HEAT PUMP CYCLE

• US 20130312447A1
• Filed: 02/10/2012
• Published: 11/28/2013
• Est. Priority Date: 02/11/2011
• Status: Active Grant

• Current Assignee: DENSO Corporation
• Original Assignee: DENSO Corporation
• Inventors: Inaba, Atsushi, Itoh, Satoshi
• Granted Patent: US 9,441,865 B2
• Time in Patent Office: Days
• US Class Current: 62/324.6
• CPC Class Codes: B60H 1/00921 where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
• CPC Class Codes: B60H 1/3223 characterised by the arrangement or type of the compressor B60H1/3222 takes precedence
• CPC Class Codes: F24F 11/30 for purposes related to the operation of the system, e.g. for safety or monitoring
• CPC Class Codes: F24F 11/62 characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
• CPC Class Codes: F24F 11/65 for selecting an operating mode
• CPC Class Codes: F24F 11/67 Switching between heating and cooling modes
• CPC Class Codes: F24F 11/84 using valves
• CPC Class Codes: F24F 11/86 by controlling compressors within refrigeration or heat pump circuits
• CPC Class Codes: F24F 2140/00 Control inputs relating to system states
• CPC Class Codes: F24F 3/153 with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
• CPC Class Codes: F25B 2400/02 Centrifugal separation of gas, liquid or oil
• CPC Class Codes: F25B 2400/0409 for the evaporator
• CPC Class Codes: F25B 2400/0411 for the expansion valve or capillary tube
• CPC Class Codes: F25B 30/02 of the compression type
• CPC Class Codes: F25B 41/24 Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
• CPC Class Codes: F25B 41/39 Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
• CPC Class Codes: F25B 43/00 Arrangements for separating or purifying gases or liquids in analysers or rectifiers F25B33/00; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat F25B40/00 takes precedence
• CPC Class Codes: F25B 49/02 for compression type machines, plants or systems

Abstract

A heat pump cycle is capable of switching an operation mode to a cooling operation mode, a heating operation mode and a dehumidifying-heating operation mode, and is applicable to an air conditioning device. The heat pump cycle is configured to set both of a high-pressure side pressure reducing device and a low-pressure side pressure reducing device—in a throttled state and a fully open state. In this way, the heat pump cycle realizes cooling, heating, and dehumidifying-heating by a simple structure without providing separate refrigerant flow passages extended from a compressor to an outside heat exchanger based on the operation modes of the air conditioning device.

Claims

1. A heat pump cycle capable of switching an operation mode to a cooling operation mode, a heating operation mode, and a dehumidifying-heating operation mode, and applicable to an air conditioning device, the heat pump cycle comprising:

a compressor sucking, compressing and discharging a refrigerant;

a first usage side heat exchanger making a high pressure refrigerant discharged from a discharge port of the compressor exchange heat with air to be blown into a space to be air-conditioned or exchange heat with a heating medium for heating the air;

a first pressure reducing portion configured to reduce pressure of the refrigerant flowing out of the first usage side heat exchanger;

a gas-liquid separation portion separating gas and liquid of the refrigerant having passed through the first pressure reducing portion;

a second pressure reducing portion configured to reduce pressure of a liquid-phase refrigerant separated by the gas-liquid separation portion;

an outside heat exchanger making the refrigerant passing the second pressure reducing portion exchange heat with an outside air;

a second usage side heat exchanger making the refrigerant exchange heat with the air to be blown into the space and making the refrigerant flow out toward a suction port of the compressor;

a third pressure reducing portion reducing pressure of the refrigerant flowing into the second usage side heat exchanger;

an intermediate pressure refrigerant passage guiding a gas-phase refrigerant separated by the gas-liquid separation portion to an intermediate pressure port provided in the compressor to thereby mix the gas-phase refrigerant with the refrigerant in a compression process of the compressor; and

a refrigerant flow passage switching device switching a refrigerant flow passage of the refrigerant circulated in the cycle,

wherein each of the first pressure reducing portion and the second pressure reducing portion is configured to be set not only in a throttled state in which each of the first pressure reducing portion and the second pressure reducing portion performs a pressure reducing operation but also in a fully open state in which each of the first pressure reducing portion and the second pressure reducing portion does not perform the pressure reducing operation.

2. The heat pump cycle as in claim 1, wherein

in the heating operation mode, both of the first pressure reducing portion and the second pressure reducing portion are set in the throttled state,

in the cooling operation mode, both of the first pressure reducing portion and the second pressure reducing portion are set in the fully open state, and

in the humidifying-heating operation mode, at least one of the first pressure reducing portion and the second pressure reducing portion is set in the fully open state.

3. The heat pump cycle as in claim 2, wherein

in the heating operation mode, the refrigerant flow passage switching device causes the refrigerant discharged from the compressor to flow through the first usage side heat exchanger→

the first pressure reducing portion→

the gas-liquid separation portion→

the second pressure reducing portion→

the outside heat exchanger in sequence and causes the gas-phase refrigerant separated by the gas-liquid separation portion to flow into the intermediate pressure refrigerant passage,

in the cooling operation mode, the refrigerant flow passage switching device causes the refrigerant discharged from the compressor to flow through the first pressure reducing portion→

the gas-liquid separation portion→

the second pressure reducing portion→

the outside heat exchanger→

the third pressure reducing portion→

the second usage side heat exchanger in sequence, and

in the dehumidifying-heating operation mode, the refrigerant flow passage switching device causes the refrigerant discharged from the compressor to flow through the first usage side heat exchanger→

the first pressure reducing portion→

the gas-liquid separation portion→

the second pressure reducing portion→

the outside heat exchanger→

the third pressure reducing portion→

the second usage side heat exchanger in sequence.

4. The heat pump cycle as in claim 2, wherein

the refrigerant flow passage switching device includes an intermediate pressure side opening/closing valve for opening and closing the intermediate pressure refrigerant passage.

5. The heat pump cycle as in claim 4, wherein

the intermediate pressure side opening/closing valve is configured to open the intermediate pressure refrigerant passage when both of the first pressure reducing portion and the second pressure reducing portion are set in the throttled state, and to close the intermediate pressure refrigerant passage when at least one of the first pressure reducing portion and the second pressure reducing portion is set in the fully open state.

6. The heat pump cycle as in claim 5, wherein

the intermediate pressure side opening/closing valve is a pressure difference opening/closing valve that is open and closed according to a pressure difference between before and after the second pressure reducing portion, which is set in the fully open state in the dehumidifying-heating operation mode, of the first pressure reducing portion and the second pressure reducing portion.

7. The heat pump cycle as in claim 1, wherein

one of the first pressure reducing portion and the second pressure reducing portion is constructed of a variable throttle mechanism capable of varying a throttle opening,

the third pressure reducing portion is constructed of a variable throttle mechanism capable of varying a throttle opening, and

in the dehumidifying-heating operation mode, the other of the first pressure reducing portion and the second pressure reducing portion is set in the fully open state, and the one of the first pressure reducing portion and the second pressure reducing portion has its throttle opening that is changed to decrease in accordance with an increase in a target temperature of air to be blown into the space and the third pressure reducing portion has its throttle opening changed to increase in accordance with the increase in the target temperature of air to be blown into the space.

8. The heat pump cycle as in claim 1,

wherein at least one of the first pressure reducing portion and the second pressure reducing portion includes a fixed throttle having a fixed throttle opening, a fixed throttle bypassing passage through which the refrigerant flows while bypassing the fixed throttle, and a passage opening/closing valve for opening and closing the fixed throttle bypassing passage.

9. The heat pump cycle as in claim 1, wherein

the first pressure reducing portion is constructed of a variable throttle mechanism capable of varying a throttle opening, and

the second pressure reducing portion is constructed of a fixed throttle having a fixed throttle opening, a fixed throttle bypassing passage through which the refrigerant bypasses the fixed throttle, and a passage opening/closing valve for opening and closing the fixed throttle bypassing passage.

10. The heat pump cycle as in claim 1, further comprising

an accumulator for separating gas and liquid of the refrigerant flowing toward the suction port of the compressor and for causing a separated gas-phase refrigerant to flow into a side of the suction port of the compressor, wherein

the gas-liquid separation portion is configured to make a separated liquid-phase refrigerant not remain therein but flow out of a liquid-phase refrigerant outlet of the gas-liquid separation portion.

11. The heat pump cycle as in claim 1, further comprising

an accumulator for separating gas and liquid of the refrigerant flowing toward the suction port of the compressor and for causing a separated gas-phase refrigerant to flow into a side of the suction port of the compressor,

wherein the gas-liquid separation portion has a liquid-phase refrigerant outlet through which a liquid-phase refrigerant just after separation is made to flow out.

12. The heat pump cycle as in claim 1, further comprising:

an accumulator for separating gas and liquid of the refrigerant flowing toward the suction port of the compressor and for causing a separated gas-phase refrigerant to flow into a side of the suction port of the compressor, wherein

the gas-liquid separation portion has a liquid-phase refrigerant outlet through which the liquid-phase refrigerant just after separation is made to flow out, and

an inner volume of the gas-liquid separation portion is smaller than a volume of an excess refrigerant, which is acquired by subtracting a necessary maximum refrigerant volume when an amount of refrigerant necessary for the cycle to perform a maximum capacity is converted into a liquid-phase refrigerant, from a volume of a charged refrigerant when an amount of refrigerant charged into the cycle is converted into a liquid-phase refrigerant.

13. The heat pump cycle as in claim 10,

wherein the gas-liquid separation portion is a centrifugal-separation type gas-liquid separator in which gas and liquid of the refrigerant is separated by a centrifugal force.

14. The heat pump cycle as in claim 10,

wherein the liquid-phase refrigerant outlet is positioned on a lower side than a gas-phase refrigerant outlet through which the gas-phase refrigerant separated by the gas-liquid separation portion is made to flow out, and the liquid-phase refrigerant outlet makes a part of the gas-phase refrigerant flow out together with the liquid-phase refrigerant.

15. The heat pump cycle as in claim 12,

wherein the liquid-phase refrigerant outlet is opened and closed by a float valve that is displaced according to a height of a liquid level of the liquid-phase refrigerant in the gas-liquid separation portion.

16. The heat pump cycle as in claim 12,

wherein the gas-liquid separation portion is a surface-tension type gas-liquid separator in which gas and liquid of the refrigerant is separated by using a surface tension of the liquid-phase refrigerant.

17. The heat pump cycle as in claim 1,

wherein a quality fraction dryness of the refrigerant flowing into the outside heat exchanger is 0.1 or less in a heating operation mode.

18. The heat pump cycle as in claim 1,

wherein the first usage side heat exchanger is a heat exchanger in which the high pressure refrigerant discharged from the discharge port of the compressor exchanges heat with the air to be blown into the space.

19. The heat pump cycle as in claim 1,

wherein the first usage side heat exchanger is a heat exchanger in which the high pressure refrigerant discharged from the discharge port of the compressor exchanges heat with a heating medium for heating the air.

20. The heat pump cycle as in claim 18,

wherein in the heating operation mode, the air heated by the first usage side heat exchanger is blown to the space to be air-conditioned.

21. The heat pump cycle as in claim 18, further comprising

a heat exchange capacity regulation portion regulating a heat exchange capacity of the first usage side heat exchanger, wherein

in the cooling operation mode, the heat exchange capacity regulation portion reduces a heat exchange capacity in the first usage side heat exchanger such that the air cooled by the second usage side heat exchanger is blown to the space to be air-conditioned.

22. The heat pump cycle as in claim 18, wherein

the second usage side heat exchanger is arranged at an upstream side of the first usage side heat exchanger in an air flow, and

in the dehumidifying-heating operation mode, the air cooled by the second usage side heat exchanger is heated by the first usage side heat exchanger and is blown to the space to be air-conditioned.

23. The heat pump cycle as in claim 17,

wherein the second pressure reducing portion is a fixed throttle made of a nozzle or an orifice.