JP2012067967A - Refrigeration cycle apparatus and hot water heating apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigeration cycle apparatus capable of improving a heating capability by rapid control to a proper refrigeration cycle state, and to provide a hot water heating appratus with the same.SOLUTION: The refrigeration cycle apparatus includes: a first temperature sensor 61 for detecting a temperature of refrigerant delivered from a compressor 21; a second temperature sensor 62 for detecting a temperature of refrigerant flowing out of an evaporator 25 in a refrigerant circuit 2; and a control device 4. The refrigeration cycle apparatus adjusts the amount of the refrigerant flowing through a bypass expansion valve 31, based on the temperature detected by the first temperature sensor 61 and a degree of superheat at an outlet of the evaporator 25 calculated from the temperature detected by the second temperature sensor 62. According to this arrangement, the distribution of an optimal refrigerant flow rate can always be secured, and thereby the high efficiency of operation and sufficient heating ability can be obtained.

Description

  The present invention relates to a refrigeration cycle apparatus and a hot water heating apparatus that bypass a part of refrigerant flowing out of a condenser and supercool the mainstream refrigerant by exchanging heat between the mainstream refrigerant and the bypass refrigerant.

  Conventionally, this type of refrigeration cycle apparatus and hot water heating apparatus is provided with a supercooling heat exchanger on the downstream side of the condenser in the refrigerant circuit, and the expanded refrigerant flows into the supercooling heat exchanger to flow from the condenser. The refrigerant that has flowed out is supercooled (see, for example, Patent Document 1).

  FIG. 4 shows a conventional refrigeration cycle apparatus described in Patent Document 1. As shown in FIG.

  As shown in FIG. 4, the refrigeration cycle apparatus 100 includes a refrigerant circuit 110 that circulates refrigerant and a bypass 120. The refrigerant circuit 110 is configured by connecting a compressor 111, a condenser 112, a supercooling heat exchanger 113, a main expansion valve 114, and an evaporator 115 in an annular shape by piping.

  The bypass 120 branches from the refrigerant circuit 110 between the supercooling heat exchanger 113 and the main expansion valve 114, and enters the refrigerant circuit 110 between the evaporator 115 and the compressor 111 via the supercooling heat exchanger 113. linked. The bypass passage 120 is provided with a bypass expansion valve 121 upstream of the supercooling heat exchanger 113.

  Further, the refrigeration cycle apparatus 100 detects a temperature sensor 141 that detects the temperature (discharge temperature) Td of the refrigerant discharged from the compressor 111, and detects the temperature of the refrigerant that flows into the evaporator 115 (evaporator inlet temperature) Te. The temperature sensor 142 that detects the temperature (bypass side inlet temperature) Tbi of the refrigerant flowing into the subcooling heat exchanger 113 in the bypass passage 120, and the subcooling heat exchanger 113 that flows out in the bypass passage 120. A temperature sensor 144 that detects the refrigerant temperature (bypass side outlet temperature) Tbo, and a target temperature Td (target) of the discharge pipe of the compressor is set from the evaporator inlet temperature Te detected by the temperature sensor 142, and the temperature sensor 141. The main expansion valve 114 is controlled so that the discharge temperature Td detected in step 1 becomes the target temperature Td (target). Bypass for controlling the expansion valve 121 so that the difference (Tbo-Tbi) between the bypass side outlet temperature Tbo and the bypass side inlet temperature Tbi in the supercooling heat exchanger 113 becomes a predetermined target value. It is comprised from the expansion valve control part.

Japanese Patent Laid-Open No. 10-68553

However, in the conventional configuration, when the refrigerant state at the outlet of the bypass passage 120 is adjusted to a wet state in order to obtain the maximum effect of improving the operation efficiency of the bypass, the degree of dryness cannot be controlled, so that the bypass-side flow rate does not increase. It becomes. Therefore, even if the discharge temperature Td is near the target temperature Td (target), which is substantially determined by the compressor suction refrigerant mixed with the main flow refrigerant and the bypass flow refrigerant (when there is no other change factor), the main flow side before the merge There is a possibility that the control of the main expansion valve converges in an inefficient refrigeration cycle state where the refrigerant circulation amount on the bypass side is not appropriate. In this case, a sufficient amount of heat absorption in the evaporator 115 cannot be obtained, and the supercooling heat exchanger 11
3 does not work sufficiently, the effect of increasing the enthalpy difference in the evaporator 115 and the effect of reducing the pressure loss of the low-pressure side piping due to the bypass are reduced, maintaining the refrigeration cycle state where the efficiency is poor and the heating capacity is insufficient It had the problem of end up.

  In particular, when the circulation amount of the main flow side refrigerant is excessive and the circulation amount of the bypass flow side refrigerant is excessive, the discharge temperature Td is lower than the target temperature Td (Target), so the main expansion valve 114 is controlled in the closing direction. In addition to a further decrease in operating efficiency, there has been a problem that the compressor suction pressure and liquid back may occur, the compressor may be damaged, and the reliability of the system is reduced.

  This invention solves the said conventional subject, and it aims at providing the refrigerating-cycle apparatus and hot water heating apparatus which can improve a heating capability by rapidly controlling to an appropriate refrigerating-cycle state. .

  In order to solve the above-described conventional problems, a refrigeration cycle apparatus according to the present invention includes a compressor, a condenser, a supercooling heat exchanger, a main expansion unit, a refrigerant circuit in which an evaporator is annularly connected, and the supercooling heat. A bypass path branched from the refrigerant circuit between the exchanger and the main expansion means, and connected to the refrigerant circuit between the evaporator and the compressor via the supercooling heat exchanger; Bypass expansion means provided upstream of the subcooling heat exchanger in the bypass passage, a first temperature sensor for detecting the temperature of refrigerant discharged from the compressor, and refrigerant flowing out of the evaporator in the refrigerant circuit A second temperature sensor that detects the temperature of the evaporator, and a control device, the degree of superheat at the evaporator outlet calculated from the temperature detected by the first temperature sensor and the temperature detected by the second temperature sensor And said bypass expansion It is characterized in that adjusting the amount of refrigerant flowing through the unit.

  As a result, an inappropriate refrigerant flow distribution from the temperature of the refrigerant discharged from the compressor and the degree of superheat at the evaporator outlet (the circulation amount of the bypass refrigerant is excessive and the circulation amount of the main refrigerant is too small). It can be determined that the main expansion means and the bypass expansion means are controlled in the inefficient refrigeration cycle state. In this case, the bypass expansion means is forcibly closed by a predetermined operation amount, so that the circulation amount of the bypass refrigerant is reduced. In addition, the circulation amount of the mainstream refrigerant is increased, and the refrigerant distribution is quickly improved, the amount of heat absorbed in the evaporator is increased, and the heat exchange between the mainstream refrigerant and the bypass refrigerant in the supercooling heat exchanger is performed in the evaporator. The effect of increasing the enthalpy difference and the effect of reducing the pressure loss of the low-pressure side refrigerant path due to the bypass of the refrigerant can be quickly and fully utilized, and it is possible to obtain an efficient and sufficient heating capacity. It is possible to provide a refrigeration cycle apparatus that.

  The refrigeration cycle apparatus and hot water heating apparatus of the present invention judge improper distribution of the main flow side refrigerant flow rate and bypass flow side refrigerant flow rate, and always promptly controls the proper flow rate distribution. Ensuring sufficient and maximizing the effect of increasing the enthalpy difference in the evaporator by heat exchange between the main refrigerant and bypass refrigerant in the subcooling heat exchanger and the pressure loss reducing effect in the low-pressure side refrigerant path due to refrigerant bypass Thus, it is possible to provide a refrigeration cycle apparatus and a hot water heating apparatus that can obtain a sufficient heating capacity even at a higher operating efficiency and a low outside air temperature.

Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention. Mollier diagram of the refrigeration cycle apparatus shown in FIG. Flowchart of operation control of the refrigeration cycle apparatus in Embodiment 1 of the present invention. Schematic configuration diagram of a conventional refrigeration cycle apparatus

  A first invention includes a compressor, a condenser, a supercooling heat exchanger, main expansion means, a refrigerant circuit in which an evaporator is connected in an annular shape, and between the supercooling heat exchanger and the main expansion means. A bypass path branched from the refrigerant circuit and connected to the refrigerant circuit between the evaporator and the compressor via the supercooling heat exchanger, and upstream of the supercooling heat exchanger in the bypass path Bypass expansion means provided on the side, a first temperature sensor for detecting the temperature of refrigerant discharged from the compressor, a second temperature sensor for detecting the temperature of refrigerant flowing out of the evaporator in the refrigerant circuit, and control And a refrigerant flowing through the bypass expansion means based on a temperature detected by the first temperature sensor and a degree of superheat at the outlet of the evaporator calculated from the temperature detected by the second temperature sensor Characterized by adjusting the amount Than is.

  As a result, it is possible to determine that the circulation rate of the bypass flow refrigerant is excessive and the circulation rate of the main flow refrigerant is excessive, and that the refrigerant is in an inefficient refrigeration cycle state due to inappropriate refrigerant distribution. Since the predetermined operation amount is forcibly closed, the circulation amount of the bypass refrigerant is reduced and the circulation amount of the main refrigerant is increased, so that the refrigerant flow distribution is improved. Therefore, sufficient heat absorption in the evaporator, the effect of increasing the enthalpy difference in the evaporator due to heat exchange between the mainstream refrigerant and the bypass refrigerant in the supercooling heat exchanger, and the pressure loss in the low-pressure side refrigerant path due to refrigerant bypass The reduction effect can be fully utilized, and sufficient heating capacity can be obtained even at high operating efficiency and low outside air temperature.

  In particular, the second invention is such that the temperature detected by the first temperature sensor of the first invention is lower than a predetermined temperature, and the degree of superheat at the evaporator outlet calculated from the temperature detected by the second temperature sensor. Is controlled to reduce the amount of refrigerant flowing through the bypass expansion means when the degree of superheat is equal to or greater than a predetermined degree of superheat.

  Thereby, when the temperature of the refrigerant discharged from the compressor is equal to or lower than the target temperature and the degree of superheat at the evaporator outlet becomes excessive, the circulation amount of the bypass flow refrigerant is excessive, and the circulation of the main flow refrigerant Since it is possible to more accurately determine that the refrigeration cycle state is inefficient due to improper refrigerant distribution with an insufficient amount, the efficiency of the first invention can be further enhanced without a decrease in efficiency due to erroneous determination. .

  In a third aspect of the invention, in particular, in the first or second aspect of the invention, a pressure sensor for detecting the pressure of the refrigerant sucked into the compressor is provided, and the pressure detected by the pressure sensor is sucked into the compressor. And calculating a degree of superheat at the outlet of the bypass passage from the calculated saturation temperature and the temperature detected by the second temperature sensor. By calculating the saturation temperature at the pressure of the refrigerant sucked into the compressor from the applied pressure, the degree of superheat at the outlet of the bypass passage can be accurately calculated.

  According to a fourth aspect of the invention, in particular, in the first or second aspect of the invention, by setting the change opening degree of the bypass expansion means to be larger as the degree of superheat at the evaporator outlet is larger, The degree of appropriateness of the refrigerant flow rate distribution can be determined from the degree, and the bypass expansion means is closed with the operation amount corresponding to the appropriate degree, so that the control responsiveness is improved. Therefore, the effects of the invention can be obtained quickly, and comfort can be improved.

In particular, according to a fifth aspect of the invention, in the third or fourth aspect of the invention, the temperature detected by the first temperature sensor is lower than a predetermined temperature, and the evaporator is calculated from the temperature detected by the second temperature sensor. When the degree of superheat at the outlet is equal to or higher than a predetermined degree of superheat, the main expansion means is opened even if the bypass expansion means is closed by controlling the amount of refrigerant flowing through the main expansion means to be increased,
An abnormal drop in the suction pressure due to excessive throttling of the main expansion means can be prevented, and the reliability of the compressor can be improved in addition to the effects of the above invention.

  In a sixth aspect of the present invention, particularly in the fifth aspect, the temperature detected by the first temperature sensor is lower than a predetermined temperature, and the degree of superheat at the evaporator outlet calculated from the temperature detected by the second temperature sensor. Is detected by the pressure sensor by controlling the amount of refrigerant flowing through the main expansion means to be increased when the pressure detected by the pressure sensor is equal to or lower than a predetermined pressure value. Since it is determined from the value that the suction pressure has decreased, the main expansion means can be opened only in a state where the main expansion means is excessively throttled. Therefore, the flow distribution can be improved more quickly while reliably preventing an abnormal drop in the suction pressure, and the effects of the invention can be further improved.

  According to the seventh aspect of the present invention, in particular, in the fifth or sixth aspect of the invention, by setting the change opening of the main expansion means to be larger as the pressure detected by the pressure sensor becomes lower than a predetermined pressure value, Since the opening operation amount according to the reduced state of the suction pressure when the means is closed, it is possible to quickly cope with a sudden change in the suction pressure due to a change in the operation state or the load state. The compressor reliability can be particularly improved.

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

(Embodiment 1)
FIG. 1 shows a schematic configuration diagram of a refrigeration cycle apparatus and a hot water heating apparatus according to a first embodiment of the present invention. In FIG. 1, the refrigeration cycle apparatus 1 </ b> A includes a refrigerant circuit 2 that circulates refrigerant, a bypass 3, and a control device 4. 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.

  The refrigerant circuit 2 is configured by connecting a compressor 21, a condenser 22, a supercooling heat exchanger 23, a main expansion valve (main expansion means) 24, and an evaporator 25 in an annular shape by piping. In the present embodiment, a sub-accumulator 26 and a main accumulator 27 that perform gas-liquid separation are provided between the evaporator 25 and the compressor 21. The refrigerant circuit 2 is provided with a four-way valve 28 for switching between normal operation and defrost operation.

  In the present embodiment, the refrigeration cycle apparatus 1A constitutes a heating means of a hot water heating apparatus that uses hot water generated by the heating means for heating, and the condenser 22 exchanges heat between the refrigerant and water. It is a heat exchanger that heats water.

  Specifically, a supply pipe 71 and a recovery pipe 72 are connected to the condenser 22. Water is supplied to the condenser 22 through the supply pipe 71, and water (hot water) heated by the condenser 22 is recovered in the recovery pipe 72. It has come to be collected through. The hot water collected by the collection pipe 72 is sent to a heater such as a radiator directly or via a hot water storage tank, and thereby heating is performed.

  The bypass path 3 branches from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve 24, and enters the refrigerant circuit 2 between the evaporator 25 and the compressor 21 via the supercooling heat exchanger 23. linked. In the present embodiment, the bypass path 3 is connected to the refrigerant circuit 2 between the sub accumulator 26 and the main accumulator 27. The bypass passage 3 is provided with a bypass expansion valve (bypass expansion means) 31 on the upstream side of the supercooling heat exchanger 23.

In the normal operation, the refrigerant discharged from the compressor 21 is sent to the condenser 22 via the four-way valve 28, and in the defrost operation, the refrigerant discharged from the compressor 21 is sent to the evaporator 25 via the four-way valve 28. It is done. In FIG. 1, the flow direction of the refrigerant during normal operation is indicated by solid arrows. Hereinafter, the state change of the refrigerant in the normal operation will be described.

  The high-pressure refrigerant discharged from the compressor 21 flows into the condenser 22 and radiates heat to the water passing through the condenser 22. The high-pressure refrigerant flowing out of the condenser 22 flows into the supercooling heat exchanger 23 and is supercooled by the low-pressure refrigerant decompressed by the bypass expansion valve 31. The high-pressure refrigerant that has flowed out of the supercooling heat exchanger 23 is distributed to the main expansion valve 24 side and the bypass expansion valve 31 side.

  The high-pressure refrigerant distributed to the main expansion valve 24 is decompressed and expanded by the main expansion valve 24 and then flows into the evaporator 25. Here, the low-pressure refrigerant flowing into the evaporator 25 absorbs heat from the air.

  On the other hand, the high-pressure refrigerant distributed to the bypass expansion valve 31 side is decompressed by the bypass expansion valve 31 and expanded, and then flows into the supercooling heat exchanger 23. The low-pressure refrigerant that has flowed into the supercooling heat exchanger 23 is heated by the high-pressure refrigerant that has flowed out of the condenser 22. Thereafter, the low-pressure refrigerant that has flowed out of the supercooling heat exchanger 23 merges with the low-pressure refrigerant that has flowed out of the evaporator 25, and is sucked into the compressor 21 again.

  The configuration of the refrigeration cycle apparatus 1A according to the present embodiment is that the refrigerant pressure sucked into the compressor 21 at the low outside air temperature is reduced and the refrigerant circulation amount is reduced, thereby reducing the heating capacity of the condenser 22. It is for preventing.

  In order to realize this, the amount of gas-phase refrigerant having a small endothermic effect that flows through the low pressure side portion of the refrigerant circuit 2 by increasing the enthalpy difference in the evaporator 25 by supercooling and bypassing the refrigerant by the bypass passage 3. It is important to reduce the pressure loss at the low pressure side portion of the refrigerant circuit 2.

  If the pressure loss at the low pressure side portion of the refrigerant circuit 2 is reduced, the pressure of the refrigerant sucked into the compressor 21 is increased accordingly, and the specific volume is reduced, so that the refrigerant circulation amount is increased. Moreover, if the enthalpy difference in the evaporator 25 is increased, even if the mass flow rate of the refrigerant passing through the evaporator 25 is reduced by bypass, the heat absorption amount in the evaporator 25 can be secured. That is, if the degree of supercooling of the refrigerant and the amount of bypass are maximized, the maximum heating capacity improvement effect of the condenser 22 and the coefficient of performance improvement effect of the refrigeration cycle apparatus 1A can be obtained.

  In the present embodiment, as will be described in detail later, when the refrigerant circulation amount on the bypass flow side becomes excessive, the refrigerant circulation amount on the main flow side becomes excessive, and when the refrigerant flow distribution becomes inappropriate, the bypass expansion valve Control is performed so that 31 is closed by a predetermined opening and the main expansion valve 24 is opened by a predetermined opening. Therefore, in the bypass passage 3, the amount of refrigerant circulating on the bypass flow side decreases, and the state of the refrigerant flowing out from the supercooling heat exchanger 23 is changed from a state with a low dryness as indicated by point a in FIG. It approaches saturation as shown by the dots.

  On the other hand, in the evaporator 25, the circulation amount of the main stream side refrigerant increases, so the state of the refrigerant that has flowed out of the evaporator 25 changes from an overheated state as indicated by point b in FIG. Will approach. That is, the subcooling heat exchanger 23 operates sufficiently, and the heat absorption amount in the evaporator 25 is increased and the compression is performed while the effect of increasing the enthalpy difference in the evaporator 25 and the effect of reducing the pressure loss due to the bypass are sufficiently obtained. The discharge refrigerant temperature of the machine 21 is ensured appropriately.

Hereinafter, the operation control operation will be described. The refrigerant circuit 2 includes a pressure sensor 51 that detects the pressure (intake pressure) Ps of the refrigerant sucked into the compressor 21 and a first temperature that detects the temperature (discharge temperature) Td of the refrigerant discharged from the compressor 21. A sensor 61 and a second temperature sensor 62 for detecting the temperature (evaporator outlet temperature) Teo of the refrigerant flowing out of the evaporator 25 are provided. On the other hand, the bypass passage 3 is provided with a third temperature sensor 63 for detecting the temperature (bypass passage outlet temperature) Tbo of the refrigerant flowing out from the supercooling heat exchanger 23.

  The control device 4 includes a first control device 4A and a second control device 4B, and detection values detected by various sensors, a pressure sensor 51, a first temperature sensor 61, a second temperature sensor 62, and a third temperature sensor 63. Based on the above, the rotational speed of the compressor 21, the switching of the four-way valve 28, and the opening degrees of the main expansion valve 24 and the bypass expansion valve 31 are controlled.

  In the present embodiment, the first control device 4A is configured to calculate the bypass path based on the bypass path outlet temperature Tbo detected by the third temperature sensor 63 and the suction pressure Ps detected by the pressure sensor 51 during normal operation. The bypass expansion valve 31 is controlled so that the superheat degree SHb at the three outlets becomes a predetermined superheat degree (bypass superheat degree control target value), and the temperature detected by the first temperature sensor 61 is set in advance. The degree of superheat at the outlet of the evaporator 25 which is lower than the predetermined temperature and is calculated based on the evaporator outlet temperature Teo detected by the second temperature sensor 62 and the suction pressure Ps detected by the pressure sensor 51. The bypass expansion valve 31 is controlled so that a predetermined first operation amount is closed when SHe is equal to or higher than a predetermined predetermined superheat (evaporator superheat control target value).

  Further, the second control device 4B controls the main expansion valve 24 so that the discharge temperature Td detected by the first temperature sensor 61 becomes a predetermined temperature (discharge temperature control target value) during normal operation. The temperature detected by the first temperature sensor 61 is lower than a predetermined temperature, and the evaporator outlet temperature Teo detected by the second temperature sensor 62 and the suction pressure detected by the pressure sensor 51 are controlled. The superheat degree SHe at the outlet of the evaporator 25 calculated based on Ps is equal to or higher than a predetermined predetermined superheat degree, and the suction pressure Ps detected by the pressure sensor 51 is equal to or lower than a predetermined predetermined pressure. When this happens, the main expansion valve 24 is controlled to open a predetermined second operation amount.

  Next, the control of the control device 4 during normal operation will be described in detail with reference to the flowchart shown in FIG.

  First, the control device 4 detects the discharge temperature Td with the first temperature sensor 61, the evaporator outlet temperature Teo with the second temperature sensor 62, and the bypass outlet temperature Tbo with the third temperature sensor 63 (step S1).

  Next, the control device 4 detects the suction pressure Ps by the pressure sensor 51 (step S2), and calculates the saturation temperature STs at the pressure of the refrigerant sucked into the compressor 21 from the detected suction pressure Ps (step S3). ). The calculation of the saturation temperature STs is performed using a refrigerant physical property formula. Thereafter, the control device 4 calculates the degree of superheat SHe at the outlet of the evaporator 25 by SHe = Teo-STs, and the degree of superheat SHb at the outlet of the bypass passage 3 by SHb = Tbo-STs (step S4).

  Here, the control device 4 determines whether or not the discharge temperature Td is lower than a predetermined discharge temperature (step S5).

When the discharge temperature Td is equal to or higher than a predetermined discharge temperature (NO in step S5), the bypass-side refrigerant circulation amount is in an appropriate or small state, and the flow distribution adjustment in the normal control is possible. Therefore, the control device 4 adjusts the opening degree of the bypass expansion valve 31 so that the superheat degree SHb becomes the superheat degree control target value (step S6), and then the discharge temperature Td becomes the discharge temperature control target. The opening degree of the main expansion valve 24 is adjusted so as to be a value (step S7), and the process returns to step S1.

  On the other hand, when the discharge temperature Td is lower than the predetermined discharge temperature set in advance (YES in step S5), there is a possibility that the bypass-side refrigerant circulation amount is excessive. In order to determine whether or not the state is a proper state, it is determined whether or not the superheat degree SHe at the outlet of the evaporator 25 is equal to or higher than a predetermined superheat degree (step S8).

  When the superheat degree SHe at the outlet of the evaporator 25 is smaller than a predetermined superheat degree (NO in step S8), the refrigeration cycle state is in a transitional state, and the overall pressure reduction amount by the expansion valve is Since the controller 4 is considered to be insufficient, the controller 4 adjusts the opening degree of the bypass expansion valve 31 so that the superheat degree SHb becomes the bypass superheat degree control target value (step S6), and then the discharge temperature Td is The opening degree of the main expansion valve 24 is adjusted so as to be the discharge temperature control target value (step S7), and the process returns to step S1.

  On the other hand, when the superheat degree SHe at the outlet of the evaporator 25 is equal to or higher than a predetermined superheat degree (YES in step S8), the main stream side refrigerant is in the state of point b shown in FIG. Since the bypass side refrigerant is in the state of point a (too wet due to excessive flow rate) and the performance of the evaporator 25 and the supercooling heat exchanger 23 is not fully utilized, the control device 4 closes the opening degree of the bypass expansion valve 31 by a predetermined first operation amount (step S9).

  Thereafter, the control device 4 determines whether or not the suction pressure Ps is equal to or lower than a predetermined pressure (step S10). In the case of NO in step S10, the opening degree of the main expansion valve 24 is considered to be appropriate, and the process directly returns to step S1.

  On the other hand, in the case of YES in step S10, the opening degree of the main expansion valve 24 is considered to be too small. Therefore, the control device 4 sets the opening degree of the bypass expansion valve 31 to a predetermined second operation amount. Open (step S11) and return to step S1.

  As described above, in the present embodiment, the first temperature sensor 61 that detects the temperature of the refrigerant discharged from the compressor 21 in the refrigerant circuit 2 and the second temperature that detects the temperature of the refrigerant flowing out of the evaporator 25. A sensor 62; a pressure sensor 51 for detecting the pressure of the refrigerant sucked into the compressor 21; a third temperature sensor 63 for detecting the temperature of the refrigerant flowing out of the supercooling heat exchanger 23 in the bypass passage 3; Bypass so that the degree of superheat at the outlet of the bypass passage 3 calculated based on the temperature of the bypass passage outlet detected by the temperature sensor 63 and the suction pressure detected by the pressure sensor 51 becomes a predetermined degree of superheat. The expansion valve 31 is controlled, the temperature detected by the first temperature sensor 61 is lower than a predetermined temperature, and the degree of superheat at the outlet of the evaporator 25 is predetermined. When a degree of superheat above, controls the bypass expansion valve 31 so as to close a predetermined first operation amount predetermined, a configuration having a first control device 4A.

Thereby, from the temperature of the refrigerant discharged from the compressor 21 and the degree of superheat at the outlet of the evaporator 25, inappropriate refrigerant flow distribution (the circulation amount of the bypass flow refrigerant is excessive, and the circulation amount of the mainstream refrigerant is too small. In this case, the bypass expansion valve 31 is forcibly closed by a predetermined operation amount, so that the circulation amount of the bypass refrigerant is decreased and the circulation amount of the main refrigerant is increased. Thus, the refrigerant circulation amount can be quickly and appropriately distributed. Therefore, sufficient heat absorption in the evaporator, the effect of increasing the enthalpy difference in the evaporator due to heat exchange between the mainstream refrigerant and the bypass refrigerant in the supercooling heat exchanger, and the pressure loss in the low-pressure side refrigerant path due to refrigerant bypass The reduction effect can be fully utilized, and sufficient heating capacity can be obtained even at high operating efficiency and low outside air temperature.

  In the present embodiment, during the normal operation, the main expansion valve 24 is controlled so that the discharge temperature detected by the first temperature sensor 61 becomes a predetermined temperature, and the first temperature sensor 61 is used. The outlet of the evaporator 25 is calculated based on the evaporator outlet temperature detected by the second temperature sensor 62 and the suction pressure detected by the pressure sensor 51. When the suction pressure detected by the pressure sensor 51 is equal to or lower than a predetermined predetermined pressure. It is set as the structure provided with the 2nd control apparatus 4B which controls the main expansion valve 24 so that the operation amount may open.

  Thereby, since it is judged from the detection value of the pressure sensor 51 that the suction pressure is reduced, the main expansion means can be opened only by restricting the main expansion means to an excessively throttled state. Therefore, the flow distribution can be improved more quickly while reliably preventing an abnormal drop in the suction pressure, and the reliability of the compressor can be improved in addition to the effects of the above invention.

  Further, the predetermined first operation amount of the present embodiment is configured to be determined according to the degree of superheat at the outlet of the evaporator 25 so that the amount of operation increases as the degree of superheat at the outlet of the evaporator 25 increases. Thus, the degree of appropriateness of refrigerant distribution can be determined from the degree of superheat at the outlet of the evaporator 25, and the bypass expansion valve 31 is closed with an operation amount corresponding to the appropriate degree, so that control responsiveness is improved. Therefore, the effects of the invention can be obtained quickly, and comfort can be improved.

  Further, the predetermined second operation amount according to the present embodiment is determined according to the pressure so that the operation amount increases as the pressure detected by the pressure sensor 51 becomes lower than the predetermined pressure value. Therefore, it is possible to quickly cope with a sudden change in the suction pressure due to a change in the operation state or the load state, and it is possible to particularly improve the compressor reliability in the effect of the present invention. .

  In FIG. 1, the pressure sensor 51 is provided between the position where the bypass path 3 in the refrigerant circuit 2 is connected and the main accumulator 27, but the pressure sensor 51 is between the evaporator 25 and the compressor 21. It may be provided at any position in the refrigerant circuit 2. Alternatively, the pressure sensor 51 may be provided on the downstream side of the subcooling heat exchanger 23 in the bypass passage 3.

  In the present embodiment, the bypass expansion valve 31 is controlled so that the degree of superheat SHb at the outlet of the bypass passage 3 becomes a target value. However, the method of controlling the bypass expansion valve 31 is not limited to this. Absent. For example, the bypass expansion valve 31 may be controlled so that the temperature or the degree of supercooling at the outlet of the supercooling heat exchanger 23 becomes a target value.

  Alternatively, the bypass expansion valve 31 can be controlled based on the degree of supercooling of the refrigerant at the outlet of the condenser 22.

  Further, the bypass passage 3 does not necessarily have to branch from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve 24, and the refrigerant circuit 2 is between the condenser 22 and the supercooling heat exchanger 23. You may branch from.

  Furthermore, the main expansion means and bypass expansion means of the present invention are not necessarily expansion valves, and may be an expander that recovers power from the expanding refrigerant. In this case, for example, the rotational speed of the expander may be controlled by changing the load with a generator connected to the expander.

  INDUSTRIAL APPLICABILITY The present invention is particularly useful for a hot water heater that generates hot water using a refrigeration cycle apparatus and uses the hot water for heating.

DESCRIPTION OF SYMBOLS 1A Refrigeration cycle apparatus 2 Refrigerant circuit 3 Bypass path 4 Control apparatus 4A 1st control apparatus 4B 2nd control apparatus 21 Compressor 22 Condenser 23 Supercooling heat exchanger 24 Main expansion valve (main expansion means)
25 Evaporator 31 Bypass expansion valve (Bypass expansion means)
51 Pressure sensor 61 First temperature sensor 62 Second temperature sensor

Claims (8)

A compressor, a condenser, a supercooling heat exchanger, a main expansion means, a refrigerant circuit in which an evaporator is connected in an annular shape, and a branch from the refrigerant circuit between the supercooling heat exchanger and the main expansion means, A bypass passage connected to the refrigerant circuit between the evaporator and the compressor via the supercooling heat exchanger, and bypass expansion means provided on the upstream side of the supercooling heat exchanger in the bypass passage A first temperature sensor for detecting a temperature of refrigerant discharged from the compressor, a second temperature sensor for detecting a temperature of refrigerant flowing out of the evaporator in the refrigerant circuit, and a control device, The amount of refrigerant flowing through the bypass expansion means is adjusted based on the temperature detected by the first temperature sensor and the degree of superheat at the outlet of the evaporator calculated from the temperature detected by the second temperature sensor. Refrigeration cycle equipment When the temperature detected by the first temperature sensor is lower than the predetermined temperature and the superheat degree of the evaporator outlet calculated from the temperature detected by the second temperature sensor is equal to or higher than the predetermined superheat degree, the bypass expansion means is 2. The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is controlled so as to reduce an amount of flowing refrigerant. A pressure sensor for detecting the pressure of the refrigerant sucked into the compressor is provided, a saturation temperature at the pressure of the refrigerant sucked into the compressor is calculated from the pressure detected by the pressure sensor, and the calculated saturation temperature and The refrigeration cycle apparatus according to claim 1 or 2, wherein the degree of superheat at the outlet of the bypass path is calculated from the temperature detected by the second temperature sensor. 3. The refrigeration cycle apparatus according to claim 1, wherein the degree of change of the bypass expansion means is set to increase as the degree of superheat at the evaporator outlet increases. 4. When the temperature detected by the first temperature sensor is lower than the predetermined temperature and the superheat degree at the evaporator outlet calculated from the temperature detected by the second temperature sensor is equal to or higher than the predetermined superheat degree, the main expansion means is 5. The refrigeration cycle apparatus according to claim 3, wherein the refrigeration cycle apparatus is controlled so as to increase a flowing refrigerant amount. The temperature detected by the first temperature sensor is lower than a predetermined temperature, and the degree of superheat at the evaporator outlet calculated from the temperature detected by the second temperature sensor is equal to or higher than a predetermined temperature. 6. The refrigeration cycle apparatus according to claim 5, wherein when the pressure detected by the pressure sensor is equal to or lower than a predetermined pressure value, control is performed to increase the amount of refrigerant flowing through the main expansion means. 7. The refrigeration cycle apparatus according to claim 5, wherein the refrigeration cycle apparatus is set to increase the change opening of the main expansion means as the pressure detected by the pressure sensor becomes lower than a predetermined pressure value. The hot water heating apparatus provided with the refrigeration cycle apparatus of any one of Claims 1-7.

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