JP2018105514A - Heat pump type temperature adjustment device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve performance of a heat pump type temperature adjustment device.SOLUTION: A cooling evaporator E1 acting as a fluid cooling unit for heat exchanging between refrigerant (r) and fluid OA and a heat absorbing evaporator E2 for heat exchanging between the refrigerant (r) with the fluid OA are individually arranged. A heating condenser C1 acting as a fluid heater for heat exchanging between the refrigerant (r) and the fluid OA and a radiation condenser C2 for heat exchanging between the refrigerant (r) and the radiation source Aa are individually arranged. There are provided evaporation side shunt ratio adjustment means Ex1, Ex2 for adjusting the shunt ratio between the refrigerant (r) passing through a cooling evaporator E1 and the refrigerant (r) passing through a heat absorbing evaporator E2 and at the same time there are provided condensation side shunt ratio adjustment means Mv1,Mv2 for adjustment of shunt ratio of the refrigerant (r) passing through the heating condenser C1 and the refrigerant (r) passing through the radiation condenser C2 while being independent from the shunt ratio adjustment.SELECTED DRAWING: Figure 1

Description

  TECHNICAL FIELD The present invention relates to a heat pump temperature control device, and more particularly, includes a vapor compression refrigerant circuit that circulates refrigerant by a compressor, a cooling operation that processes a cooling load of fluid, and a heating operation that processes the heating load of the fluid. It is related with the heat pump type temperature control apparatus which enabled switching implementation.

  Conventionally, in this type of heat pump temperature control device, as shown in FIG. 12, the temperature adjustment side heat exchanger Ni that exchanges heat between the fluid OA to be adjusted and the refrigerant r, and the heat exchange between the refrigerant r and the heat absorbing / dissipating source A And a cooling circulation state in which the refrigerant r is circulated in the order of the compressor Cmp → the heat source side heat exchanger No → the expansion means Ex → the temperature adjustment side heat exchanger Ni → the compressor Cmp. (Indicated by a solid arrow in the figure) and a circulating state for heating in which the refrigerant r is circulated in the order of the compressor Cmp → the temperature adjustment side heat exchanger Ni → the expansion means Ex → the heat source side heat exchanger No → the compressor Cmp. A four-way valve V that reverses the direction of the flow of the refrigerant r in the refrigerant circuit RC is provided in the refrigerant circuit RC (indicated by a dashed arrow in the figure), and switching between the cooling operation and the heating operation is performed by the switching operation of the four-way valve V. It was like that.

  That is, in the cooling operation (solid arrow), the heat source side heat exchanger No. functions as a condenser, and the temperature adjustment side heat exchanger Ni functions as an evaporator, so that the fluid OA to be adjusted is temperature adjusted side heat. In the exchanger Ni, cooling is performed by exchanging heat with the refrigerant r in the evaporation process. On the other hand, in the heating operation (broken arrow), the heat source side heat exchanger No. functions as an evaporator and temperature control is performed. The side heat exchanger Ni is caused to function as a condenser, and the fluid OA to be adjusted is heated by exchanging heat with the refrigerant r in the condensation process in the temperature adjustment side heat exchanger Ni.

Japanese Utility Model Publication No. 62-145070

  However, in the above-described conventional heat pump temperature control device, the flow of the refrigerant r is substantially the entire refrigerant circuit RC (specifically, all circuit portions except for the portion between the compressor Cmp and the four-way valve V). Since the switching between the cooling operation and the heating operation is performed by reversing the direction, the operation of the compressor Cmp is temporarily stopped at the time of the switching, and the flow of the refrigerant r in the refrigerant circuit RC is totally changed. During the stop period, it is impossible to cope with the cooling load and the heating load. In this respect, there is a problem that the performance of the apparatus is limited to be low.

  In addition, there is a lower limit in the output adjustment range of the compressor Cmp, and the output of the compressor Cmp cannot be reduced below the lower limit with respect to a decrease in cooling load or heating load. There is a load range that cannot be handled between the load range that can be handled by adjusting the output of the compressor Cmp and the load range that can be handled by adjusting the output of the compressor Cmp during heating operation. There was a limited problem.

  In view of this situation, the main problem of the present invention is to solve the above problems at once and to effectively improve the performance of the heat pump temperature control device.

The first characteristic configuration of the present invention relates to a heat pump temperature control device,
Provided with a vapor compression refrigerant circuit that circulates refrigerant with a compressor,
A heat pump temperature control device that enables switching between a cooling operation for processing a cooling load of a fluid and a heating operation for processing a heating load of the fluid,
As an evaporator in the refrigerant circuit, a cooling evaporator as a fluid cooler for exchanging heat between the refrigerant and the fluid, and an endothermic evaporator for exchanging heat between the refrigerant and an endothermic source are provided separately.
As the condenser in the refrigerant circuit, a heating condenser as a fluid heater for exchanging heat between the refrigerant and the fluid, and a heat dissipating condenser for exchanging heat between the refrigerant and a heat radiation source are provided separately.
Providing an evaporation-side diversion ratio adjusting means for adjusting a diversion ratio between the refrigerant that passes through the cooling evaporator and the refrigerant that passes through the endothermic evaporator;
Independently of the diversion ratio adjustment by the diversion ratio adjustment means on the evaporation side, the diversion ratio adjustment on the condensation side that adjusts the diversion ratio between the refrigerant that passes through the heating condenser and the refrigerant that passes through the heat dissipation condenser Means is provided.

  According to this configuration, while the output of the compressor is kept constant, in the cooling operation, the flow rate ratio of the refrigerant on the side to be passed through the cooling evaporator is reduced in the diversion ratio adjustment by the evaporation side diversion ratio adjusting means. The cooling amount for the fluid in the cooling evaporator can be reduced, and in the heating operation, the flow rate of the refrigerant on the side to be passed to the heating condenser in the diversion ratio adjustment by the diversion ratio adjustment means on the condensation side The smaller the ratio, the smaller the heating amount for the fluid in the heating condenser.

  As a result, the load range that can be handled by the cooling operation and the load range that can be handled by the heating operation can be made substantially continuous, and the load ranges that can be handled can be handled. It is possible to avoid an impossible load range.

  Further, according to the above configuration, the cooling operation state and the heating operation state are substantially changed by changing the balance between the cooling amount for the fluid in the cooling evaporator and the heating amount for the fluid in the heating condenser. Therefore, switching between the cooling operation and the heating operation can be performed only by adjusting the diversion ratio by the diversion ratio adjustment means on the evaporation side and the condensation side.

  In other words, this requires a period for temporarily stopping the compressor operation when switching between the cooling operation and the heating operation, as in the case of a conventional device in which switching between the cooling operation and the heating operation is performed by a four-way valve. Can be avoided.

  Therefore, according to this configuration, the switching between the cooling operation and the heating operation can be performed without causing the temporary operation stop of the compressor and constantly following the temperature control output appropriately with respect to the load change. In this respect, the device performance can be effectively enhanced as compared with the conventional device.

  In addition, in the implementation of the above configuration, the switching from the cooling operation to the heating operation is automatically executed as the fluid temperature control load changes from the cooling load to the heating load, and the fluid temperature control load is changed to the heating load. If the configuration is such that the switching from the heating operation to the cooling operation is automatically performed in accordance with the change from the cooling load to the cooling load, the convenience of the apparatus can be further enhanced.

  The “adjustment of the diversion ratio” referred to in the present invention may be an adjustment including setting the flow rate ratio of one refrigerant to 0%.

The second feature configuration of the present invention specifies an embodiment suitable for the implementation of the first feature configuration.
As the cooling operation, in the state where the flow rate ratio of the refrigerant passing through the cooling evaporator is maximized in the diversion ratio adjustment by the diversion ratio adjustment means on the evaporation side, the output of the compressor is set to the cooling load of the fluid. Normal cooling operation to adjust according to,
With the output of the compressor minimized, the diversion ratio between the refrigerant passing through the cooling evaporator and the refrigerant passing through the endothermic evaporator is determined according to the cooling load of the fluid. Selectively performing the low-load cooling operation adjusted by the adjusting means,
As the heating operation, in the state where the flow rate ratio of the refrigerant passing through the heating condenser in the diversion ratio adjustment by the condensing side diversion ratio adjusting means is maximized, the output of the compressor is set to the heating load of the fluid. Normal heating operation to adjust according to,
In the state where the output of the compressor is minimized, the diversion ratio between the refrigerant that passes through the heating condenser and the refrigerant that passes through the heat dissipation condenser depends on the heating load of the fluid. The low load heating operation adjusted by the adjusting means is selectively implemented.
According to this configuration, a normal cooling operation is performed as a cooling operation when the cooling load is large, and a low-load cooling operation is performed as a cooling operation when the cooling load is small. A large load range can be secured.

  Similarly, when the heating load is large, the normal heating operation is performed as the heating operation, and when the heating load is small, the low load heating operation is performed as the heating operation. A large range can be secured.

The third feature configuration of the present invention specifies an embodiment suitable for the implementation of the second feature configuration.
During the implementation of the normal cooling operation, when the output of the compressor is minimized, switching to the low-load cooling operation is performed,
During the execution of the low load cooling operation, when the flow rate ratio of the refrigerant passing through the cooling evaporator is maximized in the diversion ratio adjustment by the evaporation diversion ratio adjustment means, the switching to the normal cooling operation is performed. Run
During the implementation of the normal heating operation, when the output of the compressor is minimized, switching to the low load heating operation is performed,
During the execution of the low load heating operation, when the flow rate ratio of the refrigerant passing through the heating condenser is maximized in the diversion ratio adjustment by the condensing side diversion ratio adjusting means, switching to the normal heating operation is performed. The point is that it is configured to execute.

  According to this configuration, the switching between the normal cooling operation and the low load cooling operation is automatically performed according to the change in the cooling load, and the switching between the normal heating operation and the low load heating operation is performed according to the change in the heating load. Since it is performed automatically, the convenience of the apparatus can be further enhanced.

The fourth characteristic configuration of the present invention specifies an embodiment suitable for the implementation of any of the first to third characteristic configurations,
The refrigerant circuit divides the refrigerant discharged from the compressor into two flows, passes one of the divided refrigerants through the heating condenser, and condenses sent from the other divided refrigerant and the heating condenser. The refrigerant is combined and passed through the heat dissipation condenser.

  According to this configuration, while condensing the refrigerant in each of the heating condenser that exchanges heat between the refrigerant and the fluid to be adjusted and the heat radiation condenser that exchanges heat between the refrigerant and the heat radiation source, Since the state of the refrigerant sent to the evaporation step can be made uniform in the heat dissipation condenser, the operation of the refrigerant circuit can be stabilized.

The fifth characteristic configuration of the present invention specifies an embodiment suitable for implementation of any of the first to fourth characteristic configurations,
The fluid is air;
In the cooling operation, the air is cooled and dehumidified in the cooling evaporator, and then the cooled and dehumidified air is reheated to a required temperature in the heating condenser.

  According to this configuration, the air to be adjusted can be adjusted to the required temperature while cooling and dehumidifying the air to be adjusted in the cooling operation. Can be a perfect device.

Device configuration diagram of heat pump air conditioner Diagram showing the state of normal cooling operation Diagram showing the state of low-load cooling operation Diagram showing the state of normal heating operation The figure which shows the execution state of low load heating operation Table explaining each control in cooling operation Table explaining each control in heating operation Flow chart showing switching control between normal cooling operation and low load cooling operation Flow chart showing switching control between normal heating operation and low load heating operation Flow chart showing switching control between cooling operation and heating operation Graph showing the transition state of each part when switching between cooling operation and heating operation Configuration diagram of a conventional heat pump temperature controller

  FIG. 1 shows a heat pump type air conditioner which is an example of a heat pump type temperature control device, and this heat pump type air conditioner adjusts the temperature and humidity of the introduced outside air OA using the introduced outside air OA as a fluid to be adjusted.

  In addition, the heat pump air conditioner includes a vapor compression refrigerant circuit RC that circulates the refrigerant r by the compressor Cmp.

  Reference numeral 1 denotes an air conditioner casing. An air inlet 2 is formed at one end of the air conditioner casing 1, and an air outlet 3 is formed at the other end of the air conditioner casing 1.

  Inside the air conditioner casing 1, the air is humidified by spraying a finned tube type cooling evaporator E <b> 1 as an air cooler, a finned tube type heating condenser C <b> 1 as an air heater, and water vapor s. The humidifiers 4 are arranged in that order from the air inlet 2 side to the air outlet 3 side.

  The air outlet 3 in the air conditioner casing 1 is equipped with an air supply fan 6. By operating the air supply fan 6, outside air OA to be adjusted is introduced into the air conditioner casing 1 through the air inlet 2. The outside air adjusted in temperature and humidity inside the air conditioner casing 1 is sent as adjusted air SA from the air conditioner casing 1 to the air conditioning target space 5 through the air outlet 3.

  Reference numeral 7A denotes a heat radiating outdoor unit. The heat radiating outdoor unit 7A includes a fin tube type heat radiating condenser C2 serving as a heat radiating device, and heat radiating air Aa (for example, a heat radiating source for the heat radiating condenser C2). And a heat dissipating fan 8 for ventilating the outside air.

  Further, the outdoor unit 7A for heat dissipation is also equipped with a compressor Cmp in the refrigerant circuit RC.

  Reference numeral 7B denotes an endothermic outdoor unit. The endothermic outdoor unit 7B includes a finned tube-type endothermic evaporator E2 as a heat absorber and an endothermic air Ab (for example, an endothermic source for the endothermic evaporator E2). , A heat absorption fan 9 for ventilating the outside air and the air discharged from the air-conditioning target space 5.

In configuring the refrigerant circuit RC, the refrigerant discharge port of the compressor Cmp is connected to the refrigerant inlet of the heating condenser C1 through the refrigerant path 10, and the refrigerant outlet of the heating condenser C1 is for heat dissipation through the refrigerant path 11. It is connected to the refrigerant inlet of the condenser C2.
The refrigerant path 10 and the refrigerant path 11 are short-circuited by a bypass refrigerant path 12, and a part of the refrigerant r discharged from the compressor Cmp directly passes through the bypass refrigerant path 12 to the refrigerant of the heat radiation condenser C <b> 2. It leads to the entrance.

  That is, in this refrigerant circuit RC, the refrigerant r discharged from the compressor Cmp is divided into two flows, one of the divided refrigerants r is passed through the heating condenser C1, and the other divided refrigerant r and the heating condenser are passed. The condensed refrigerant r delivered from C1 is merged and passed through the heat radiation condenser C2.

  The refrigerant inlet of the heating condenser C1 is equipped with a heating flow rate adjustment valve Mv1, and the bypass refrigerant path 12 is equipped with a heat dissipation flow rate adjustment valve Mv2.

  The heating flow rate adjustment valve Mv1 and the heat dissipation flow rate adjustment valve Mv2 are used to adjust the diversion ratio on the condensing side for adjusting the diversion ratio between the refrigerant r passed through the heating condenser C1 and the refrigerant r passed through the heat dissipation condenser C2. Configure the means.

  The refrigerant outlet of the heat dissipating condenser C2 is connected to the refrigerant inlet of the cooling evaporator E1 through the refrigerant passage 13, and the refrigerant outlet of the cooling evaporator E1 is connected to the refrigerant inlet of the compressor Cmp through the refrigerant passage 14. is there.

  The refrigerant path 15 branched from the refrigerant path 13 is connected to the refrigerant inlet of the endothermic evaporator E2, and the refrigerant outlet of the endothermic evaporator E2 is connected to the refrigerant path 14 through the refrigerant path 16.

  The refrigerant inlet of the cooling evaporator E1 is equipped with a cooling expansion valve Ex1, the refrigerant outlet of the cooling evaporator E1 is equipped with an evaporation pressure control valve Er, and the refrigerant inlet of the endothermic evaporator E2 is installed. Is equipped with an endothermic expansion valve Ex2.

  The cooling expansion valve Ex1 and the endothermic expansion valve Ex2 are expansion valves, and at the same time, an evaporation that adjusts the diversion ratio between the refrigerant r that passes through the cooling evaporator E1 and the refrigerant r that passes through the endothermic evaporator E2. Side diversion ratio adjusting means.

  The refrigerant r that has been split into two streams after being discharged from the compressor Cmp joins at the inflow stage to the heat radiation condenser C2, and is sent out from each of the cooling evaporator E1 and the endothermic evaporator E2. Since the refrigerant r is combined at the return stage to the compressor Cmp, the diversion ratio adjustment by the condensation side diversion ratio adjusting means Mv1 and Mv2 and the diversion ratio by the evaporation side diversion ratio adjusting means Ex1 and Ex2 are described above. Adjustments are independent of each other.

  On the other hand, with respect to the sensors, a temperature sensor S0 that detects the temperature T0 of the outside air OA to be adjusted, a temperature sensor S1 that detects the temperature T1 of the outlet air in the cooling evaporator E1, and an adjustment that is sent from the air conditioner casing 1 A temperature sensor S2 for detecting the temperature T2 of the air SA and a humidity sensor S3 for detecting the humidity X2 of the adjusted air SA are provided.

  Other sensors include the suction pressure Ps of the compressor Cmp, the degree of superheat Sh1 of the outlet refrigerant r in the cooling evaporator E1, the degree of superheat Sh2 of the outlet refrigerant r in the endothermic evaporator E2, and the heat radiation condenser C2. Sensors (not shown) for detecting the condensing pressure Pc of the refrigerant r are provided.

  In this heat pump type air conditioner, basically, a cooling operation for processing the cooling load of the introduced outside air OA and a heating operation for processing the heating load of the introduced outside air OA are alternatively performed.

  Specifically, in the cooling operation, the outside air OA introduced into the air conditioner casing 1 is cooled and dehumidified by exchanging heat with the refrigerant r in the evaporation process in the cooling evaporator E1, and then the air thus cooled and dehumidified is removed. In the heating condenser C1, heat is exchanged with the refrigerant r in the condensation process to reheat (heat after cooling and dehumidification), and the reheated air is humidified by the humidifier 4 as necessary and adjusted. The air SA is sent from the air conditioner casing 1 to the air conditioning target space 5.

  In the heating operation, the outside air OA introduced into the air conditioner casing 1 is heated by exchanging heat with the refrigerant r in the condensation process in the heating condenser C1, and then the heated air is heated by the humidifier 4. The humidified air is sent out from the air conditioner casing 1 to the air conditioning target space 5 as the adjusted air SA.

  There are two types of cooling operation, “normal cooling operation” performed under a large cooling load condition and “low load cooling operation” performed under a small cooling load condition. As described above, the refrigerant r discharged from the compressor Cmp is divided into two flows, and one of the refrigerants r is supplied to the heating condenser C1 through the heating flow rate adjusting valve Mv1, and is supplied to the heating condenser C1. Heat exchange with air after cooling and dehumidification in the condensation process.

  In parallel with this, the other shunt refrigerant r is supplied to the heat radiation condenser C2 through the heat radiation flow adjustment valve Mv2 in a state where it is combined with the refrigerant r sent out from the heating condenser C1, and this heat radiation refrigerant C In the condensation process in the condenser C2, heat is exchanged with the heat radiation air Aa.

  The condensed refrigerant r delivered from the heat radiation condenser C2 is supplied to the cooling evaporator E1 through the cooling expansion valve Ex1, and is exchanged with the introduced outside air OA in the evaporation process in the cooling evaporator E1.

  And the evaporative refrigerant | coolant r sent out from the evaporator E1 for cooling returns to the compressor Cmp through the evaporating pressure control valve Er.

  On the other hand, in the low load cooling operation, as shown in FIG. 3, the refrigerant r discharged from the compressor Cmp is divided into two flows, and one of the refrigerants r is supplied to the heating condenser through the heating flow rate adjustment valve Mv1. It supplies to C1, and heat-exchanges with the air after cooling dehumidification in the condensation process in this condenser C1 for a heating.

  In parallel with this, the other shunt refrigerant r is supplied to the heat radiation condenser C2 through the heat radiation flow adjustment valve Mv2 in a state where it is combined with the refrigerant r sent out from the heating condenser C1, and this heat radiation refrigerant C In the condensation process in the condenser C2, heat is exchanged with the heat radiation air Aa.

  The condensed refrigerant r sent out from the heat radiation condenser C2 is again divided into two flows, and one of the divided refrigerants r is supplied to the cooling evaporator E1 through the cooling expansion valve Ex1, and this cooling evaporator E1 In the evaporation process, heat is exchanged with the introduced outside air OA.

  In parallel with this, the other shunt refrigerant r is supplied to the endothermic evaporator E2 through the endothermic expansion valve Ex2, and exchanges heat with the endothermic air Ab in the evaporation process in the endothermic evaporator E2.

  Then, the evaporative refrigerant r delivered from the cooling evaporator E1 and the evaporative refrigerant r delivered from the endothermic evaporator E2 are merged and returned to the compressor Cmp.

  Similarly, there are two types of heating operation, “normal heating operation” performed under a large heating load condition and “low load heating operation” performed under a small heating load condition. As shown in FIG. 4, the entire amount of refrigerant r discharged from the compressor Cmp is supplied to the heating condenser C1 through the heating flow rate adjusting valve Mv1, and introduced outside air OA in the condensation process in the heating condenser C1. Heat exchange.

  The condensed refrigerant r sent out from the heating condenser C1 is supplied to the endothermic evaporator E2 through the radiating condenser C2 and the endothermic expansion valve Ex2, and the endothermic air is evaporated in the endothermic evaporator E2. Heat exchange with Ab.

  Then, the evaporative refrigerant r delivered from the endothermic evaporator E2 is returned to the compressor Cmp.

  On the other hand, in the low load heating operation, as shown in FIG. 5, the discharge refrigerant r from the compressor Cmp is divided into two flows, and one of the divided refrigerant r passes through the heating flow rate adjustment valve Mv1. C1 is supplied, and heat is exchanged with the introduced outside air OA in the condensation process in the heating condenser C1.

  In parallel with this, the other shunt refrigerant r is supplied to the heat radiation condenser C2 through the heat radiation flow rate adjustment valve Mv2 in a state of being merged with the refrigerant sent from the heating condenser C1, and this heat radiation condensation is performed. The heat is exchanged with the heat radiation air Aa in the condensation process in the vessel C2.

  The entire amount of the condensed refrigerant r delivered from the heat radiation condenser C2 is supplied to the heat absorption evaporator E2 through the heat absorption expansion valve Ex2, and the heat absorption air Ab and heat are evaporated in the heat absorption evaporator E2. Let them exchange.

  Then, the evaporative refrigerant r delivered from the endothermic evaporator E2 is returned to the compressor Cmp.

  That is, in the low load cooling operation, the condensed refrigerant r delivered from the heat radiation condenser C2 is cooled by the cooling evaporator E1 with respect to the introduced outside air OA, and the endothermic evaporator E2 also performs the heat absorption air. An endothermic action (in other words, a cooling action) is performed on Aa, so that the required output G of the compressor Cmp is kept high, so that the output G of the compressor Cmp can be maintained even when the cooling load of the introduced outside air OA is small. Is less than the lower limit value Gmin of the adjustment range, so that the cooling operation can be continued.

  Similarly, in the low load heating operation, in addition to heating the discharged refrigerant r from the compressor Cmp to the introduced outside air OA by the heating condenser C1, the radiating air Aa is also discharged by the radiating condenser C2. The required output G of the compressor Cmp is kept high by performing a heat dissipating action (in other words, a heating action), so that the output G of the compressor Cmp is reduced even in a situation where the heating load of the introduced outside air OA is small. The heating operation can be continued by avoiding being less than the lower limit Gmin of the adjustment range.

  Reference numeral 17 denotes a control device, and the control device 17 executes the following control in each of the four types of operations.

(Normal cooling operation) See Fig. 6 a. The suction pressure Ps of the compressor Cmp is adjusted to a set value by adjusting the output G of the compressor Cmp (specifically, the rotational frequency of the compressor motor) based on the detected value of the suction pressure Ps in the compressor Cmp.

  b. The degree of superheat Sh1 of the outlet refrigerant r in the cooling evaporator E1 is adjusted to a set value by adjusting the opening of the cooling expansion valve Ex1 based on the detected value of the degree of superheat Sh1 of the outlet refrigerant r in the cooling evaporator E1. To do.

  c. The endothermic expansion valve Ex2 is fixed in a fully closed state.

  d. By adjusting the opening degree of the evaporation pressure control valve Er based on the detected value of the outlet air temperature T1 in the cooling evaporator E1, the outlet air temperature T1 in the cooling evaporator E1 is adjusted to the set value Ts1.

  e. The temperature T2 of the adjusted air SA sent to the air-conditioning target space 5 is adjusted to the set value Ts2 by adjusting the opening of the heating flow rate adjustment valve Mv1 based on the detected value of the temperature T2 of the adjusted air SA.

  f. The opening degree of the heat dissipation flow rate adjustment valve Mv2 is adjusted to a state opposite to the opening degree of the heating flow rate adjustment valve Mv1.

  g. Adjustment sent out to the air-conditioning target space 5 by adjusting the opening of the humidification flow rate adjustment valve Mv3 based on the detected value of the humidity X2 of the adjusted air SA and adjusting the spray amount of the water vapor s in the humidifier 4. The humidity X2 of the used air SA is adjusted to the set value Xs2.

  h. By adjusting the output of the heat radiation fan 8 based on the detected value of the condensation pressure Pc of the refrigerant r in the heat radiation condenser C2, the condensation pressure Pc of the refrigerant r in the heat radiation condenser C2 is adjusted to a set value.

(Low-load cooling operation) See Fig. 6 a. The output G of the compressor Cmp is fixed to the lower limit value Gmin of the adjustment range.

  b. Similar to the normal cooling operation, the degree of superheat of the outlet refrigerant r in the cooling evaporator E1 is adjusted by adjusting the opening of the cooling expansion valve Ex1 based on the detected value of the degree of superheat Sh1 of the outlet refrigerant r in the cooling evaporator E1. Sh1 is adjusted to a set value.

  c. The suction pressure Ps of the compressor Cmp is adjusted to a set value by adjusting the opening of the heat absorption expansion valve Ex2 based on the detected value of the suction pressure Ps in the compressor Cmp.

  d. As in the normal cooling operation, the outlet air temperature T1 in the cooling evaporator E1 is set by adjusting the opening of the evaporation pressure control valve Er based on the detected value of the outlet air temperature T1 in the cooling evaporator E1. Adjust to Ts1.

  e. Similar to the normal cooling operation, the temperature T2 of the adjusted air SA sent to the air-conditioning target space 5 is set by adjusting the opening of the heating flow rate adjustment valve Mv1 based on the detected value of the temperature T2 of the adjusted air SA. Adjust to Ts2.

  f. Similar to the normal cooling operation, the opening degree of the heat-dissipation flow rate adjustment valve Mv2 is adjusted to be in a state opposite to that of the heating flow rate adjustment valve Mv1.

  g. Similar to the normal cooling operation, the opening degree of the humidification flow rate adjustment valve Mv3 is adjusted based on the detected value of the humidity X2 of the adjusted air SA, and the amount of water vapor s sprayed in the humidifier 4 is adjusted. The humidity X2 of the adjusted air SA sent to the space 5 is adjusted to the set value Xs2.

  h. As with the normal cooling operation, the condensation pressure Pc of the refrigerant r in the heat dissipation condenser C2 is adjusted by adjusting the output of the heat dissipation fan 8 based on the detected value of the condensation pressure Pc of the refrigerant r in the heat dissipation condenser C2. Adjust to.

  That is, in the normal cooling operation, in the state where the flow rate ratio of the refrigerant r on the side to be passed through the cooling evaporator E1 is maximized in the diversion ratio adjustment by the evaporation side diversion ratio adjusting means Ex1 and Ex2, the compressor Cmp An operation mode in which the output G is adjusted according to the cooling load of the introduced outside air OA is employed.

  On the other hand, in the low load cooling operation, with the output G of the compressor Cmp minimized, the flow dividing ratio between the refrigerant r passed through the cooling evaporator E1 and the refrigerant r passed through the endothermic evaporator E2 is set. An operation mode is adopted in which adjustment is performed by the diversion ratio adjusting means Ex1, Ex2 on the evaporation side according to the cooling load of the introduced outside air OA.

(Normal heating operation) See FIG. 7 a. By adjusting the output G of the compressor Cmp based on the detected value of the temperature T2 of the adjusted air SA, the temperature T2 of the adjusted air SA sent to the air-conditioning target space 5 is adjusted to the set value Ts2.

  b. The cooling expansion valve Ex1 is fixed in a fully closed state.

  c. In a situation where the detected value of the temperature T0 of the introduced outside air OA is smaller than the set threshold Te (T0 <Te), the opening degree of the endothermic expansion valve Ex2 is set based on the detected value of the degree of superheat Sh2 of the outlet refrigerant r in the endothermic evaporator E2. By adjusting, the degree of superheat Sh2 of the outlet refrigerant r in the endothermic evaporator E2 is adjusted to a set value.

  Further, in a situation where the detected value of the temperature T0 of the introduced outside air OA is equal to or higher than the set threshold Te (T0 ≧ Te), the opening degree of the endothermic expansion valve Ex2 is adjusted based on the detected value of the suction pressure Ps in the compressor Cmp. Then, the suction pressure Ps of the compressor Cmp is adjusted to a set value.

  d. The evaporation pressure control valve Er is fixed in a fully closed state or a minimum opening state.

  e. The heating flow rate adjustment valve Mv1 is fixed in a fully open state.

  f. The heat dissipation flow adjustment valve Mv2 is fixed in a fully closed state.

  g. As in the cooling operation, the opening degree of the humidification flow rate adjustment valve Mv3 is adjusted based on the detected value of the humidity X2 of the adjusted air SA, and the amount of water vapor s sprayed in the humidifier 4 is adjusted. The humidity X2 of the adjusted air SA sent to 5 is adjusted to the set value Xs2.

  h. Similar to the cooling operation, the condensation pressure Pc of the refrigerant r in the heat radiation condenser C2 is adjusted to the set value by adjusting the output of the heat radiation fan 8 based on the detected value of the condensation pressure Pc of the refrigerant r in the heat radiation condenser C2. adjust.

(Low load heating operation) See Fig. 7 a. The output G of the compressor Cmp is fixed to the lower limit value Gmin of the adjustment range.

  b. As in the normal heating operation, the cooling expansion valve Ex1 is fixed in a fully closed state.

  c. As in the normal heating operation, in a situation where the detected value of the temperature T0 of the introduced outside air OA is smaller than the set threshold Te (T0 <Te), the endothermic expansion is based on the detected value of the superheat degree Sh2 of the outlet refrigerant r in the endothermic evaporator E2. By adjusting the opening degree of the valve Ex2, the superheat degree Sh2 of the outlet refrigerant r in the endothermic evaporator E2 is adjusted to a set value.

  Further, in a situation where the detected value of the temperature T0 of the introduced outside air OA is equal to or higher than the set threshold Te (T0 ≧ Te), the opening degree of the endothermic expansion valve Ex2 is adjusted based on the detected value of the suction pressure Ps in the compressor Cmp. Then, the suction pressure Ps of the compressor Cmp is adjusted to a set value.

  d. Similar to the normal heating operation, the evaporation pressure control valve Er is fully closed or fixed to the minimum opening state.

  e. The temperature T2 of the adjusted air SA sent to the air-conditioning target space 5 is adjusted to the set value Ts2 by adjusting the opening of the heating flow rate adjustment valve Mv1 based on the detected value of the temperature T2 of the adjusted air SA.

  f. The opening degree of the heat dissipation flow rate adjustment valve Mv2 is adjusted to a state opposite to the opening degree of the heating flow rate adjustment valve Mv1.

  g. As in the cooling operation, the opening degree of the humidification flow rate adjustment valve Mv3 is adjusted based on the detected value of the humidity X2 of the adjusted air SA, and the amount of water vapor s sprayed in the humidifier 4 is adjusted. The humidity X2 of the adjusted air SA sent to 5 is adjusted to the set value Xs2.

  h. Similar to the cooling operation, the condensation pressure Pc of the refrigerant r in the heat radiation condenser C2 is adjusted to the set value by adjusting the output of the heat radiation fan 8 based on the detected value of the condensation pressure Pc of the refrigerant r in the heat radiation condenser C2. adjust.

  That is, in the normal heating operation, in the state where the flow rate ratio of the refrigerant r on the side to be passed to the heating condenser C1 is maximized in the diversion ratio adjustment by the condensation side diversion ratio adjusting means Mv1 and Mv2, the compressor Cmp The driving | running form which adjusts the output G according to the heating load of introduction external air OA is taken.

  Further, in the low load heating operation, the shunt ratio between the refrigerant r passed through the heating condenser C1 and the refrigerant r passed through the heat radiation condenser C2 in the state where the output G of the compressor Cmp is minimized is introduced outside air OA. The operation form is adjusted by the diversion ratio adjusting means Mv1, Mv2 on the condensing side according to the heating load.

  In addition to the above controls, the control device 17 automatically executes switching between the normal cooling operation and the low load cooling operation and switching between the normal heating operation and the low load heating operation.

  Specifically, as shown in FIG. 8, under the “normal cooling operation” in which the suction pressure Ps in the compressor Cmp is adjusted to the set value by adjusting the output G of the compressor Cmp, the compressor Cmp When the output G decreases to the lower limit value Gmin of the adjustment range, switching from the normal cooling operation to the low load cooling operation is executed.

  In addition, when the “low load cooling operation” is performed in which the suction pressure Ps in the compressor Cmp is adjusted to the set value by adjusting the opening of the endothermic expansion valve Ex2, the opening of the endothermic expansion valve Ex2 is fully closed. When the state is reached (in other words, the flow rate ratio of the refrigerant r on the side that passes through the cooling evaporator E1 is maximized in the diversion ratio adjustment by the evaporation side diversion ratio adjusting means Ex1, Ex2), the low load cooling operation is started. Switch to normal cooling operation.

  On the other hand, as shown in FIG. 9, under the “normal heating operation” in which the temperature T2 of the adjusted air SA is adjusted to the set value Ts2 by adjusting the output G of the compressor Cmp, the output G of the compressor Cmp. Decreases to the lower limit value Gmin of the adjustment range, switching from the normal heating operation to the low load heating operation is executed.

  Further, under the “low load heating operation” in which the temperature T2 of the adjusted air SA is adjusted to the set value Ts2 by adjusting the opening of the heating flow rate adjusting valve Mv1, the opening of the heating flow rate adjusting valve Mv1 is adjusted. Is fully opened (in other words, the flow rate ratio of the refrigerant r on the side to be passed through the heating condenser C1 is maximized in the diversion ratio adjustment by the condensing side diversion ratio adjusting means Mv1, Mv2). Switch from operation to normal heating operation.

  Further, the control device 17 automatically performs switching between the cooling operation and the heating operation. Specifically, as shown in FIG. 10, the evaporation for cooling is performed by adjusting the opening degree of the evaporation pressure control valve Er. Under the “cooling operation” in which the outlet air temperature T1 in the evaporator E1 is adjusted to the set value Ts1, the temperature T0 of the outside air OA detected by the temperature sensor S0 is the set value of the outlet air temperature T1 in the cooling evaporator E1. When Ts1 or less (T0 ≦ Ts1) (ie, the cooling load of the introduced outside air OA is eliminated and the heating load is generated), switching from the cooling operation to the heating operation (usually from the low load cooling operation to the low load heating) Switch to operation).

  Further, under the “heating operation”, the temperature T0 of the outside air OA detected by the temperature sensor S0 becomes higher than the set value Ts1 of the outlet air temperature T1 in the cooling evaporator E1 (T0> Ts1) (that is, introduction) When the heating load of the outside air OA is eliminated and a cooling load is generated), switching from the heating operation to the cooling operation (usually switching from the low load heating operation to the low load cooling operation) is performed.

  That is, with this heat pump type air conditioner, the load range that can be handled by the cooling operation and the load range that can be handled by the heating operation are continuous, and the conventional device that switches between the cooling operation and the heating operation by a four-way valve is also available. As described above, the cooling operation and the heating operation do not reverse the flow direction of the refrigerant in the majority of the refrigerant circuit, and the cooling operation is performed while maintaining the flow direction of the refrigerant r for the entire refrigerant circuit RC. Therefore, the switching between the cooling operation and the heating operation can be performed without interposing the operation stop period between the cooling operation and the heating operation.

  In this respect, the performance of the heat pump air conditioner can be effectively enhanced as compared with the conventional machine.

  FIG. 11 is a graph showing a transition state of each part at the time of switching between the cooling operation and the heating operation in the experimental machine. In this graph, the temperature T0 of the introduced outside air OA is equal to the outlet air temperature T1 in the cooling evaporator E1. When it becomes higher than the set value Ts1 (T0> Ts1), it is recognized that the cooling expansion valve Ex1 and the evaporation pressure control valve Er start to open, and the switching from the heating operation to the cooling operation is performed.

  Conversely, when the temperature T0 of the introduced outside air OA becomes lower than the set value Ts1 of the outlet air temperature T1 in the cooling evaporator E1 (T0 ≦ Ts1), the cooling expansion valve Ex1 and the evaporation pressure control valve Er start to close. It can be seen that switching from the cooling operation to the heating operation is performed.

[Another embodiment]
Next, other embodiments of the present invention will be listed.

  In the above embodiment, the heat pump type air conditioner is shown as an example of the heat pump type temperature control device. However, the heat pump type temperature control device according to the present invention is not limited to the air conditioner and can be applied to various uses in various fields. it can.

  The fluid whose temperature is to be controlled may be any fluid, regardless of whether it is a gas or a liquid, as long as the temperature is adjusted by cooling or heating.

  Also, in application as a heat pump air conditioner, the air to be introduced into the air conditioner is not limited to the outside air OA, but the return air from the air-conditioning target space 5, the mixed air of the return air and the outside air, or Moreover, the intake air from another room, the delivery air from another apparatus, etc. may be sufficient.

  The heat absorption source that exchanges heat with the refrigerant r in the heat absorption evaporator E2 and the heat radiation source that exchanges heat with the refrigerant r in the heat radiation condenser C2 are also air Aa and Ab such as outside air, exhaust gas from other equipment, etc. Any gas may be used, and it may be a liquid such as river water, well water, or waste water, or a solid such as soil or skeleton.

  In the above-described embodiment, the diversion ratio adjusting means on the evaporation side that adjusts the diversion ratio between the refrigerant r that passes through the cooling evaporator E1 and the refrigerant r that passes through the endothermic evaporator E2 is provided for each of the evaporators E1 and E2. Although an example in which the expansion valves Ex1 and Ex2 are configured has been shown, the diversion ratio adjustment means on the evaporation side is configured by using other types of valve devices such as a dedicated flow rate adjustment valve and a three-way valve for adjusting the diversion ratio. May be.

  Further, in the above-described embodiment, the flow rate adjustment means for adjusting the diversion ratio on the condensing side that adjusts the diversion ratio between the refrigerant r that passes through the heating condenser C1 and the refrigerant r that passes through the heat dissipation condenser C2 Although an example in which the valves Mv1 and Mv2 are configured has been described, the condensing side diversion ratio adjusting means may be configured by using other types of valve devices such as a three-way valve for adjusting the diversion ratio.

  In the above-described embodiment, the refrigerant r discharged from the compressor Cmp is divided into two flows, one of the divided refrigerants r is passed through the heating condenser C1, and the other divided refrigerant r and the heating condenser C1. The refrigerant r sent out from the refrigerant is merged and passed through the heat radiation condenser C2. After the refrigerant r discharged from the compressor Cmp is divided into two streams, one refrigerant refrigerant r is heated to the condenser for heating. While passing through C1, the other shunt refrigerant r may be passed through the heat dissipation condenser C2, and the two shunt refrigerants r may be merged after being sent out from the condensers C1 and C2.

In the above-described embodiment, an example in which the cooling evaporator E1 and the heating condenser C1 are separately provided has been described. However, in some cases, a dual-purpose apparatus that serves as both the cooling evaporator E1 and the heating condenser C1 is provided. ,
In the cooling operation, the dual function device may function as the cooling dehumidifier E1, and in the heating operation, the dual function device may function as the heating condenser C1.

  The heat pump type temperature control device according to the present invention is not limited to an air conditioner and can be used for various applications in various fields.

Cmp Compressor r Refrigerant RC Refrigerant circuit OA Outside air (fluid)
E1 Cooling evaporator Ab Absorption air (endothermic source)
E2 Evaporator for heat absorption C1 Condenser for heating Aa Heat release air (heat release source)
C2 Heat radiation condenser Ex1 Cooling expansion valve (Evaporation side diversion ratio adjustment means)
Ex2 endothermic expansion valve (evaporation side diversion ratio adjusting means)
Mv1 Heating flow rate adjustment valve (Condensation-side diversion ratio adjustment means)
Mv2 Heat dissipation flow adjustment valve (Condensation-side diversion ratio adjustment means)
G Compressor output

Claims (5)

Provided with a vapor compression refrigerant circuit that circulates refrigerant with a compressor,
A heat pump temperature control device that enables switching between a cooling operation for processing a cooling load of a fluid and a heating operation for processing a heating load of the fluid,
As an evaporator in the refrigerant circuit, a cooling evaporator as a fluid cooler for exchanging heat between the refrigerant and the fluid, and an endothermic evaporator for exchanging heat between the refrigerant and an endothermic source are provided separately.
As the condenser in the refrigerant circuit, a heating condenser as a fluid heater for exchanging heat between the refrigerant and the fluid, and a heat dissipating condenser for exchanging heat between the refrigerant and a heat radiation source are provided separately.
Providing an evaporation-side diversion ratio adjusting means for adjusting a diversion ratio between the refrigerant that passes through the cooling evaporator and the refrigerant that passes through the endothermic evaporator;
Independently of the diversion ratio adjustment by the diversion ratio adjustment means on the evaporation side, the diversion ratio adjustment on the condensation side that adjusts the diversion ratio between the refrigerant that passes through the heating condenser and the refrigerant that passes through the heat dissipation condenser A heat pump type temperature control device provided with means. As the cooling operation, in the state where the flow rate ratio of the refrigerant passing through the cooling evaporator is maximized in the diversion ratio adjustment by the diversion ratio adjustment means on the evaporation side, the output of the compressor is set to the cooling load of the fluid. Normal cooling operation to adjust according to,
With the output of the compressor minimized, the diversion ratio between the refrigerant passing through the cooling evaporator and the refrigerant passing through the endothermic evaporator is determined according to the cooling load of the fluid. Selectively performing the low-load cooling operation adjusted by the adjusting means,
As the heating operation, in the state where the flow rate ratio of the refrigerant passing through the heating condenser in the diversion ratio adjustment by the condensing side diversion ratio adjusting means is maximized, the output of the compressor is set to the heating load of the fluid. Normal heating operation to adjust according to,
In the state where the output of the compressor is minimized, the diversion ratio between the refrigerant that passes through the heating condenser and the refrigerant that passes through the heat dissipation condenser depends on the heating load of the fluid. The heat pump type temperature control device according to claim 1, wherein the low load heating operation adjusted by the adjusting means is selectively performed. During the implementation of the normal cooling operation, when the output of the compressor is minimized, switching to the low-load cooling operation is performed,
During the execution of the low load cooling operation, when the flow rate ratio of the refrigerant passing through the cooling evaporator is maximized in the diversion ratio adjustment by the evaporation diversion ratio adjustment means, the switching to the normal cooling operation is performed. Run
During the implementation of the normal heating operation, when the output of the compressor is minimized, switching to the low load heating operation is performed,
During the execution of the low load heating operation, when the flow rate ratio of the refrigerant passing through the heating condenser is maximized in the diversion ratio adjustment by the condensing side diversion ratio adjusting means, switching to the normal heating operation is performed. The heat pump type temperature control device according to claim 2, wherein   The refrigerant circuit divides the refrigerant discharged from the compressor into two flows, passes one of the divided refrigerants through the heating condenser, and condenses sent from the other divided refrigerant and the heating condenser. The heat pump type temperature control device according to any one of claims 1 to 3, wherein a refrigerant is combined and passed through the heat dissipation condenser. The fluid is air;
In the cooling operation, the air is cooled and dehumidified in the cooling evaporator, and subsequently, the cooled and dehumidified air is reheated to a required temperature in the heating condenser. The heat pump type temperature control apparatus according to any one of the above.

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