DK2647928T3

DK2647928T3 - Cooling Cycle Unit

Info

Publication number: DK2647928T3
Application number: DK13166596.0T
Authority: DK
Inventors: Takashi Okazaki; Fumitake Unezaki; Tomoyoshi Oobayashi
Original assignee: Mitsubishi Electric Corp
Priority date: 2007-11-30
Filing date: 2008-11-20
Publication date: 2016-12-12
Also published as: DK2647926T3; EP2647926B1; EP2196745B1; EP2647926A2; US20100205987A1; CN101842645A; EP2196745A1; CN101842645B; EP2647926A3; ES2700938T3; EP2196745A4; JP4948374B2; DK2196745T3; ES2611980T3; CN102425872A; DK2647925T3; EP2647925B1; EP2647927A2; CN102425872B; EP2647927B1

Description

DESCRIPTION

Technical Field [0001] The present invention relates to a refrigeration cycle apparatus using an internal heat exchanger, more particularly to a refrigerant control for stably securing performance.

Background Art [0002] Descriptions will be given to prior art as follows.

[0003] Conventionally, a hot water supply apparatus is proposed as a built-in refrigeration cycle apparatus such as: a hot water supply apparatus comprising a refrigeration cycle including a compressor, a hot water supply heat exchanger, an electronic expansion valve, and a heat source side heat exchanger whose heat source is an external air, and a hot water supply cycle including a hot water supply heat exchanger and a hot water supply tank, wherein since ability control means that uses an ability-variable type compressor and ability-controls the compressor in response to changes in external environment conditions of the heat source side heat exchanger is attached, expansion valve opening degree control means for controlling an opening degree of an electronic expansion valve so as to make a discharge temperature of a compressor to be a target value in response to changes in external environment conditions (an external temperature, for example) of the heat source side heat exchanger and rotation speed control means for controlling a rotation speed of the compressor to be a target value in response to changes in the external environment conditions of the heat source side heat exchanger are attached, an opening of the electronic expansion valve is controlled so as to make the discharge temperature of the compressor becomes a target value in response to changes in the external environment conditions (an external temperature, for example) of the heat source side heat exchanger, and the rotation speed of the compressor is controlled to be a target value in response to changes in the external environment conditions of the heat source side heat exchanger, an optimal operation condition can be obtained in which a hot water supply ability and a hot water supply load further match, and a coefficient of performance (COP) can be improved and down-sizing of elements such as an heat exchanger becomes possible. (For example, refer to Patent Document 1 or US 2003/0061827) [0004] A water heater is also proposed such as: a water heater for heating a hot water supply fluid in a supercritical heat pump cycle where a refrigerant pressure in a high pressure side becomes equal to or more than the critical pressure of the refrigerant comprising: a compressor, a radiator that performs heat exchange between a refrigerant discharged from the compressor and a hot water supply fluid and is configured so that a refrigerant flow and the hot water supply fluid flow opposes, a decompressor for decompressing the refrigerant flowing out of the radiator, and an evaporator that makes the refrigerant that flows out of the compressor evaporate, makes the refrigerant absorb a heat to discharge it into a suction side of the compressor, wherein a refrigerant pressure of a high-pressure side is controlled so that a temperature difference (ΔΤ) between the refrigerant that flows out of the radiator and the hot water supply fluid that flows therein becomes a predetermined temperature difference (ΔΤο). (For example, refer to Patent Document 2) In this example of the prior art, a heat exchange efficiency of the radiator can be enhanced to improve efficiency of a heat pump.

[0005] [Patent Document 1] Japanese Patent Gazette No. 3601369 (pp.6; Fig. 1) [Patent Document 2] Japanese Patent Gazette No.3227651 (pp.1 - 3; Fig. 2)

Summary of Invention

Problems to be Solved by the Invention [0006] Both of the above examples of the prior art control refrigerant conditions so that a discharge temperature of the compressor or a temperature difference (ΔΤ) between the refrigerant that flows out of the radiator and the hot water supply fluid that flows therein becomes a target value to achieve an efficient operation. However, there was a problem that in the vicinity where an efficiency (COP) of the refrigeration cycle becomes maximum, a control based only on an inlet side (the above discharge temperature) of the radiator or an outlet side (the above temperature difference ΔΤ) is difficult to achieve stable and efficient operation conditions because changes in the discharge temperature or the temperature difference ΔΤ are small. In addition, since an operation in which an internal heat exchanger exists in the refrigerant circuit is not considered, there was a problem that to control to achieve stable and efficient operation conditions is difficult.

[0007] The present invention is made to solve the above problems in the prior art. The object is to obtain a refrigeration cycle apparatus capable of stably achieving efficient operation conditions by controlling operation values based on standard conditions of the radiator and outlet conditions of the radiator to be a target value.

Means for Solving the Problems [0008] In order to solve the above problems, the refrigeration cycle apparatus according to the present invention includes at least a compressor, a radiator, decompression means capable of changing an open degree, a heat absorber, an internal heat exchanger that performs heat exchange between a refrigerant at an outlet of the radiator and the refrigerant at the outlet of the heat absorber. The refrigeration cycle apparatus is characterized in that at least first refrigerant conditions detection means for detecting standard conditions of the radiator and second refrigerant conditions detection means for detecting refrigerant conditions between an outlet of the radiator and a high-pressure side inlet of an internal heat exchanger are provided, and an opening degree of decompression means is controlled so that a calculation value calculated based on an output of the first refrigerant conditions detection means and the output of the second refrigerant conditions detection means becomes a target value.

Effect of the Invention [0009] According to the present invention, the expansion valve opening degree is controlled so that the COP becomes maximum based on standard conditions of the radiator and refrigerant conditions of the radiator outlet part, so that a refrigerant cycle apparatus capable of stably achieving efficient operation can be obtained.

Brief Description of Drawings [0010] [Fig. 1] Fig. 1 is a diagram showing a configuration of a refrigeration cycle apparatus of the present invention.

[Fig. 2] Fig. 2 is a diagram showing an operation behavior on a P-h diagram of the present invention.

[Fig. 3] Fig. 3 is a diagram showing a temperature distribution of a refrigerant and water in a water heat exchanger of the present invention.

[Fig. 4] Fig. 4 is a diagram showing cycle conditions against an expansion valve opening degree of the present invention.

[Fig. 5] Fig. 5 is a diagram showing changes in each calculation value, heating ability, and COP against an expansion valve opening degree of the present invention.

[Fig. 6] Fig. 6 is a diagram showing changes in other calculation value, heating ability, and COP against an expansion valve opening degree of the present invention.

[Fig. 7] Fig. 7 is a diagram showing a control flowchart of the present invention.

Descriptions of Codes and Symbols [0011] 1 compressor 2 radiator (water heat exchanger) 3 expansion valve 4 heat absorber (evaporator) 5 internal heat exchanger 20 hot water supply side pump 21 hot water storage tank 22 use side pump 23, 24, 25 on-off valve 29 blower 30,31,32,33,41,42,52 temperature detection means 35, 51 pressure detection means 40 controller 50 heat source apparatus 60 hot water storage apparatus Best Mode for carrying Out the Invention Embodiment 1 [0012] Fig. 1 shows a configuration diagram of the refrigerant cycle apparatus according to the invention. In the figure, the refrigerant cycle apparatus according to the present embodiment is a hot water supply apparatus using carbon dioxide (hereinafter, CO2) as a refrigerant, composed of a heat source apparatus 50, a hot water storage apparatus 60, and a controller 40 for controlling these. It shows an example of the hot water supply apparatus, however, it is not limited thereto. The apparatus may be an air conditioner. In the same way, the refrigerant is not limited to carbon dioxide but an FIFC refrigerant may be used.

[0013] The heat source apparatus 50 is composed of a compressor 1 for compressing the refrigerant, a radiator 2 (hereinafter, referred to "water heat exchanger") for taking out heat of a high-temperature high-pressure refrigerant compressed in the compressor 1, an internal heat exchanger 5 for further cooling the refrigerant output from the water heat exchanger 2, a decompressor 3 (hereinafter, referred to "expansion valve") that decompresses the refrigerant and whose opening degree can be changed, an heat-absorber 4 (hereinafter, referred to "evaporator") for evaporating the refrigerant decompressed in the expansion valve 3, and an internal heat exchanger 5 for further heating the refrigerant flowed out of the evaporator 4. That is, the internal heat exchanger 5 is a heat exchanger that heat-exchanges the refrigerant at an outlet of the water heat exchanger 2 with the refrigerant at the outlet of the evaporator 4. A blower 29 is provided for sending air on an outer surface of the evaporator 4. There are also provided first temperature detection means 30 for detecting a discharge temperature of the compressor 1, second temperature detection means 31 for detecting an outlet temperature of the water heat exchanger 2, fifth temperature detection means 32 for detecting an inlet refrigerant temperature of the evaporator 4, and sixth temperature detection means 33 for detecting a suction temperature of the compressor 1. In addition, the first temperature detection means 30 and the second temperature detection means 31 correspond to a first refrigerant conditions detection means and second refrigerant conditions detection means respectively in an example of control in Fig. 7 to be described later.

[0014] A hot water storage apparatus 60 is connected with the water heat exchanger 2, which is a radiator, via piping, being composed of a heat source side pump 20, a hot water storage tank 21, a use side pump 22, and on-off valves 23, 24, 25. Here, on-of f valves 23, 24, 25 may be a simple valve only for switching operation or an opening variable valve. When a water level of the hot water storage tank 21 drops, the on-off valves 24, 25 are closed, the on-off valve 23 is opened, and hot water storage operation is performed in which supplied water is heated up to a predetermined temperature. When a heat dissipation loss is large and the temperature in the hot water storage tank 21 decreases such as in winter, the on-off valves 23, 25 are closed, the on-off valve 24 is opened, and circulation heating operation is performed in which low-temperature hot water in the hot water storage tank 21 is re-boiled. At the time of using the hot water supply, the on-off valves 23, 24 are closed, the on-off valve 25 is opened, the use side pump 22 starts operation to transfer stored hot water to the use side. At an inlet side of the water heat exchanger 2, third temperature detection means 41 is attached for detecting an inlet temperature of a medium (water) to be heated. At an outlet side of the water heat exchanger 2, fourth temperature detection means 42 is attached for detecting the outlet temperature of the medium (water) to be heated.

[0015] A controller 40 performs calculation using detected values from first temperature detection means 30, second temperature detection means 31, fifth temperature detection means 32, sixth temperature detection means 33, third temperature detection means 41, and fourth temperature detection means 42 to control an opening degree of the expansion valve 3, a rotation speed of the compressor 1, and the rotation speed of the hot water supply side pump 20, respectively.

[0016] Fig. 2 is a P-h diagram describing cycle conditions during hot water storage operation in the refrigeration cycle apparatus shown in Fig. 1. In Fig. 2, solid lines denote refrigerant conditions at a certain expansion valve opening degree and A, B, C, D, and E denote refrigerant conditions in the hot water storage operation. At the time of the hot water storage operation, a high-temperature high-pressure refrigerant (A) discharged from the compressor 1 flows into the water heat exchanger 2. In the water heat exchanger 2, the refrigerant heats supplied water while dissipating heat to water circulating the hot water storage circuit to decrease the own temperature. A refrigerant (B) flowed out of the water heat exchanger 2 dissipates heat in the internal heat exchanger 5 to further decrease (C) the temperature, being decompressed (D) by the expansion valve 3 to turn into a low-temperature low-pressure refrigerant. The low-temperature low-pressure refrigerant absorbs heat from the air in the evaporator 4 to evaporate (E). The refrigerant flowed out of the evaporator 4 is heated in the internal heat exchanger 5 to turn into a gas (F) and sucked by the compressor 1 to form a refrigeration cycle.

[0017] Here, the expansion valve 3 is controlled so that a suction superheat degree of the compressor 1 becomes a target value (for example, 5 to 10 °C). Specifically, based on a detection value of fifth temperature detection means 32 detecting an inlet refrigerant temperature of the evaporator 4, a temperature decrease amount due to a pressure loss in the evaporator 4 and the internal heat exchanger 5 is corrected, an evaporation temperature (ET) is estimated, a suction superheat degree SHs is calculated by the following formula using a detection value (Ts) of sixth temperature detection means 33 detecting a suction temperature of the compressor 1.

SHs = Ts - ET

[0018] Using the above formula, an opening degree of the expansion valve 3 is controlled so that SHs becomes a target value. An example is given in which an evaporation temperature (ET) is estimated based on the detection value of the fifth temperature detection means 32, however, it is not limited thereto. Pressure detection means (second pressure detection means) 51 (refer to Fig. 1) is installed between a low-pressure side outlet of the internal heat exchanger 5 and the inlet of the compressor 1, and from the detection value, a refrigerant saturation temperature may be obtained. A suction superheat degree control precedes other high efficiency operation control because a function to prevent liquid return of the compressor 1 precedes a function to efficiently operate the water heat exchanger 2 from the viewpoint of securing reliability of the equipment.

[0019] Next, operation on the P-h diagram in the case when the opening degree of the expansion valve 3 is made smaller is denoted by broken lines in Fig. 2. When the opening degree of expansion valve 3 is made smaller, the refrigerant flow amount flowing from the expansion valve 3 to the evaporator 4 decreases and the suction superheat degree of the compressor 1 temporarily increases. In addition, since the refrigerant shifts to a high pressure side, the pressure on the high pressure side increases and a discharge temperature becomes high. At the same time, a water heat exchanger output temperature decreases so that a temperature difference in the becomes constant. When the water heat exchanger output temperature decreases, a heat exchange amount in the internal heat exchanger 5 decreases, and as a result, the suction superheat degree becomes almost the same state as that of before the opening degree of the expansion valve 3 is made smaller to indicate a constant value. That is, a change in opening degree of the expansion valve 3 is absorbed by the heat exchange amount of the internal heat exchanger 5 (the heat exchange amount varies in response to the opening degree of the expansion valve 3) to make a change in the suction superheat degree small. Accordingly, control of the suction superheat degree of the compressor 1 alone cannot secure heating ability in the water heat exchanger 2 and efficiency is lowered. Therefore, new control is required in order to secure heating ability and improve operation efficiency.

[0020] Next, descriptions will be given to why a local maximal value occurs in performance (COP) using a temperature distribution in the water heat exchanger shown in Fig. 3.

[0021] Fig. 3 shows a refrigerant and water temperature distribution in the water heat exchanger 2. In the figure, thick solid lines show a change in refrigerant temperature, and a thin solid lines denote a change in water temperature. ΔΤ1 denotes a temperature difference between the water heat exchanger inlet temperature and water outlet temperature, and ΔΤ2 denotes a temperature difference between the water heat exchanger outlet temperature and water inlet temperature. Δ Tp is a temperature difference at a pinch point where the temperature difference between a refrigerant and water in the water heat exchanger 2 becomes minimum. ΔΤ denotes a temperature difference between the water heat exchanger inlet temperature and the water heat exchanger outlet temperature. As show/n by a cycle state against the expansion valve opening degree in Fig. 4, when a discharge temperature is increased by decreasing the expansion valve 3 opening degree, under a condition when heating ability in the water heat exchanger 2 is almost constant, the outlet temperature of the water heat exchanger 2 decreases so that an average temperature difference of the refrigerant and water in the water heat exchanger 2 is maintained, and the temperature difference Δ Tp of pinch point also decreases. Further, as the refrigerant amount shifts to a high pressure side, a discharge pressure rises to increase an input and COP is lowered. To the contrary, when the expansion valve 3 opening degree is made large and the discharge temperature is lowered, the outlet temperature of the water heat exchanger 2 increases so that an average temperature difference between the refrigerant and water in the water heat exchanger 2 is maintained. The temperature difference ΔΤρ at the pinch point also increases, however, a heating ability ratio becomes small and COP is lowered. Accordingly, as shown by broken lines in the figure, a suitable expansion opening degree exists that makes COP maximum.

[0022] Next, Fig. 5 shows changes in operation values obtained from the temperature of each part when the opening degree of the expansion valve 3 changes. In Fig. 5, the horizontal axis represents the opening degree (%) of the expansion valve 3, and the vertical axis represents the suction superheat degree, discharge temperature, temperature difference ΔΤ2 between the outlet temperature of the water heat exchanger and water inlet temperature, heating ability ratio, COP ratio. The heating ability ratio and COP ratio show a ratio when a maximum value against the expansion valve opening degree is set as 100%, respectively. Against changes in the opening degree of the expansion valve 3, changes in the suction superheat degree can be regarded as almost a constant value, so that it is understood that changes in the heating ability ratio and the COP ratio cannot be judged by the suction superheat degree. When controlling the COP to be maximum based on the temperature difference ΔΤ2 between the discharge temperature and the outlet temperature of the water heat exchanger and water inlet temperature, changes in the discharge temperature and temperature difference ΔΤ2 are small in the vicinity of the expansion valve opening degree when the COP reaches maximum as shown by a dotted line in the figure, so that it is found that a high accuracy temperature measurement is required for controlling COP to be maximum.

[0023] Next, Fig. 6 shows changes in other operation values obtained from temperatures of each part when the opening degree of the expansion valve 3 is changed. In Fig. 6, the horizontal axis represents the opening degree (%) of the expansion valve 3. The vertical axis represents an outlet/inlet temperature difference ΔΤΙιχ of the internal heat exchanger, a temperature difference ΔΤ between a discharge temperature and an outlet temperature of the water heat exchanger, a total temperature difference £At of the above ΔΤ1 and ΔΤ2, heating ability, and a COP ratio, respectively. Characteristics of Fig. 6 shows that operation can be performed in the vicinity where the COP becomes maximum by either controlling a heat exchange amount of the internal heat exchanger 5 based on the temperature difference ΔΤΙιχ between the outlet and inlet of the internal heat exchanger or controlling the heat exchange amount of the water heat exchanger 2 based on the total temperature difference £ΔΤ of ΔΤ1 and ΔΤ2 of the water heat exchanger 2. Further, the temperature difference ΔΤ between the discharge temperature and the outlet temperature of the water heat exchanger significantly changes in the vicinity of the expansion valve opening degree at which the COP becomes maximum, so that it is understood that a deviation from the maximum value of the COP could be controlled to be small based on the temperature difference ΔΤ. Here, only the case of the temperature difference ΔΤ is shown, however, the same effect can be expected by controlling based on the difference (ΔΤ1 - ΔΤ2) of the temperature differences ΔΤ1 and ΔΤ2.

[0024] Thus, it is possible to achieve an operation in the vicinity of the maximum efficiency by adopting a high-pressure side outlet temperature of the internal heat exchanger 5 for AThx, the discharge temperature for At, and the discharge temperature and a water side outlet/inlet temperatures for £AT.

[0025] As is understood from Fig. 6, a total temperature difference £At of the temperature difference ΔΤ1 between the water heat exchanger inlet temperature and water outlet temperature and the temperature difference ΔΤ2 between the water heat exchanger outlet temperature and water inlet temperature becomes a minimum. The control based on such an index has a physical meaning and being reasonable. However, high-precision temperature detection is required because change in temperature is small in the vicinity where the COP becomes a maximum compared with the temperature difference Δ T. Further, from Fig. 3, it is considered that when the COP becomes a maximum value, a temperature difference ΔΤρ at a pinch point is almost the same as that of ΔΤ2 between the water heat exchanger outlet temperature and water inlet temperature. This is because a maximum performance is shown when two temperature differences that become minimum in the water heat exchanger 2 become equal without being biased to either of them when considering characteristics of the heat exchanger. Accordingly, it is allowable to control the expansion valve 3 so as to make ΔΤρ and ΔΤ2 to be equal.

[0026] Next, descriptions will be given to an example of a control operation of the refrigeration cycle apparatus of Fig. 1 in which an expansion valve opening degree is controlled so as to make a suction superheat degree and the above temperature difference ΔΤ to converge at target values.

[0027] Fig. 7 is a flowchart showing a control operation of the refrigeration cycle apparatus, with the present invention, for the purpose of giving a priority to reliability of products, the suction superheat degree (SHs) control of the compressor 1 precedes the temperature difference ΔΤ control for securing the heating ability.

[0028] Firstly, when the suction superheat degree (SHs) is smaller than a target value (SHm) by a preset convergence range ASH or less (S101), the expansion valve opening degree is lowered until the suction superheat degree (SHs) converges. Thus, when the suction superheat degree (SHs) is secured, the temperature difference ΔΤ is made to converge at the target value. Specifically, when the temperature difference ΔΤ is smaller than a target value (ATm) by a preset convergence range 5T or less (S102), the expansion opening degree is lowered and ΔΤ is made to converge. Thus, lower limit values of the suction superheat degree (SHs) and the temperature difference ΔΤ can be suppressed.

[0029] Next, when the suction superheat degree (SHs) is larger than the target value (SHm) by a preset convergence range Δ SH or more (S103), the expansion valve opening degree is increased until the suction superheat degree (SHs) converges. Thus, when the suction superheat degree (SHs) is converged, the temperature difference ΔΤ is made to converge at the target value. Thus, when the suction superheat degree (SHs) is converged, the temperature difference ΔΤ is made to converge at the target value. Specifically, when the temperature difference ΔΤ is larger than the target value (ATm) by a preset convergence range δΤ or more (S104), the expansion opening degree is increased and AT is made to converge. Thus, upper limit values of the suction superheat degree (SHs) and the temperature difference AT can be suppressed. An example is shown in which a priority is given to control the suction superheat degree, however, it is not limited thereto when using a compressor which is resistant to liquid return. The same effect can be expected even when the priority order is exchanged. Through the above control, the suction superheat degree (SHs) and the temperature difference AT are converged at target values.

[0030] In the above, descriptions are given to an example in which the suction superheat degree (SHs) and the temperature difference AT are controlled to converge at target values (SHm, ATm), however, it is allowable that, in place of the temperature difference AT, a total temperature difference £ AT of ΔΤ1 and ΔΤ2, a difference between AT 1 and ΔΤ2 (AT 1 - ΔΤ2), or AThx can be used to control them to converge at a target value, respectively. When using £AT and (ΔΤ1 - Δ T2), they are obtained by calculating detection temperatures by the first temperature detection means 30, the second temperature detection means 31, the third temperature detection means 41, and the fourth temperature detection means 42. When using A Thx, internal heat exchanger outlet temperature detection means 52 is attached (refer to Fig. 1) between a high-pressure side outlet of the internal heat exchanger 5 and an inlet of the expansion valve 3, the temperature difference AThx is obtained from a detection temperatures by the second temperature detection means 31 and the internal heat exchanger outlet temperature detection means 52.

[0031] Since, in the invention, in addition to suction superheat degree control of the compressor, the expansion valve opening degree is made to be controlled so that the COP becomes maximum based on a temperature difference AThx between the discharge temperature and the water heat exchanger outlet temperature, a high efficiency refrigeration cycle apparatus can be obtained.

[0032] A refrigerant saturation temperature (ET) is obtained based on an output of the fifth temperature detection means 32 or pressure detection means, the suction superheat degree (SHs) is obtained by the detection temperature (Ts) of the sixth temperature detection means and the refrigerant saturation temperature (ET), and the expansion valve opening degree is controlled so that the suction superheat degree (SHs) becomes a target value, so that the superheat degree of the suction part of the compressor 1 is secured , liquid return to the compressor 1 can be prevented, and reliability can be secured. In the example of Fig. 1, descriptions are given to an example in which the fifth temperature detection means 32 is provided between the expansion valve 3 and the evaporator 4, it can be disposed at any position between the inlet of the evaporator 4 and a low-pressure side inlet of the internal heat exchanger 5.

[0033] In the present invention, when controlling the superheat degree and the above temperature difference AThx, the control of the superheat degree precedes the control of the above temperature differences. From this point, the reliability of the compressor 1 is secured.

[0034] In the present invention, the radiator is composed of the water heat exchanger, so that a high efficiency hot water supply apparatus can be obtained.

[0035] In any one of said previously mentioned refrigerant cycle apparatuses said radiator may be a heat exchanger that exchanges heat with water.

[0036] In any one of said previously mentioned refrigerant cycle apparatuses carbon dioxide may be used as a refrigerant.

REFERENCES CITED IN THE DESCRIPTION

This list of references cited by the applicant is for the reader's convenience only. It does not form part of the European patent document. Even though great care has been taken in compiling the references, errors or omissions cannot be excluded and the EPO disclaims all liability in this regard.

Patent documents cited in the description • US20030Q31827A Γ00031 • JP3601369B [6005] • JP3227651B Γ00051

Claims

A refrigerant cycle apparatus comprising: at least one compressor (1), a radiator (2), decompression means (3) capable of changing an opening degree, a heat absorber (4), an internal heat exchanger (5) which performs heat exchange between a refrigerant at an outlet of the radiator (2) and the refrigerant at an outlet of the heat absorber (4), a second temperature detection means (31) for detecting a refrigerant temperature between an outlet of the radiator (2) and a high pressure side input of the internal heat exchanger (5); internal heat exchanger output temperature detection means (52) for detecting the refrigerant temperature between a high pressure side outlet of the internal heat exchanger (5) and an input of the compression means (3), characterized in that an opening degree of the decompression means (3) is controlled such that a temperature difference ( detection temperature at the second temperature detection means (31) and the detection temperature at the internal heat exchanger output system a perimeter detection means (52) becomes a target value.

The refrigerant cycle apparatus of claim 1, wherein the sixth temperature detection means (33) for detecting the refrigerant temperature between a low pressure side outlet of the internal heat exchanger (5) and an input of the compressor (1) is provided, the the sixth temperature detection means (33) and a detection temperature at the sixth temperature detection means (33), and the degree of opening of the decompression means (3) is controlled such that the degree of overheating becomes the target value.

The refrigerant cycle apparatus of claim 2, wherein second pressure sensing means (51) is provided between the low pressure side output of the internal heat exchanger (5) and the input of the compressor (1) and the coolant saturation temperature is calculated based on a detection value of the second pressure sensing means (51).

The refrigerant cycle apparatus of claim 2, wherein the fifth temperature detection means (32) is provided between the input of the heat absorber (4) and the low pressure side input of the internal heat exchanger (5) and the refrigerant saturation temperature is calculated based on the detection temperature of the fifth temperature detection means (32).

The refrigerant cycle apparatus of any one of claims 2 to 4, wherein it is a priority to control the degree of overheating above the temperature difference.

The refrigerant cycle apparatus of any one of claims 1 to 5, wherein the radiator (2) is a heat exchanger that exchanges heat with water.

The refrigerant cycle apparatus of any one of claims 1 to 5, wherein carbon dioxide is used as a refrigerant.