JP2015017773A - Refrigeration cycle device and clothes drying device using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the performance of a refrigeration cycle device and a clothes drying device using the refrigeration cycle device while restraining an increase in the number of components and an increase in costs.SOLUTION: A refrigeration cycle device comprises: a main refrigerant circuit 10 including a compressor 2, a first heat exchanger 3, a first thin tube 4 such as a capillary tube, and a second heat exchanger 6, and formed by connecting these components in a circular pattern in this order; at least one bypass circuit 20 branching from the middle of a refrigerant passage of the first heat exchanger 3 of the main refrigerant circuit 10 and joining the main refrigerant circuit 10 between the first thin tube 4 and the second heat exchanger 6; and a second thin tube 22 in the middle of a passage of the bypass circuit 20.

Description

  The present invention relates to a refrigeration cycle apparatus and a clothes drying apparatus using the refrigeration cycle apparatus.

  As means for improving the efficiency of a refrigeration cycle using a small diameter tube such as a capillary tube as the expansion means, a plurality of small diameter tubes are installed between the condenser and the evaporator, and one or more small diameter tubes are connected. A technique is known in which a bypass circuit having a valve that can be opened and closed, such as a solenoid valve installed in parallel, is provided so that a small-diameter pipe that allows a refrigerant to pass can be selected in accordance with a change in capacity of the refrigeration cycle apparatus. (For example, refer to Patent Document 1).

  Patent Document 1 discloses a refrigeration cycle apparatus of the dehumidifying apparatus shown in FIG. The refrigeration cycle apparatus 100 includes a compressor 101, a condenser 102, a first capillary tube 103, a second capillary tube 104, and a main refrigerant circuit 110 in which an evaporator 105 is connected in an annular shape. Further, a bypass circuit 111 having an electromagnetic valve 106 that branches from between the condenser 102 and the first capillary tube 103 and merges with the main refrigerant circuit 110 between the first capillary tube 103 and the second capillary tube 104 is provided. doing. By opening the electromagnetic valve 106 of the bypass circuit 111 and flowing the refrigerant through the bypass circuit 111, the amount of refrigerant circulating increases, the refrigeration capacity of the refrigeration cycle apparatus 100 increases and the dehumidification capacity also increases. In addition, it is possible to prevent liquid refrigerant accumulation in the condenser 102.

JP 59-164857 A

  In the refrigeration cycle apparatus 100 used in the dehumidification apparatus described in Patent Document 1, a bypass circuit 111 in which the electromagnetic valve 106 is installed and a control device that controls the electromagnetic valve 106 are required in accordance with the fluctuation in the capacity of the refrigeration cycle apparatus 100. Therefore, there are problems that increase the number of parts used in the refrigeration cycle apparatus 100, increase the arrangement space, increase the cost of the refrigeration cycle apparatus, and the like.

  In view of such circumstances, an object of the present invention is to improve the performance of a refrigeration cycle apparatus and a clothing drying apparatus using the refrigeration cycle apparatus by suppressing an increase in the number of parts and cost increase.

  In order to solve the conventional problems, the refrigeration cycle apparatus of the present invention includes a compressor, a first heat exchanger, a first small diameter tube, and a second heat exchanger, and these components are arranged in this order. A main refrigerant circuit formed by being connected in a ring shape, and a branch from the middle of the refrigerant path of the first heat exchanger of the main refrigerant circuit, between the first small diameter tube and the second heat exchanger Alternatively, at least one bypass circuit joined to the main refrigerant circuit between the first small diameter tube and the first compressor, and a second small diameter tube in the middle of the bypass circuit.

With this configuration, the capacity of the refrigeration cycle apparatus is increased by the bypass circuit that branches off from the middle of the refrigerant path of the first heat exchanger and joins the main refrigerant circuit between the first small-diameter pipe and the second heat exchanger. It is possible to reduce the accumulation of liquid refrigerant in the first heat exchanger that occurs when Accordingly, it is possible to reduce the pressure increase on the high-pressure side of the refrigeration cycle and at the same time reduce the excessive degree of superheat of the refrigerant at the outlet of the second heat exchanger. This improves the performance of the refrigeration circuit. In addition, during low load operation where the capacity of the refrigeration cycle apparatus is low, the refrigerant on the bypass circuit inlet side is in a two-phase state, so that almost no refrigerant flows through the bypass circuit. For this reason, during low load operation, the refrigerant circulates only in the main refrigerant circuit, so there is no adverse effect on the refrigeration cycle during low load operation. These enable efficient refrigeration cycle operation that matches the load fluctuations of the refrigeration cycle without using a bypass circuit with an electromagnetic valve or an expansion mechanism with an adjustable opening such as an electronic expansion valve in the main refrigerant circuit. The energy-saving performance of the refrigeration cycle apparatus is improved. And the increase in a number of parts and cost increase can be suppressed, and the performance of a refrigerating cycle device can be improved.

  The refrigeration cycle apparatus of the present invention occurs when the capacity of the refrigeration cycle apparatus is increased by a bypass circuit that branches from the middle of the refrigerant path of the first heat exchanger and merges with the main refrigerant circuit after the first small-diameter pipe. The liquid refrigerant pool in the first heat exchanger can be reduced, and the performance of the refrigeration circuit is improved. In addition, efficient refrigeration cycle operation can be performed according to the load fluctuation of the refrigeration cycle without using a bypass circuit with a solenoid valve or an expansion mechanism with adjustable opening such as an electronic expansion valve in the main refrigerant circuit. The energy saving performance of the refrigeration cycle device is improved. And the increase in a number of parts and cost increase can be suppressed, and the performance of a refrigerating cycle device can be improved.

Configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention. The block diagram of the washing-drying machine which concerns on Embodiment 2 of this invention Configuration diagram of the refrigeration cycle device of the washer / dryer Configuration diagram of conventional refrigeration cycle equipment

  The refrigeration cycle apparatus of the first invention has a compressor, a first heat exchanger, a first small-diameter tube such as a capillary tube, and a second heat exchanger, and these components are connected in an annular shape in this order. A main refrigerant circuit formed by the operation of the first heat exchanger of the main refrigerant circuit, and the main refrigerant circuit joins the main refrigerant circuit between the first small-diameter pipe and the compressor. And at least one bypass circuit, and a second small diameter tube in the middle of the bypass circuit.

  With this configuration, the capacity of the refrigeration cycle apparatus is increased by the bypass circuit that branches off from the middle of the refrigerant path of the first heat exchanger and joins the main refrigerant circuit between the first small-diameter pipe and the second heat exchanger. It is possible to reduce the accumulation of liquid refrigerant in the first heat exchanger that occurs when Accordingly, it is possible to reduce the pressure increase on the high-pressure side of the refrigeration cycle and at the same time reduce the excessive degree of superheat of the refrigerant at the outlet of the second heat exchanger. This improves the performance of the refrigeration circuit. In addition, during low load operation where the capacity of the refrigeration cycle apparatus is low, the refrigerant on the bypass circuit inlet side is in a two-phase state, so that almost no refrigerant flows through the bypass circuit. For this reason, during low load operation, the refrigerant circulates only in the main refrigerant circuit, so there is no adverse effect on the refrigeration cycle during low load operation. These enable efficient refrigeration cycle operation that matches the load fluctuations of the refrigeration cycle without using a bypass circuit with an electromagnetic valve or an expansion mechanism with an adjustable opening such as an electronic expansion valve in the main refrigerant circuit. The energy-saving performance of the refrigeration cycle apparatus is improved. And the increase in a number of parts and cost increase can be suppressed, and the performance of a refrigerating cycle device can be improved.

In a second aspect based on the first aspect, the bypass circuit joins the main refrigerant circuit between the first small diameter tube and the second heat exchanger. According to this configuration, since all the circulating refrigerant passes through the second heat exchanger, the energy saving performance of the refrigeration cycle apparatus can be improved without reducing the cooling capacity of the refrigeration cycle apparatus.

  A clothing drying apparatus according to a third aspect of the present invention includes the refrigeration cycle apparatus according to the first aspect of the present invention, and a rotating tub that is rotatably provided to store the clothes, and from the first heat exchanger of the refrigeration cycle apparatus. A blower for circulating air to the rotating tank is provided. According to this structure, the energy-saving performance of the clothing drying apparatus and the clothes drying speed are improved by improving the energy-saving performance of the refrigeration cycle apparatus mounted on the clothes drying apparatus.

  According to a fourth aspect of the present invention, there is provided a clothes drying apparatus comprising: the refrigeration cycle apparatus according to the second aspect of the invention described above; and a rotating tub that is rotatably provided to store clothes, and the first heat exchanger of the refrigeration cycle apparatus. A blower for circulating air to the rotating tank is provided. According to this structure, the energy-saving performance of the clothing drying apparatus and the clothes drying speed are improved by improving the energy-saving performance of the refrigeration cycle apparatus mounted on the clothes drying apparatus.

  According to a fifth invention, in the third or fourth invention, the first temperature sensor that measures the temperature of the refrigerant at the outlet of the first small-diameter tube and the refrigerant temperature at the outlet of the second small-diameter tube are measured. A second temperature sensor, and a controller for controlling the rotational speed of the compressor of the refrigeration cycle apparatus based on the measurement results of the first temperature sensor and the second temperature sensor. According to this configuration, the energy saving performance of the refrigeration cycle apparatus can be improved by adjusting the rotation speed of the compressor based on the measurement results of the first temperature sensor and the second temperature sensor.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the following embodiments.

(Embodiment 1)
FIG. 1 shows a refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention. The refrigeration cycle apparatus 1 includes a main refrigerant circuit 10, a bypass circuit 20, and a controller 7. The main refrigerant circuit 10 includes a compressor 2, a first heat exchanger 3, a first small diameter tube 4, and a second heat exchanger 6. The main refrigerant circuit 10 is a refrigerant circuit formed by connecting these components in an annular shape in this order. The bypass circuit 20 branches from the main refrigerant circuit 10 at a branch position 21 in the middle of the path of the first heat exchanger 3, and the main refrigerant at a junction position 24 between the first small diameter tube 4 and the second heat exchanger 6. This is a refrigerant circuit joined to the circuit 10. Here, the 1st small diameter pipe | tube 4 is a capillary tube in which opening degree adjustment is impossible, for example. During operation of the refrigeration cycle apparatus 1, the refrigerant circulates through the main refrigerant circuit 10 and the bypass circuit 20. As the refrigerant, for example, a non-azeotropic refrigerant mixture such as R407C, a pseudo-azeotropic refrigerant mixture such as R410A, or a single refrigerant can be used.

  Next, taking the refrigeration cycle apparatus 1 as an example, the flow of the refrigerant in the main refrigerant circuit 10 of the refrigeration cycle apparatus 1 will be described. The superheated high-pressure gas refrigerant compressed by the compressor 2 is discharged from the compressor 2, flows through the flow path 10 </ b> A, and flows into the first heat exchanger 3. The refrigerant is cooled when it flows through the first heat exchanger 3. Therefore, in the flow path 10B between the first heat exchanger 3 and the first small diameter tube 4, the refrigerant is a supercooled high-pressure liquid refrigerant. The refrigerant expands in the first small-diameter tube 4 to be in a low pressure state, and flows into the second heat exchanger 6 through the flow path 10C. The refrigerant evaporates when it flows through the second heat exchanger 6 and cools the surroundings. The refrigerant that has flowed out of the second heat exchanger 6 is sucked into the compressor 2 through the flow path 10 </ b> D and is compressed again in the compressor 2. In this way, the refrigerant circulates through the main refrigerant circuit 10.

As shown in FIG. 1, the bypass circuit 20 branches from the main refrigerant circuit 10 at a branch position 21 in the middle of the refrigerant path of the first heat exchanger 3. Further, the bypass circuit 20 merges with the main refrigerant circuit 10 at a merge position 24 between the first small diameter tube 4 and the second heat exchanger 6. A part of the refrigerant flowing through the first heat exchanger 3 flows through the bypass circuit 20 and joins the refrigerant flowing through the main refrigerant circuit 10 between the first small diameter pipe 4 and the compressor 2. By connecting this bypass circuit 20 to the main refrigerant circuit 10 between the first small-diameter pipe 4 and the compressor 2, the amount of refrigerant flowing through the main refrigerant circuit 10 increases. Therefore, the pressure of the refrigerant flowing from the compressor 2 through the first heat exchanger 3 is reduced.

  The bypass circuit 20 includes a second small diameter tube 22. The second small diameter tube 22 is, for example, a capillary tube whose opening degree cannot be adjusted. One end of the bypass circuit 20 is connected in the middle of the refrigerant circuit of the first heat exchanger 3, and the other end of the bypass circuit 20 is connected to the main refrigerant circuit 10 between the first small diameter pipe 4 and the compressor 2. That's fine. Alternatively, a plurality of bypass circuits 20 may be provided by changing the position of the branch position 21. When the bypass circuit 20 is configured in this way, the supercooling temperature of the refrigerant cooled when flowing through the first heat exchanger 3 at the branch position 21 of the first heat exchanger 3 is large due to the characteristics of the refrigerant. In the case of liquid refrigerant, the refrigerant flows smoothly to the bypass circuit 20. As a result, the first heat exchanger 3 liquid refrigerant accumulation can be prevented. As a result, the pressure of the refrigerant flowing from the compressor 2 through the first small diameter tube 4 can be reduced.

  Furthermore, when the refrigerant cooled when flowing through the first heat exchanger 3 at the branch position 21 of the first heat exchanger 3 is in a two-phase state or a state with a low degree of supercooling, to the bypass circuit 20 Only a very small amount of refrigerant flows. As a result, the flow rate of the refrigerant flowing through the main refrigerant circuit 10 is naturally adjusted according to the state of the refrigerant at the branch position 21 of the first heat exchanger 3 without using a valve whose opening degree can be adjusted, such as an electronic expansion valve. The energy saving performance of the refrigeration cycle apparatus 1 can be improved.

  Generally, when an expansion device using a capillary tube, for example, is used between the first heat exchanger 3 and the second heat exchanger 6, the opening degree of the expansion device cannot be adjusted in accordance with a change in the capacity of the refrigeration cycle device. Therefore, as the capacity change of the refrigeration cycle apparatus 1, for example, the pressure on the high pressure side of the refrigeration cycle increases with an increase in the compressor rotation speed, the supercooling temperature of the refrigerant flowing through the first heat exchanger 3 increases. The performance of the refrigeration cycle is reduced.

  According to the first embodiment, the flow rate of the refrigerant flowing through the main refrigerant circuit 10 and the bypass circuit 20 varies depending on the state of the refrigerant at the branch position 21 of the first heat exchanger 3. Therefore, it is particularly effective when the capacity of the refrigeration cycle apparatus is greatly changed.

  Moreover, in order to improve the energy saving performance of the refrigeration cycle apparatus 1 without reducing the cooling capacity in the second heat exchanger 6, the outlet of the bypass circuit 20 is connected to the first small diameter pipe 4 and the second heat exchange. It is desirable that the main refrigerant circuit is joined between the vessels 6.

  Further, the refrigeration cycle apparatus 1 includes the first temperature sensor 5 in the middle of the flow path between the first small diameter tube 4 and the merge position 24, and the second temperature sensor 23 between the second small diameter tube 22 and the merge position 24. , And the temperature of the refrigerant that has expanded into a low-pressure state in each small-diameter tube is measured.

  When the temperature difference measured by the first temperature sensor 5 and the second temperature sensor 23 is large, the refrigerant does not flow through the second small-diameter pipe 22, so that the rotation speed of the compressor 2 can be increased. When the temperature difference is small, the refrigerant flows into the second small-diameter pipe 22, and therefore the rotational speed of the compressor 2 is not increased. Thus, the energy-saving performance of the refrigeration cycle apparatus can be improved by adjusting the rotation speed of the compressor based on the measurement results of the first temperature sensor and the second temperature sensor.

With these configurations, the capacity of the refrigeration cycle apparatus is increased by a bypass circuit that branches off from the middle of the refrigerant path of the first heat exchanger and joins the main refrigerant circuit between the first small diameter pipe and the second heat exchanger It is possible to reduce the accumulation of liquid refrigerant in the first heat exchanger, which occurs when it is made to occur. Accordingly, it is possible to reduce the pressure increase on the high-pressure side of the refrigeration cycle and at the same time reduce the excessive degree of superheat of the refrigerant at the outlet of the second heat exchanger. This improves the performance of the refrigeration circuit. In addition, during low load operation where the capacity of the refrigeration cycle apparatus is low, the refrigerant on the bypass circuit inlet side is in a two-phase state, so that almost no refrigerant flows through the bypass circuit. For this reason, during low load operation, the refrigerant circulates only in the main refrigerant circuit, so there is no adverse effect on the refrigeration cycle during low load operation. These enable efficient refrigeration cycle operation that matches the load fluctuations of the refrigeration cycle without using a bypass circuit with an electromagnetic valve or an expansion mechanism with an adjustable opening such as an electronic expansion valve in the main refrigerant circuit. The energy-saving performance of the refrigeration cycle apparatus is improved. And the increase in a number of parts and cost increase can be suppressed, and the performance of a refrigerating cycle device can be improved.

(Embodiment 2)
A washing / drying machine equipped with the refrigeration cycle apparatus according to Embodiment 2 will be described with reference to FIGS. Note that the refrigeration cycle apparatus 1 is configured in the same manner as the refrigeration cycle apparatus 1 according to Embodiment 1 except for parts specifically described below. Moreover, although it demonstrates using a washing-drying machine, a washing-drying machine is contained in a clothing drying apparatus.

  In FIG. 2, a rotating tub 31 that accommodates clothing is rotatably disposed in a water tub 33 that is swingably supported in a housing 32. A drive motor 36 is attached to the rear surface of the water tank 33 to rotate the rotation axis of the rotary tank 31 so as to tilt upward. The rotary tank 31 is rotated by the drive motor 36 and is put into the rotary tank 31. Stir and wash the clothes that have been put on and dry.

  A door body 45 is provided at the front of the housing 32 so as to face the opening end side of the rotating tub 31, and the user opens the door body 45 so that the laundry ( Clothes). A water supply pipe 44 provided with a water supply valve 43 is connected to the upper part of the water tank 33, and a drain pipe 42 provided with a drain valve 41 is connected to the lowermost part of the water tank 33. Below the water tank 33, there is provided a damper 34 that supports the water tank 33 and attenuates vibrations of the water tank 33 that are generated due to uneven clothing in the rotating tank 31 during dehydration. The damper 34 has a cloth amount detection unit (not shown) that detects the amount of clothing by detecting the amount of displacement of the shaft of the damper 34 up and down due to the weight change caused by the clothing in the water tank 33 to be supported. It is attached.

  In order to dry clothes in a drying process, the air path 37 which circulates the air for drying in the water tank 33 and the rotating tank 31 with the air blower fan 35 of an air blower is comprised. In the air path 37, two heat exchangers of the refrigeration cycle apparatus 1 are incorporated. The drying air that has taken moisture from the laundry in the rotating tub 31 and has become humid is passed through the discharge port 46 provided in the upper side surface of the water tub 33, and in the second heat exchanger 6 of the refrigeration cycle apparatus 1. Cooled and dehumidified. The drying air cooled and dehumidified by the second heat exchanger 6 is heated by the first heat exchanger 3 of the refrigeration cycle apparatus 1. The heated drying air passes through the blowout port 38 from the blower fan 35 disposed in the middle of the air passage 37 and blows out again into the rotary tank 31.

  In addition, an inflow temperature detection unit 39 such as a thermistor for detecting the temperature of the drying air flowing into the rotary tank 31 is provided, and the inflow temperature detection unit 39 is in the vicinity of the air outlet 38 of the air passage 37 or the first heat exchanger. 3 is provided in the vicinity. The blower fan motor 40 rotationally drives the blower fan 35 that works during drying. Further, the rotation operation of the blower fan motor 40 such as a rotation speed is controlled by a controller such as an inverter.

The operation of the washing / drying machine configured as described above will be described below. When the pressure and temperature on the high-pressure side of the refrigeration cycle increase due to an increase in the temperature of the drying air or an increase in the cooling capacity (dehumidification capacity) of the washing dryer, a liquefied refrigerant pool is likely to occur in the first heat exchanger 3, This reduces the energy efficiency of the refrigeration cycle apparatus. At this time, when the liquid refrigerant reaches the branch position 21 of the first heat exchanger 3, the liquid refrigerant pool of the first heat exchanger 3 can be reduced using the bypass circuit 20. As the temperature of the drying air rises, it is possible to reduce the pressure increase on the high-pressure side of the refrigeration cycle and at the same time reduce the excessive degree of superheat of the refrigerant at the outlet of the second heat exchanger 6. This improves the performance of the refrigeration circuit.

  Further, when the drying proceeds and the refrigeration cycle apparatus has a low capacity and the load is low, the refrigerant at the inlet side of the bypass circuit is in a two-phase state, so that the refrigerant hardly flows through the bypass circuit. For this reason, during low load operation, the refrigerant circulates only in the main refrigerant circuit, so there is no adverse effect on the refrigeration cycle during low load operation. These enable efficient refrigeration cycle operation that matches the load fluctuations of the refrigeration cycle without using a bypass circuit with an electromagnetic valve or an expansion mechanism with an adjustable opening such as an electronic expansion valve in the main refrigerant circuit. The energy-saving performance of the refrigeration cycle apparatus is improved.

  With these configurations, in the process of drying clothing, the performance of the refrigeration cycle apparatus is improved by the same effect as the refrigeration cycle apparatus according to Embodiment 1, and the energy efficiency and the drying speed of the drying process of the washing dryer are improved. Can be achieved.

  The refrigeration cycle apparatus according to the present invention can be used as a hot water heater, a hot water heating apparatus, a refrigeration apparatus and an air conditioning apparatus, a washing dryer and a clothes drying apparatus, or a refrigeration cycle apparatus for other uses.

DESCRIPTION OF SYMBOLS 1 Refrigeration cycle apparatus 2 Compressor 3 1st heat exchanger 4 1st small diameter pipe 5 1st temperature sensor 6 2nd heat exchanger 7 Controller 10 Main refrigerant circuit 20 Bypass circuit 21 Branch position 22 2nd small diameter pipe 23 Second temperature sensor 24 Junction position 31 Rotating tank 35 Blower fan

Claims (5)

A main refrigerant circuit formed by a compressor, a first heat exchanger, a first small-diameter tube such as a capillary tube, and a second heat exchanger, and these components are connected in an annular shape in this order; , At least one bypass circuit branched from the middle of the refrigerant path of the first heat exchanger of the main refrigerant circuit and joined to the main refrigerant circuit between the first small-diameter pipe and the compressor; A refrigeration cycle apparatus having a second small diameter pipe in the middle of the path of the bypass circuit. The refrigeration cycle apparatus according to claim 1, wherein the bypass circuit joins the main refrigerant circuit between the first small diameter tube and the second heat exchanger. An air blower for circulating air from the first heat exchanger of the refrigeration cycle apparatus to the rotary tank, comprising the refrigeration cycle apparatus according to claim 1 and a rotary tank that is rotatably provided and contains clothing. A clothes drying device having An air blower for circulating air from the first heat exchanger of the refrigeration cycle apparatus to the rotation tank, comprising the refrigeration cycle apparatus according to claim 2 and a rotation tank that is rotatably provided and contains clothes. A clothes drying device having A first temperature sensor for measuring the refrigerant temperature at the outlet of the first small-diameter pipe; and a second temperature sensor for measuring the refrigerant temperature at the outlet of the second small-diameter pipe, the first temperature sensor and the first The clothes drying apparatus according to claim 3, further comprising a controller that controls a rotation speed of the compressor of the refrigeration cycle apparatus based on a measurement result of the two temperature sensors.

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