the electric heat pump, or to provide the cold energy at the ambient temperature generated by the adsorption heat pump to the condenser of the electric heat pump.

In addition, the condenser of the electric heat pump is integrated with the second evaporator of the adsorption heat pump, and the heat generated by the electric heat pump that should be discarded outside is discharged outside by the condenser of the adsorption heat pump through piping inside the adsorption heat pump.

In addition, when the output of the adsorption heat pump is smaller than the required cold heat output due to reasons such as high outside air temperature or low exhaust heat temperature, the connection of the pipes to the adsorber can be switched so that water vapor can be adsorbed from the second evaporator to the adsorber.

(Configuration of the heat pump system according to the first embodiment)
A heat pump system according to a first embodiment of the present invention will be described with reference to Figures 1 to 9. In this embodiment, a heat pump system using an adsorption heat pump that uses silica gel as a physical adsorbent of the adsorber and water vapor (water) as a fluid supplied to the adsorber, and an electric heat pump that uses fluorocarbon gas as a refrigerant will be described in detail as an example.

As shown in FIG. 1, the heat pump system 100 of this embodiment is an adsorption heat pump that includes an adsorption mechanism 10 consisting of a first adsorption device 11 and a second adsorption device 12 configured to adsorb a fluid (water vapor), a first evaporator 21, a condenser 30 that condenses the fluid discharged from the first adsorption device 11 and the second adsorption device 12, and a load 40.

The first evaporator 21 is connected to the first adsorption device 11 and the second adsorption device 12 so as to be able to vaporize water and supply the fluid produced by the vaporization, that is, water vapor. Specifically, one end of a flow pipe 75 having a valve V1, which is a flow control valve, is connected to the first evaporator 21.

As described above, the first evaporator 21 removes the heat of vaporization by vaporizing the fluid, and generates cold energy equivalent to the heat of vaporization of water vapor. The first evaporator 21 is thermally connected to a load 40, such as an air conditioner outdoor unit, which is an example of a cold energy demand, via heat exchange pipes 85 and 86 through which circulating water circulates, making it possible to effectively utilize the cold energy.

The first adsorber 11 is configured to receive water vapor from the first evaporator 21, adsorb and hold the water vapor, and desorb and release the adsorbed water vapor to the condenser 30. Specifically, the first adsorber 11 is connected to one end of a flow pipe 74 having a valve V5 and one end of a flow pipe 77 having a valve V7.

The second adsorber 12 is configured to receive water vapor from the first evaporator 21, adsorb and retain the water vapor, and desorb and release the adsorbed water vapor. Specifically, the second adsorber 12 is connected to one end of a flow pipe 73 having a valve V4 and one end of a flow pipe 76 having a valve V6.

The condenser 30 is connected so that water vapor can be supplied from the first adsorption device 11 and the second adsorption device 12, and condenses the water vapor supplied from the first adsorption device 11 and the second adsorption device 12. Specifically, the condenser 30 is connected to one end of a circulation pipe 76 having a valve V6 and one end of a circulation pipe 77 having a valve V7.

The condenser 30 is also connected to the second evaporator 22 via a flow pipe 71 having a valve V3, and condenses the water vapor supplied from the second evaporator 22.

The condenser 30 is connected to the first evaporator 21 and the second evaporator 22 by a circulation pipe (not shown) having a pump. The water condensed in the condenser 30 is supplied to the first evaporator 21 and the second evaporator 22 through the circulation pipe.

As shown in FIG. 1 above, the heat pump system 100 is an electric heat pump that includes a compressor 50 configured to generate compressed refrigerant, an expansion valve 60 configured to expand the refrigerant, and a second evaporator 22.

The second evaporator 22 functions as a condenser configured to condense the compressed refrigerant and supply it to the expansion valve 60. The second evaporator 22 also uses the compressed refrigerant to evaporate a fluid and supply it to the condenser 30. Specifically, one end of a flow pipe 71 having a valve V3 is connected to the second evaporator 22.

The second evaporator 22 is connected to the compressor 50 and the expansion valve 60 so as to be able to supply the refrigerant, freon gas. Specifically, one end of each of the flow pipes 81 and 82 is connected to the second evaporator 22.

The first evaporator 21 is also used as an evaporator for an electric heat pump that is configured to generate cold heat from the expanded refrigerant and supply the refrigerant to the compressor 50.

The first evaporator 21 is connected to the compressor 50 and the expansion valve 60 so as to be able to supply the refrigerant, freon gas. Specifically, one end of each of the flow pipes 83 and 84 is connected to the first evaporator 21.

The control device 90 is a control means that is responsible for overall control of the heat pump system 100, and is electrically connected to the valves V1 to V7, the compressor 50, the load 40, and the external heat source, and is configured to control the valves, heat source, and heat exchanger to control the use of cold energy.

Specifically, the control device 90 is connected to an environmental temperature sensor 92 that detects the environmental temperature, an exhaust heat temperature sensor 94 that detects the exhaust heat temperature, and a load side sensor 96 that detects load side information including the required cold heat output, the load side indoor temperature, and the circulating cold water temperature. Based on the environmental temperature, the exhaust heat temperature, the required cold heat output, the load side indoor temperature, and the circulating cold water temperature, the control device 90 controls to switch between an AHP alone mode in which the adsorption heat pump is driven alone, a high efficiency mode in which the electric heat pump is driven alone with high efficiency, a parallel drive mode in which the adsorption heat pump and the electric heat pump are driven in parallel, and an EHP alone mode in which the electric heat pump is driven alone. The AHP alone mode is an example of the first mode, the high efficiency mode is an example of the second mode, and the parallel drive mode is an example of the third mode.

Here we'll explain each mode.

In the high efficiency mode, as shown in FIG. 2, the adsorption mechanism 10 is controlled to supply cold energy to the second evaporator 22, which functions as a condenser for the electric heat pump.

Figure 2 shows valve operation in high efficiency mode, with dotted valves indicating valves in an open state and white valves indicating valves in a closed state. The same is true for Figures 5, 6, 7, and 10. Also, in the example of Figure 2, the first adsorber 11 is an adsorber that is regenerated using exhaust heat, and the second adsorber 12 is an adsorber that is cooled to the ambient temperature.

Specifically, when the compressor 50 is driven to generate cold energy as an electric heat pump, valves V2 and V4 are opened, water vapor is supplied from the second evaporator 22 to the second adsorption device 12 via the circulation pipes 71, 72, and 73, and the water vapor is adsorbed in the second adsorption device 12. This allows cold energy to be supplied from the adsorption heat pump to the second evaporator 22, which functions as a condenser for the electric heat pump.

In addition, valve V7 is opened, and the water vapor desorbed from the first adsorption device 11 is supplied to the condenser 30 via the flow pipe 77, and the water vapor is condensed in the condenser 30.

The first adsorber 11 and the second adsorber 12 are alternately operated like a normal adsorption heat pipe. When the first adsorber 11 or the second adsorber 12, cooled to the ambient temperature, is connected to the second evaporator 22 via the circulation pipes 73 or 74 and the circulation pipes 71 and 72, the second evaporator 22 is cooled, and the second evaporator 22, which functions as a condenser for the electric heat pump, is cooled to the cold heat generation temperature of the adsorption heat pump, thereby reducing the power of the compressor 50 of the electric heat pump.

To demonstrate the efficiency advantages of the high-efficiency mode, Fig. 3 (A) and (B) show scatter plots of the equilibrium adsorption amount versus adsorber temperature (which depends on the ambient temperature) and exhaust heat temperature for an adsorber using RD silica gel, for two cold generation temperatures of 10°C and 20°C. When the ambient temperature rises or the exhaust heat temperature falls, there are many areas where the adsorption amount is below 0 at a cold generation temperature of 10°C, but as the cold generation temperature increases to 20°C, it can be seen that the area where an adsorption amount can be obtained expands.

For example, when the exhaust heat temperature is 80°C and the ambient temperature is 40°C, the output of the adsorption heat pump will be 0 at a cold heat generation temperature of 10°C, making air conditioning with the adsorption heat pump impossible. In this case, if we consider switching to a mode in which the condensation heat of the electric heat pump is cooled, for example, the adsorption amount will be 0.07 at a cold heat generation temperature of 20°C, and sufficient output will be obtained. Let's consider the effect of applying this cold heat to the condenser of an electric heat pump.

Figure 4 shows the relationship between the actual compressor power consumption in an electric heat pump, the ambient temperature, and the cold temperature. If it is assumed that the ambient temperature in an electric heat pump can be lowered by using the cold heat from an adsorption heat pump, and that the ambient temperature can be lowered by about 20°C from 40°C under the above conditions, it is possible to significantly reduce the compressor power consumption Qcomp. For example, if the ambient temperature is lowered by about 20°C from 40°C, the compressor power consumption Qcomp can be reduced by 33%.

At this time, the cold output from the electric heat map, if ideal operation is achieved, will be the cold output from the adsorption heat pump QAHP minus the compressor power consumption Qcomp. The power consumption Qcon of an adsorption heat pump equipped with a water-spraying condenser is about 1/30 of the cold output QAHP. When considering a large steam-transporting adsorption heat pump, excluding the power consumed by accessories such as the air valves used to drive the valves, the power consumption is dominated by the condenser's water-spraying pump and fan power, and approximately 1/30 of the power required for the amount of cold is required. If we assume that this is 1/30, then the calculation is

As shown in FIG. 7, when the same capacity is operated in EHP only mode (a mode used when exhaust heat cannot be supplied at all to meet the demand for cold heat),

The effect of improvement is also significant when viewed from the perspective of electricity COP.

Next, the AHP only mode will be described. This AHP only mode is used when there is sufficient exhaust heat. In the AHP only mode, as shown in FIG. 5, the compressor 50 is not driven, valves V1 and V4 are opened, and water vapor is supplied from the first evaporator 21 to the second adsorber 12 via the flow pipes 72, 73, and 75, and the second adsorber 12 performs an adsorption operation of the water vapor. In addition, valve V7 is opened, and water vapor desorbed from the first adsorber 11 is supplied to the condenser 30 via the flow pipe 77, and the condenser 30 performs a condensation operation of the water vapor.

Then, the first suction device 11 and the second suction device 12 are alternately switched to perform the suction and desorption operations.

If we calculate the electricity COP in the same way using the assumptions made so far, we get

It becomes.

In the parallel drive mode, as shown in FIG. 6, when the compressor 50 is driven to generate cold heat as an electric heat pump, the valve V3 is opened, water vapor is supplied from the second evaporator 22, which functions as a condenser of the electric heat pump, to the condenser 30 via the flow pipe 71, and the condenser 30 performs a condensation operation of the water vapor. In addition, the valves V1 and V4 are opened, water vapor is supplied from the first evaporator 21 to the second adsorption device 12 via the flow pipes 72, 73, and 75, and the second adsorption device 12 performs an adsorption operation of the water vapor.

In addition, valve V7 is opened, and the water vapor desorbed from the first adsorption device 11 is supplied to the condenser 30 via the flow pipe 77, and the water vapor is condensed in the condenser 30.

Then, the first adsorption device 11 and the second adsorption device 12 are alternately switched to operate as a normal adsorption heat pipe to supply cold heat.

Parallel drive mode is used in situations where the demand for cooling is high, there is sufficient exhaust heat, and output from the electric heat pump is necessary even when the adsorption heat pump is operating at rated capacity. In this mode, the power COP is the average value according to the operating ratio of each.

When there is sufficient exhaust heat, during operation in the parallel drive mode of FIG. 6, after adsorption from the first evaporator 21 is completed in the adsorption heat pump, the operation mode of FIG. 2 can be switched to and adsorption from the second evaporator 22 can be performed, thereby achieving both highly efficient operation of the electric heat pump and operation of the adsorption heat pump.

Next, the EHP only mode will be described. In the EHP only mode, as shown in FIG. 5, the compressor 50 is driven to generate cold heat as an electric heat pump. At this time, the valve V3 is opened, and water vapor is supplied from the second evaporator 22, which functions as a condenser for the electric heat pump, to the condenser 30 via the flow pipe 71, and the water vapor is condensed in the condenser 30.

Next, the efficiency of each mode will be explained. As an example, when the ambient temperature is 30°C and the exhaust heat temperature is 85°C, the adsorption amount difference at a cold heat generation temperature of 10°C is approximately 0.05 g/g, as shown in FIG. 8(A). On the other hand, the adsorption amount difference at a cold heat generation temperature of 20°C is 0.15 g/g, as shown in FIG. 8(B). Therefore, consider a case where the adsorption heat pump adsorbs up to 0.05 g/g at a cold heat generation temperature of 10°C, and then adsorbs up to 0.15 g/g at a cold heat generation temperature of 20°C as an assist for the second evaporator 22 that functions as a condenser for the electric heat pump.

The amount of heat required when an adsorption heat pump operates independently to adsorb up to 0.05 g/g is the sum of the sensible heat of the adsorber and the latent heat of the adsorber. If the thermal COP at this time is assumed to be 0.5, the thermal efficiency when an electric heat pump is used in combination should take into account the increase in latent heat from 0.05 g/g to 0.15 g/g.

In this case, the power consumption is the same as in the high-efficiency mode of Figure 2, so the power COP and thermal COP are as follows:

In AHP only mode, power COP=30 and thermal COP=0.5.
In the high efficiency mode, the power COP=3.28 and the thermal COP=0.7.
In EHP only mode, the power COP=1.53.

In high-efficiency mode, a higher power COP can be obtained compared to operation in EHP-only mode. Since the power COP is lower compared to AHP-only mode, it is necessary to consider the balance between cold heat demand and exhaust heat when selecting the mode. Also, in high-efficiency mode, the heat COP is high due to the large difference in adsorption amount for one adsorption/desorption switch (three times in this calculation example). Therefore, in terms of heat consumption, it is also characterized by a significant decrease in terms of cold heat.

Next, we will explain in detail how the control device 90 switches modes.

First, the adsorption amount difference with respect to the operating temperatures (cold heat generation temperature, ambient temperature, exhaust heat temperature) of the adsorption heat pump is expressed as a three-dimensional map showing the adsorption isotherm of the adsorbent of the adsorption mechanism 10, as shown in Figure 3 above. Note that in Figure 3 above, it is expressed in two dimensions due to space limitations.

The environmental temperature and exhaust heat temperature are determined using values acquired by the environmental temperature sensor 92 and the exhaust heat temperature sensor 94. Here, the cold heat generation temperature is determined from the required cold heat output acquired by the load side sensor 96, the indoor temperature on the load side, and the cold water temperature of the circulating water. The adsorption amount difference Δq is obtained from the aforementioned map.

The output of the adsorption heat pump is determined by the adsorption amount difference Δq, the latent heat of vaporization (a known value), and the adsorption cycle time. Like the adsorption amount, the cycle time is a value that varies depending on the operating temperature of the adsorption heat pump and the design of the adsorber, so it is assumed that the cycle time is similarly obtained in advance using a three-dimensional map.

If the calculated output of the adsorption heat pump is greater than the required cold output, the system will switch to AHP only mode to supply cold. This is the most efficient operating mode.

Next, if the output of the adsorption heat pump is less than the required cold output, it switches to either the parallel drive mode or the high efficiency mode, whichever consumes less power, to supply cold.

The power consumption of the electric heat pump in parallel drive mode is calculated as follows. First, the power consumption of the electric heat pump is calculated using a map determined from the required cold heat output and the ambient temperature. Alternatively, the output of the electric heat pump = required cold heat output - output of the adsorption heat pump, and the power consumption of the electric heat pump is calculated from the map of the output of the electric heat pump and the outside temperature.

The power consumption in the high efficiency mode is calculated as follows. First, the output of the adsorption heat pump is calculated from the operating temperature. For this high efficiency mode to be established, the output of the adsorption heat pump needs to be greater than the required cold heat output and the estimated power consumption of the compressor 50. From this, the power consumption of the compressor 50 is calculated when using the output of the adsorption heat pump, which is determined by the operating temperature as described above, and the cold heat temperature of the adsorption heat pump, which is calculated from the map, and the operating condition that minimizes the power consumption is determined from among the operating conditions that are established, and the power consumption at this time is calculated.

The power consumption in parallel drive mode is compared with the power consumption in high efficiency mode, and the mode with the lower power consumption is selected to supply cold heat.

In addition, when the output of the adsorption heat pump is lower than the threshold, there is a concern that exhaust heat will be wasted. Therefore, when it is expected that the output of the adsorption heat pump will be below the threshold, the adsorption heat pump stops outputting and switches to EHP only mode to supply cold heat.

(Heat pump system operation)
Next, an operation of supplying cold heat to the load 40 in the heat pump system 100 of this embodiment will be described.

The control device 90 periodically executes the mode switching process shown in FIG. 9.

First, in step S100, the control device 90 acquires load-side information including the environmental temperature detected by the environmental temperature sensor 92, the exhaust heat temperature detected by the exhaust heat temperature sensor 94, and the required cold heat output, the load-side indoor temperature, and the circulating cold water temperature detected by the load-side sensor 96.

In step S102, the control device 90 calculates the output of the adsorption heat pump.

In step S104, the control device 90 compares the output of the adsorption heat pump with the required cold heat output and determines whether the output of the adsorption heat pump is greater. If the output of the adsorption heat pump is greater than the required cold heat output, the process proceeds to step S106. On the other hand, if the output of the adsorption heat pump is equal to or less than the required cold heat output, the process proceeds to step S108.

In step S106, the control device 90 switches to AHP only mode and performs operation control.

In step S108, the control device 90 determines whether the output of the adsorption heat pump is less than the threshold value. If the output of the adsorption heat pump is less than the threshold value, the process proceeds to step S110. On the other hand, if the output of the adsorption heat pump is equal to or greater than the threshold value, the process proceeds to step S112.

In step S110, the control device 90 switches to EHP only mode and performs operation control.

In step S112, the control device 90 calculates the power consumption in the parallel drive mode and the power consumption in the high efficiency mode.

In step S114, the control device 90 determines whether the power consumption in the parallel drive mode is less than the power consumption in the high efficiency mode. If the power consumption in the parallel drive mode is less than the power consumption in the high efficiency mode, the process proceeds to step S116. On the other hand, if the power consumption in the high efficiency mode is less than the power consumption in the parallel drive mode, the process proceeds to step S118.

In step S116, the control device 90 switches to parallel drive mode and performs operation control.

In step S118, the control device 90 switches to high efficiency mode and performs operation control.

As described above, according to the heat pump system of the first embodiment of the present invention, the first evaporator of the adsorption heat pump is used as the evaporator of the electric heat pump, which is configured to generate cold heat from the expanded refrigerant and supply the refrigerant to the compressor. When the electric heat pump generates cold heat, the second evaporator evaporates a fluid using the refrigerant compressed by the compressor and supplies the refrigerant to the expansion valve. At this time, the adsorption mechanism of the adsorption heat pump adsorbs the fluid evaporated in the second evaporator. In this way, with a simple configuration, it is possible to reduce the power consumption of the electric heat pump when the cold heat output of the adsorption heat pump is insufficient.

In addition, by providing the cold energy generated by the adsorption heat pump, which is lower than the ambient temperature, to the second evaporator that functions as the condenser of the electric heat pump, it is possible to lower the condenser pressure. As a result, under conditions of high ambient temperatures where the adsorption heat pump does not operate in normal mode, the compressor power becomes large, but by lowering the condenser pressure, the compressor power can be significantly reduced. Also, the efficiency of the electric heat pump can be significantly improved when the exhaust heat source is insufficient.

In addition, by integrating the adsorption heat pump and the electric heat pump and sharing the condenser and evaporator, the indoor and outdoor unit parts on the electric heat pump side are eliminated, reducing the number of parts.

In addition, when the outside temperature is high or the exhaust heat temperature is low, the COP of the electric heat pump can be improved by using cold heat of about 25°C that is generated on the adsorption heat pump side and is difficult to use for normal cooling, to lower the condenser pressure on the electric heat pump side.

In addition, when there is a high demand for cold energy, after the adsorption heat pump generates cold energy in the normal manner, the condensation heat of the electric heat pump can be reduced by using the cold energy from the adsorption heat pump to improve the efficiency of the electric heat pump.

In addition, when there is an abundance of exhaust heat, operation in parallel drive mode is possible. After the adsorption of the cold heat generation in the adsorption heat pump is completed, adsorption to process the condensation heat of the electric heat pump is performed, which makes it possible to reduce the electricity consumption of the compressor. At this time, in addition to the heat amount required in the AHP-only mode, heat amount for heat processing required for condensation heat processing in the electric heat pump is required, but since this can also serve as most of the sensible heat, the total amount of cold heat generated per heat amount is greater.

Second Embodiment
A heat pump system according to a second embodiment of the present invention will be described with reference to Fig. 10. This embodiment has a system configuration using two second evaporators. Parts having the same configuration as those in the first embodiment are given the same reference numerals and will not be described.

As shown in FIG. 10, the heat pump system 200 is an electric heat pump that includes a compressor 50, an expansion valve 60, and second evaporators 221 and 222. For simplicity, the control device 90, the environmental temperature sensor 92, the exhaust heat temperature sensor 94, and the load side sensor 96 are omitted from FIG. 10.

The second evaporators 221, 222 function as condensers configured to condense the compressed refrigerant and supply it to the expansion valve 60.

The second evaporator 221, which is closer to the compressor 50, is configured to supply the evaporated fluid to the condenser 30. Specifically, the second evaporator 221 is connected to one end of the flow pipe 71.

The second evaporator 222, which is farther from the compressor 50, is configured to supply the evaporated fluid to the adsorption mechanism 10. Specifically, one end of the flow pipe 78 is connected to the second evaporator 222.

The second evaporator 221 is connected to the compressor 50 and the second evaporator 222 so as to be able to supply the fluid refrigerant gas. Specifically, one end of the flow pipes 81 and 85 is connected to the second evaporator 221.

The first evaporator 222 is connected to the first evaporator 221 and the expansion valve 60 so as to be able to supply the fluid refrigerant gas. Specifically, one end of the flow pipes 82 and 85 is connected to the second evaporator 222.

In the high efficiency mode, as shown in FIG. 10, the adsorption mechanism 10 is controlled to supply cold energy to the second evaporator 222, which functions as a condenser for the electric heat pump.

In the example of FIG. 10, the first adsorber 11 is an adsorber that is regenerated with exhaust heat, and the second adsorber 12 is an adsorber that is cooled to the ambient temperature. Specifically, when the compressor 50 is driven to generate cold heat as an electric heat pump, the valves V2, V3, and V8 are opened, and water vapor is supplied from the second evaporator 221 to the condenser 30 via the flow pipe 71, and the condenser 30 performs a condensation operation of the water vapor. In addition, water vapor is supplied from the second evaporator 222 to the second adsorber 12 via the flow pipes 72, 73, and 78, and the second adsorber 12 performs an adsorption operation of the water vapor.

In addition, valve V7 is opened, and the water vapor desorbed from the first adsorption device 11 is supplied to the condenser 30 via the flow pipe 77, and the water vapor is condensed in the condenser 30.

The first adsorber 11 and the second adsorber 12 are alternately operated like a normal adsorption heat pipe. When the first adsorber 11 or the second adsorber 12, cooled to the ambient temperature, is connected to the second evaporator 222 via the circulation pipe 73 or 74 and the circulation pipe 72, the second evaporator 222 is cooled, and the second evaporator 222, which functions as a condenser for the electric heat pump, is cooled to the cold heat generation temperature of the adsorption heat pump, so that a reduction in the power of the compressor 50 of the electric heat pump can be expected.

The other configurations and operations of the heat pump system 200 are the same as those of the first embodiment, so the explanation is omitted.

10 Adsorption mechanism 11 First adsorption device 12 Second adsorption device 20 Cold heat generation temperature 21, 221 First evaporator 22, 222 Second evaporator 30 Condenser 40 Load 50 Compressor 60 Expansion valve 71-77 Flow pipe 81-84 Flow pipe 85, 86 Heat exchange pipe 90 Control device 92 Environmental temperature sensor 94 Exhaust heat temperature sensor 96 Load side sensor 100, 200 Heat pump system V1-V8 Valve

Claims (2)

A heat pump system including an adsorption heat pump and an electric heat pump,
The adsorption heat pump comprises:
A first evaporator;
an adsorption mechanism including a plurality of adsorbers configured to adsorb the fluid evaporated by the first evaporator;
a condenser configured to condense the fluid desorbed from the adsorption mechanism;
a load to which the cold energy generated by the first evaporator is supplied,
The electric heat pump comprises:
a compressor configured to generate a compressed refrigerant;
an expansion valve configured to expand the refrigerant;
a second evaporator configured to evaporate the fluid using compressed refrigerant and to supply the refrigerant to the expansion valve;
The adsorption mechanism is further configured to adsorb the fluid evaporated in the second evaporator,
The first evaporator is used as an evaporator of the electric heat pump, which is configured to generate cold heat from the expanded refrigerant and supply the refrigerant to the compressor;
The condenser is further configured to condense the fluid evaporated in the second evaporator;
The second evaporator functions as a condenser of the electric heat pump ,
The second evaporator includes a plurality of evaporators that are connected in series to the compressor and evaporate the fluid by using the compressed refrigerant,
an evaporator proximate to the compressor configured to supply evaporated fluid to the condenser;
A heat pump system , wherein the evaporator remote from the compressor is configured to supply the evaporated fluid to the adsorption mechanism . The heat pump system according to claim 1 , wherein the fluid is water and the refrigerant is a fluorocarbon gas.