JP2018205943A - Design support device and design support method of refrigeration cycle system - Google Patents

Abstract

To provide a design support device and method of a refrigeration cycle system further improving the design efficiency of a refrigeration cycle system.SOLUTION: A storage part 21 stores a reference model of a refrigeration cycle system 7 which defines a plurality of heat exchange characteristics of a capacitor 1 and an evaporator 2, and a performance characteristic of a compressor 3. A setting part 22 sets a calculation model in the reference model. The calculation model has a characteristic obtained by multiplying a heat exchange amount or a pressure loss of the capacitor 1 by a first coefficient K, a characteristic obtained by multiplying a heat exchange amount or a pressure loss of the evaporator 2 by a second coefficient K, and a characteristic obtained by multiplying operation efficiency of the compressor 3 by a third coefficient K. An optimization calculation part 23 executes an optimization calculation which regards the value of performance desired to be satisfied by the refrigeration cycle system 7 as an objective function, and the first coefficient K, the second coefficient Kand the third coefficient Kas a design variable, and calculates a combination of the first coefficient K, the second coefficient Kand the third coefficient Kwhich satisfy the performance.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an apparatus and method for supporting design of a refrigeration cycle system.

  2. Description of the Related Art Conventionally, a method for determining a design variable through optimization calculation by a computer at a design stage of a refrigeration cycle system is known. In other words, a calculation model that defines the specifications and characteristics of various parts included in the refrigeration cycle system is created on a computer, and the design variables and the parts in the calculation model are changed until the optimal combination of design variables is obtained. It is a technique that repeats calculations. In such optimization calculation, as the design variables and the number of parts increase, the calculation amount increases in a geometric series, and the calculation time becomes enormous. Therefore, various methods for improving the efficiency of optimization calculation have been studied (for example, see Patent Document 1).

JP 2007-164393 A

  On the other hand, when designing a system that improves or improves an existing system rather than designing a new refrigeration cycle system, the amount of calculation can be greatly reduced by diverting the existing calculation model. The design efficiency can be improved. In particular, when designing a refrigeration cycle system for an air conditioner installed in a vehicle, the required cooling capacity, power consumption, cost, and other conditions are categorized according to vehicle grade, cabin size, engine room layout, etc. There is room for improvement in terms of design efficiency.

  One of the purposes of this case was created based on the above-described knowledge, and is to further improve the design efficiency of the refrigeration cycle system. It should be noted that the present invention is not limited to this purpose, and is an operational effect that is derived from each configuration shown in “Mode for Carrying Out the Invention” to be described later. Can be positioned as a purpose.

  (1) The disclosed refrigeration cycle system design support apparatus is a design support apparatus that supports the design of a refrigeration cycle system in which a condenser, an evaporator, and a compressor are interposed on a refrigerant circulation path. The apparatus includes a storage unit that stores a reference model of the refrigeration cycle system in which a plurality of heat exchange characteristics of the condenser and the evaporator and performance characteristics of the compressor are defined. Further, based on the reference model, a heat exchange amount or pressure loss in any one of the plurality of heat exchange characteristics of the condenser is multiplied by a first coefficient, and the plurality of the heat of the evaporator Setting to set a calculation model having a characteristic obtained by multiplying the heat exchange amount or pressure loss in any one of the exchange characteristics by a second coefficient, and a characteristic obtained by multiplying the operating efficiency of the compressor by a third coefficient A part. Further, an optimization calculation using the performance value desired to be satisfied in the refrigeration cycle system to be designed as an objective function of the calculation model and the first coefficient, the second coefficient, and the third coefficient as design variables is performed. By implementing, an optimization calculation unit is provided that calculates a combination of the first coefficient, the second coefficient, and the third coefficient that satisfy the performance. Here, the type of characteristic multiplied by the first coefficient and the second coefficient is determined so as to correspond to the performance related to the objective function.

  Specific examples of the above-mentioned “performance to be satisfied in the refrigeration cycle system to be designed” include the temperature of the air cooled by the evaporator (blowing temperature), pressure loss, and the like. When the blowout temperature is the objective function of the calculation model, the target to be multiplied by the first coefficient or the second coefficient is “a heat exchange amount (for example, heat exchange amount, refrigerant flow rate in the relationship between wind speed and heat exchange amount). And the heat exchange amount in the relationship of the heat exchange amount). On the other hand, when the pressure loss is the objective function of the calculation model, the object to be multiplied by the first coefficient or the second coefficient is “air pressure loss (air pressure loss in the relationship between wind speed and air pressure loss)” or “refrigerant pressure loss ( The refrigerant pressure loss in the relationship between the refrigerant flow rate and the refrigerant pressure loss).

(2) The refrigeration cycle system is preferably a refrigeration cycle system mounted on a vehicle. The reference model is preferably defined in a refrigeration cycle system of an existing vehicle having a size comparable to that of the vehicle on which the refrigeration cycle system to be designed is mounted.
(3) Preferably, the reference model is defined in a refrigeration cycle system of an existing vehicle having the same vehicle rating as the vehicle on which the refrigeration cycle system to be designed is mounted.

(4) The disclosed refrigeration cycle system design support method is a computer-aided design support method that supports the design of a refrigeration cycle system in which a condenser, an evaporator, and a compressor are interposed on a refrigerant circulation path. In this method, the following procedure is executed on a computer.
Create a reference model of the refrigeration cycle system in which a plurality of heat exchange characteristics of the condenser and the evaporator and performance characteristics of the compressor are defined.
The heat exchange amount or pressure loss in any one of the plurality of heat exchange characteristics of the condenser with respect to the reference model has a characteristic multiplied by a first coefficient, and the heat exchange of the evaporator A calculation model having a characteristic obtained by multiplying the heat exchange amount or pressure loss of any one of the characteristics by a second coefficient and a characteristic obtained by multiplying the operating efficiency of the compressor by a third coefficient is set.
・ Perform an optimization calculation with the value of the performance to be satisfied in the refrigeration cycle system to be designed as the objective function of the calculation model and the first coefficient, the second coefficient, and the third coefficient as design variables. Thus, a combination of the first coefficient, the second coefficient, and the third coefficient satisfying the performance is calculated.
Determining the type of characteristic to be multiplied by the first coefficient and the second coefficient so as to correspond to the performance relating to the objective function;

The first coefficient is preferably any of the following.
A coefficient to be multiplied by the heat exchange amount in the characteristics of the heat exchange amount with respect to the wind speed or the refrigerant flow rate in the condenser, a coefficient to be multiplied with the air pressure loss in the characteristic of the air pressure loss with respect to the wind speed, and a refrigerant pressure loss with respect to the refrigerant flow rate. Coefficient multiplied by refrigerant pressure loss in characteristics

The second coefficient is preferably one of the following.
A coefficient multiplied by the heat exchange amount in the characteristics of the heat exchange amount with respect to the wind speed or the refrigerant flow rate in the evaporator, a coefficient multiplied with the air pressure loss in the characteristic of the air pressure loss with respect to the wind speed, and a refrigerant pressure loss with respect to the refrigerant flow rate A coefficient that is multiplied by the refrigerant pressure loss in characteristics The third coefficient is preferably a coefficient that is multiplied by the operating efficiency in characteristics of operating efficiency with respect to the rotation speed and pressure ratio of the compressor.

  By expressing the capacities of the condenser, evaporator, and compressor with the first coefficient, the second coefficient, and the third coefficient, and performing optimization calculations using these as design variables, the amount of computation can be reduced and the design can be reduced. Efficiency can be improved.

It is a model figure of a refrigerating cycle system. It is a schematic diagram which shows the design assistance apparatus of a refrigerating cycle system. (A)-(D) are the graphs for demonstrating a 1st coefficient. (A)-(D) are the graphs for demonstrating a 2nd coefficient. It is a graph for demonstrating a 3rd coefficient. It is a graph for demonstrating the combination of a coefficient. It is a flowchart which shows the design assistance method of a refrigerating cycle system.

  Hereinafter, a design support apparatus for a refrigeration cycle system as an embodiment will be described with reference to the drawings. In this embodiment, a refrigeration cycle system for an air conditioner mounted on a vehicle is designed. The embodiment described below is merely an example, and there is no intention of excluding various modifications and technical applications that are not explicitly described in the following embodiment. Each configuration of the present embodiment can be implemented with various modifications without departing from the spirit thereof. Further, they can be selected as necessary, or can be appropriately combined.

[1. Analysis model]
FIG. 1 is a model diagram of a refrigeration cycle system 7 to be analyzed by the design support apparatus. The refrigeration cycle system 7 is created as a physical model such as a one-dimensional model or a three-dimensional model, for example, and the movement of the refrigerant along the refrigerant path 6 or the heat transfer state is defined. A condenser 1 (condenser), an evaporator 2 (vaporizer), a compressor 3 (compressor), and an expansion valve 4 are interposed in the refrigerant path 6. The condenser 1 has a function of exchanging heat between the high-temperature, high-pressure, and gaseous refrigerant with the air and radiating heat from the refrigerant to the air. The refrigerant that has passed through the inside of the condenser 1 is liquefied as the temperature decreases. Further, the air that has passed through the outer surface of the condenser 1 is warmed.

  The evaporator 2 has a function of exchanging heat between low-temperature, low-pressure, and liquid refrigerant with air and absorbing heat from the air. The refrigerant that has passed through the evaporator 2 is vaporized as the temperature rises. Further, the air that has passed through the outer surface of the evaporator 2 is cooled. The air cooled here is fed into the passenger compartment by the blower fan 5 as conditioned air for cooling. The compressor 3 has a function of compressing and feeding a low-pressure refrigerant to a high pressure, and the expansion valve 4 has a function of decompressing the high-pressure refrigerant.

[2. Device configuration]
FIG. 2 is a schematic diagram illustrating a configuration of the design support apparatus 10 of the refrigeration cycle system 7. The design support apparatus 10 is a general-purpose computer that can execute the computer program 20. The design support device 10 is provided with a central processing unit 11 (CPU), a main storage device 12 (memory), an auxiliary storage device 13, an input device 14, an output device 15, and a recording device 16, which are connected via an internal bus 17. So that they can communicate with each other.

  The central processing unit 11 is a processing unit (processor) incorporating a control unit (control circuit), an arithmetic unit (arithmetic circuit), a cache memory (register group), and the like. The main storage device 12 is a memory device that stores a program and working data, and includes, for example, a ROM (Read Only Memory) and a RAM (Random Access Memory). On the other hand, the auxiliary storage device 13 is a memory device that stores data and programs that are retained for a longer period of time than the main storage device 12, and is, for example, a flash memory, an EEPROM (Electrically Erasable Program-mable Read-Only Memory), an SSD, or the like. This includes non-volatile memories such as (Solid State Drive) and hard disk drives.

  The input device 14 controls input operations and input information to a computer, and includes, for example, a keyboard, a mouse, a storage reader, and the like. The model of the refrigeration cycle system 7 to be analyzed by the design support apparatus can be input to a computer via the input device 14 and can be recorded and stored in the auxiliary storage device 13. The output device 15 manages output information from the computer, and includes, for example, a display, a printer, a storage writer, and the like. The output device 15 outputs and displays analysis processes and analysis results. The recording device 16 is a device having both a function of reading and writing information recorded and stored in a recording medium 18 (removable medium) such as an optical disk or a semiconductor memory.

  The computer program 20 executed by the design support device 10 may be recorded and stored in the main storage device 12 or may be recorded and stored in the auxiliary storage device 13. Alternatively, the program may be recorded and stored on the recording medium 18, and the program written on the recording medium 18 may be read and executed by the central processing unit 11 via the recording device 16. The computer program 20 is appropriately expanded in the memory space on the main storage device 12, and is read into the central processing unit 11 and executed.

[3. Control configuration]
General-purpose design optimization calculation software is installed in the design support apparatus 10 of this embodiment. As the optimization method, mathematical programming, quality engineering method, heuristic method (genetic algorithm, annealing method), etc. are adopted. Further, the computer program 20 is provided with a storage unit 21, a setting unit 22, and an optimization calculation unit 23. Each of these elements shows the functions of the computer program 20 for convenience, and each element may be described as an independent program, or described as a composite program having these functions. May be.

  The storage unit 21 stores a reference model of the refrigeration cycle system. A reference model is a model of a system having a reference characteristic. When designing a new system improved from an existing system, a model obtained by modeling the existing system is used as a reference model. For example, a refrigeration cycle system in an existing vehicle having the same size as a vehicle on which the refrigeration cycle system to be designed is mounted is defined as the reference model. Alternatively, a refrigeration cycle system in an existing vehicle having the same vehicle rating as the vehicle on which the refrigeration cycle system to be designed is mounted is defined as the reference model.

  In this embodiment, the model of the refrigeration cycle system 7 as shown in FIG. In the reference model, characteristics and dimensions of various devices included in the refrigeration cycle system, characteristics of the refrigerant, and the like are defined. For example, the heat exchange characteristics and dimensions of the condenser 1, the heat exchange characteristics and dimensions of the evaporator 2, the performance characteristics and dimensions of the compressor 3, the performance characteristics of the expansion valve 4, the performance characteristics of the blower fan 5, the piping shape and piping of the refrigerant path 6 Route and piping material dimensions, physical property data of refrigerant, etc. are defined.

  Specific examples of the heat exchange characteristics of the condenser 1 include the relationship between the refrigerant flow rate and the heat exchange amount, the relationship between the wind speed and the heat exchange amount, the relationship between the refrigerant flow rate and the refrigerant pressure loss, and the relationship between the wind speed and the air pressure loss. The above-mentioned characteristics due to the difference in the material of the capacitor 1 can be mentioned. Specific examples of the dimensions of the condenser 1 include the size of the condenser 1, the cross-sectional area of the flow path of the refrigerant, and the pitch of the fins. The same applies to the heat exchange characteristics and dimensions of the evaporator 2. Specific examples of the performance characteristics of the compressor 3 include the relationship between the rotation speed and the refrigerant flow rate, the relationship between the rotation speed and the pressure ratio (ratio of the discharge pressure to the refrigerant suction pressure) and the operation efficiency, the rotation speed and the refrigerant flow rate. For example, the relationship between the temperature rise and the pressure ratio. Specific examples of the dimensions of the compressor 3 include the shape of the refrigerant compression section (fixed blade or movable blade), the flow path cross-sectional area of the refrigerant, the degree of bending of the flow path from the refrigerant compression section to the discharge port, and the like.

  Specific examples of performance characteristics of the expansion valve 4 include the relationship between the refrigerant temperature and the refrigerant pressure, the relationship between the lift amount of the expansion valve 4 and the refrigerant pressure, the relationship between the lift amount of the expansion valve 4 and the refrigerant flow rate, and the refrigerant flow rate. For example, the relationship with the refrigerant temperature. Specific examples of the performance characteristics of the blower fan 5 include the relationship between the rotational speed, the temperature, and the air volume, the relationship between the air volume and the pressure ratio, the relationship between the wind speed and the air pressure loss, and the like. Specific examples of the characteristics of the refrigerant path 6 include pipe cross-sectional shape, cross-sectional area, pipe pressure, pipe material (thermal conductivity), and the like. Specific examples of the physical property data of the refrigerant include a relationship between the refrigerant temperature and specific heat, a relationship between the refrigerant temperature and viscosity, and the like.

  The setting unit 22 sets a calculation model based on the reference model. Here, it is assumed that the difference in characteristics between the reference model and the calculation model is expressed by a maximum of one parameter for each device interposed in the refrigerant path 6. That is, the calculation model differs from the reference model only in one characteristic for each device. In the case of the refrigeration cycle system 7 shown in FIG. 1, four types of devices, a condenser 1, an evaporator 2, a compressor 3, and an expansion valve 4, are interposed in the refrigerant path 6, so that the reference model and calculation can be performed with a maximum of four parameters. Differences in characteristics from the model shall be expressed.

The calculation model of the present embodiment is based on a reference model used in a design for vehicles of the same vehicle rating. That is, the reference model and the calculation model are models of a refrigeration cycle system mounted on vehicles having the same vehicle compartment size and engine room layout. In the present embodiment, the design of the three devices of the condenser 1, the evaporator 2, and the compressor 3 is changed. That is, the difference in characteristics between the reference model and the calculation model is represented by three coefficients (variables). Hereinafter, these coefficients are referred to as a first coefficient K ₁ , a second coefficient K ₂ , and a third coefficient K ₃ . The calculation model set here is stored in the storage unit 21 separately from the reference model.

The first coefficient K1 is _one of the following.
A coefficient multiplied by the heat exchange amount in the characteristics of the heat exchange amount with respect to the wind speed or the refrigerant flow rate in the condenser 1 [see FIGS. 3A and 3B]
A coefficient multiplied by the air pressure loss in the characteristics of the air pressure loss with respect to the wind speed of the air passing outside the condenser 1 (see FIG. 3C)
A coefficient multiplied by the refrigerant pressure loss in the characteristic of the refrigerant pressure loss with respect to the refrigerant flow rate of the refrigerant passing through the condenser 1 (see FIG. 3D)

3A to 3D, a solid line is a characteristic graph defined by the reference model, and a broken line corresponds to a characteristic graph in the calculation model. By the first coefficient K ₁ values, graphs shape is deformed in the vertical direction. The heat exchange characteristic of the condenser 1 on the calculation model has one characteristic including a heat exchange amount (or air pressure loss or refrigerant pressure loss) multiplied by the first coefficient K ₁ and a plurality of characteristics same as the reference model. For example, when the first coefficient K ₁ is multiplied by the heat exchange amount with respect to the wind speed in the condenser 1, the heat exchange characteristics of the condenser 1 on the calculation model are shown by the broken line graph of FIG. 3A and FIGS. The characteristic is defined by the solid line graph of (D). The size of the capacitor 1 on the calculation model is the same as that of the capacitor 1 on the reference model. In other words, the characteristics of the capacitor 1 of the calculation model are the same as the characteristics of the capacitor 1 of the reference model except that the heat exchange amount or pressure loss of one of the heat exchange characteristics is multiplied by the first coefficient K _1. Considered identical.

The multiplication destination of the first coefficient K ₁ can be changed in accordance with the performance of the refrigeration cycle system desired to be satisfied on the design model. For example, when the temperature of the air cooled by the evaporator 2 of the refrigeration cycle system (blowing temperature) is to be kept below a predetermined value, the first coefficient is added to the value of the heat exchange amount in relation to the heat exchange amount with respect to the wind speed of the condenser 1. Multiply by K ₁ Alternatively, when it is desired to suppress the pressure loss of the refrigeration cycle system to a predetermined value or less, the refrigerant pressure loss value may be multiplied by the first coefficient K ₁ in the relationship of the refrigerant pressure loss with respect to the refrigerant flow rate of the condenser 1. As described above, the type of characteristic (heat exchange amount, air pressure loss, refrigerant pressure loss) multiplied by the first coefficient K ₁ corresponds to the performance (temperature, pressure loss) desired to be satisfied in the refrigeration cycle system to be designed. To be determined.

Second coefficient K ₂ is any of the following.
A coefficient multiplied by the heat exchange amount in the characteristics of the heat exchange amount with respect to the wind speed or the refrigerant flow rate in the evaporator 2 (see FIGS. 4A and 4B)
A coefficient by which the air pressure loss is multiplied in the characteristics of the air pressure loss with respect to the wind speed of the air passing outside the evaporator 2 (see FIG. 4C)
A coefficient multiplied by the refrigerant pressure loss in the characteristic of the refrigerant pressure loss with respect to the refrigerant flow rate of the refrigerant passing through the evaporator 2 (see FIG. 4D)

The solid lines in FIGS. 4A to 4D are characteristic graphs defined by the reference model, and the broken lines correspond to characteristic graphs in the calculation model. By the second coefficient K ₂ values, the graph shape is deformed in the vertical direction. That is, the characteristics of the evaporator 2 of the calculation model are considered to be the same as those of the evaporator 2 of the reference model except that the characteristics of the heat exchange amount or pressure loss are multiplied by the second coefficient K ₂ . Note that the multiplication destination of the second coefficient K ₂ can be changed according to the performance of the refrigeration cycle system desired to be satisfied on the design model, similarly to the first coefficient K ₁ . In other words, the type of characteristic (heat exchange amount, air pressure loss, refrigerant pressure loss) multiplied by the second coefficient K ₂ also corresponds to the performance (temperature, pressure loss) desired to be satisfied in the refrigeration cycle system to be designed. Just decide.

The third coefficient K ₃ is a coefficient multiplied by the operating efficiency in the characteristics of the operating efficiency with respect to the rotation speed and pressure ratio of the compressor 3 (see FIG. 5). The solid line in FIG. 5 is a characteristic graph defined by the reference model, and the broken line corresponds to the characteristic graph in the calculation model. By a third value of the coefficient K _3, the graph shape is deformed in the vertical direction. The dimensions of the compressor 3 on the calculation model are the same as the compressor 3 on the reference model. That is, the characteristics of the compressor 3 of the calculation model are considered to be the same as the compressor 3 of the reference model except that the characteristics of the operation model ₃ are multiplied by the third coefficient K3.

The optimization calculation unit 23 calculates parameters that satisfy the target value of the performance of the refrigeration cycle system in the calculation model. For example, when the cooling performance is regarded as important, a parameter is calculated such that the temperature of the air cooled by the evaporator 2 (blowout temperature) is equal to or lower than a predetermined temperature. In other words, an optimization calculation is performed using the blowing temperature as an objective function and the above parameters (first coefficient K ₁ , second coefficient K ₂ , third coefficient K ₃ ) as design variables, and the combination of the above parameters Many are calculated. In addition, when importance is attached to the circulation performance of the refrigerant and the stability of the operation, parameters are calculated such that the pressure loss of the entire refrigeration cycle system is a predetermined value or less. For example, optimization calculation using the total value or average value of pressure loss as an objective function is performed. The optimization calculation is executed under test conditions equivalent to those of an actual vehicle using general-purpose design optimization calculation software.

FIG. 6 is a graph in which combinations of the above parameters (first coefficient K ₁ , second coefficient K ₂ , third coefficient K ₃ ) and the blowing temperature are connected by a broken line. Optimum parameters are, for example, that the blowout temperature is in the range below the target temperature, and that each parameter is in the predetermined range (for example, the range below the upper limit value K _MAX and above the lower limit value K _MIN ). The Note that, in the optimization calculation, a combination in which the blowing temperature exceeds the target temperature may be calculated, but such a combination may be deleted in advance. The position and width of the predetermined range may be individually set according to individual parameters. Also, the closer the parameter value is to 1.0, the smaller the difference from existing systems. Therefore, by including 1.0 in the predetermined range, it is possible to obtain a parameter value that gives an appropriate specification change that does not greatly deviate from the existing system.

[4. flowchart]
FIG. 7 is an example of a flowchart for explaining a control procedure by the computer program 20 described above. This flowchart shows a procedure in the case of calculating parameters such that the temperature of the air cooled by the evaporator 2 (blowout temperature) is equal to or lower than a predetermined temperature.
In step A1, a reference model is created and stored in the storage unit 21 (reference model creation step). For the creation of the reference model, data such as existing vehicle design simulation software, design optimization calculation software, heat flow analysis software, etc. may be used, or the designer may create it manually. In addition, it is preferable to create a model of an existing refrigeration cycle system applied to an actual vehicle on the condition that it is the same vehicle size and the same size as the calculation model.

In step A2, a calculation model in which the heat exchange characteristics of the condenser 1, the heat exchange characteristics of the evaporator 2, and the performance characteristics of the compressor 3 are set is set among the reference models (calculation model setting step). That is, for the condenser 1, among the plurality of heat exchange properties, is multiplied by the first coefficient K ₁ only to the heat exchange amount with respect to wind velocity, for the evaporator 2, among the plurality of heat exchange properties, heat exchange amount with respect to the wind speed only second coefficient K ₂ is multiplied, for the compressor 3, a third coefficient K ₃ is multiplied to the characteristics of the operating efficiency with respect to the rotational speed and pressure ratio. The remaining heat exchange characteristics of the condenser 1 and the evaporator 2 and the dimensions of the condenser 1, the evaporator 2 and the compressor 3 are not changed with respect to the reference model. Thereby, the difference of the calculation model with respect to the reference model is defined by only three parameters of the first coefficient K ₁ , the second coefficient K ₂ , and the third coefficient K ₃ . In addition, an upper limit value K _MAX and a lower limit value K _{MIN for} each coefficient are set. These upper limit value K _MAX and lower limit value K _MIN are set according to the layout in the engine room, the physical size of the device, the cost requirements, and the like.

In step A3, the outlet temperature of the objective function, the first coefficient K _1, the second coefficient K _2, optimizing the third coefficient K ₃ to the design variables calculations are performed (optimization calculation step). Here, for example, when the blowing temperature is set to 10 ° C. or less, each coefficient K ₁ , K ₂ , K ₃ that can generate a blowing temperature of 10 ° C. or each coefficient that can generate a blowing temperature of 8 ° C. A combination of K ₁ , K ₂ , K _3, a combination of coefficients K ₁ , K ₂ , K ₃ that can generate a blowing temperature of 6 ° C. is calculated. By performing the optimization calculation, combinations of parameters and blowing temperatures as shown in FIG. 6 are acquired. These combinations are displayed on the output device 15.

In step A4, the optimum combination of coefficients K ₁ , K ₂ , K ₃ is extracted from a plurality of combinations (extraction step). Here, combinations that satisfy both the conditions of the blowing temperature and the conditions of the upper limit value K _MAX and the lower limit value K _MIN are extracted. This extraction operation may be performed by the designer himself referring to the graph displayed on the output device 15, or may be configured such that the computer program 20 automatically selects.

In step A5, by multiplying the extracted coefficients K ₁ , K ₂ , and K ₃ , the characteristics of the heat exchange amount with respect to the wind speed of the condenser 1 and the evaporator 2 and the operating efficiency with respect to the rotation speed and pressure ratio of the compressor 3 are obtained. While the characteristics are specified, the dimensions of the condenser 1 and the evaporator 2 that satisfy these characteristics, other heat exchange characteristics, the dimensions of the compressor 3, and the like are calculated. The coefficients K ₁ , K ₂ , K ₃ obtained in step A4 are based on the same refrigeration cycle system as the reference model, except for the characteristics changed by the coefficients K ₁ , K ₂ , K ₃ . It is only based on optimization calculation. Step A5 is a step of calculating other characteristics and dimensions through desktop calculations and experiments so that the characteristics changed by the coefficients K ₁ , K ₂ , and K ₃ are actually obtained.

In step A6, it is confirmed whether or not the dimensions and heat exchange characteristics of the condenser 1 and the evaporator 2 calculated in step A5, the dimensions and performance characteristics of the compressor 3, and the like satisfy the condition of the blowing temperature (confirmation step). If the condition of the blowing temperature is satisfied, a calculation model in which the coefficients K ₁ , K ₂ , and K ₃ are substituted becomes a model of the refrigeration cycle system 7 to be obtained. On the other hand, if the condition of the blowing temperature is not satisfied, a combination different from that extracted in step A4 is extracted, and steps A5 to A6 are performed again. Or you may repeat the optimization calculation of step A3 further from the place which acquires another combination further.

[5. effect]
(1) In the above design support device and design support method, the capacities of the condenser 1, the evaporator 2 and the compressor 3 in the design model are simply expressed by the first coefficient K ₁ , the second coefficient K ₂ , and the third coefficient K _3. Is done. By performing optimization calculation using these coefficients K _{1 to} K ₃ as design variables, the amount of calculation can be reduced, and the time required for optimization can be significantly shortened. On the other hand, if the refrigeration cycle system mounted on an existing vehicle is used as a reference model, the simulation accuracy of the entire system can be maintained even if the capacities of the condenser 1, the evaporator 2 and the compressor 3 are expressed by one variable. Can do. Therefore, the design efficiency of the refrigeration cycle system can be improved.

In the design support apparatus and the design support method described above, the type of characteristic (heat exchange amount, air pressure loss, refrigerant pressure loss) to be multiplied by the first coefficient K ₁ and the second coefficient K ₂ is the refrigeration to be designed. It is determined so as to correspond to the performance (temperature, pressure loss) desired to be satisfied in the cycle system. Thereby, even if optimization calculation is performed using a calculation model in which only a part of the reference model is changed, good calculation accuracy can be ensured, and simulation accuracy of the entire system can be maintained. Therefore, the design efficiency of the refrigeration cycle system can be improved.

  In addition, since the refrigerant changes its state (phase transition) inside the condenser 1 and the evaporator 2 of the refrigeration cycle system, it is difficult to predict the correlation between various characteristics as shown in FIGS. . On the other hand, fixing only one design variable for each component of the refrigeration cycle system reduces the number of design variables for the entire system and prevents the inevitable results from being derived. it can. Therefore, the design efficiency of the refrigeration cycle system can be improved.

  (2) In the above design support apparatus and design support method, a refrigeration cycle system in an existing vehicle having the same size (for example, the same vehicle type) as the vehicle on which the refrigeration cycle system to be designed is mounted is used as a reference model. Can be defined. If the size of the vehicle to which the refrigeration cycle system is applied is approximately the same, the size of the condenser 1, the evaporator 2 and the compressor 3 will not be changed greatly, so that the characteristic data will not change greatly. For this reason, even if the data of the reference model is used as part of the data of the calculation model, the calculation accuracy is maintained. Therefore, the simulation accuracy of the entire system can be maintained, and the design efficiency of the refrigeration cycle system can be improved.

  (3) In the design support apparatus and the design support method, the refrigeration cycle system in an existing vehicle having the same vehicle rating as the vehicle on which the refrigeration cycle system to be designed is mounted can be defined as the reference model. In this case, since the performance and manufacturing cost required for the refrigeration cycle system are not significantly changed, the characteristic data does not vary greatly. Therefore, even if the data of the reference model is used as a part of the data of the calculation model, it becomes easier to maintain the calculation accuracy more reliably. Therefore, the simulation accuracy of the entire system can be maintained, and the design efficiency of the refrigeration cycle system can be improved.

(4) As shown in FIGS. 3A to 3B, for example, the first coefficient K ₁ is set as a coefficient to be multiplied by the heat exchange amount in the characteristics of the heat exchange amount with respect to the wind speed or the refrigerant flow rate. Alternatively, as shown in FIG. 3C, in the characteristic of the air pressure loss with respect to the wind speed, it is set as a coefficient to be multiplied by the air pressure loss. Alternatively, as shown in FIG. 3D, in the characteristic of the refrigerant pressure loss with respect to the refrigerant flow rate, it is set as a coefficient to be multiplied by the refrigerant pressure loss. In this way, by making the capacity of the condenser 1 included in the calculation model representative of the heat exchange amount or pressure loss, the simulation accuracy can be improved without greatly changing the tendency (graph shape) of the capacity required for the design of the condenser 1. The amount of calculation can be reduced while maintaining it. Therefore, the design efficiency of the refrigeration cycle system can be improved.

(5) Similarly, the second coefficient K ₂ is set as a coefficient to be multiplied by the heat exchange amount in the characteristics of the heat exchange amount with respect to the wind speed or the refrigerant flow rate, for example, as shown in FIGS. The Alternatively, as shown in FIG. 4C, in the characteristic of the air pressure loss with respect to the wind speed, it is set as a coefficient to be multiplied by the air pressure loss. Alternatively, as shown in FIG. 4D, in the characteristic of the refrigerant pressure loss with respect to the refrigerant flow rate, it is set as a coefficient multiplied by the refrigerant pressure loss. As a result, it is possible to reduce the amount of calculation while maintaining the simulation accuracy without greatly changing the trend (graph shape) of the heat exchange capability in the designed evaporator 2, and to improve the design efficiency of the refrigeration cycle system. Can do.

(6) As shown in FIG. 5, for example, the third coefficient K ₃ is set as a coefficient multiplied by the operating efficiency in the characteristics of the operating efficiency with respect to the rotation speed and pressure ratio of the compressor 3. As a result, it is possible to reduce the amount of calculation while maintaining the simulation accuracy without greatly changing the tendency (graph shape) of the refrigerant pumping ability in the designed compressor 3, and to improve the design efficiency of the refrigeration cycle system. Can do.

[6. Modified example]
In the above-described embodiment, an example in which three coefficients K ₁ , K ₂ , and K ₃ are set in the calculation model is illustrated, but the number of coefficients can be set to a minimum of one. For example, if you want to change the specifications of only the capacitor 1 with respect to the reference model, only the first coefficient K ₁ is set, and the difference between the reference model and the calculation model is expressed only by the first coefficient K _1. It may be a thing. Further, if the reference model it is desired to change the specification only compressor 3 may be set only third coefficient K _3. Setting only the third coefficient K ₃ is synonymous with assuming that the first coefficient K ₁ and the second coefficient K ₂ are 1 (K ₁ = K ₂ = 1). Therefore, when performing the optimization calculation, by setting the upper limit value K _MAX and the lower limit value K _MIN of the first coefficient K ₁ and the second coefficient K ₂ to 1, only when the third coefficient K ₃ is set. Substantially the same control can be realized.

DESCRIPTION OF SYMBOLS 1 Capacitor 2 Evaporator 3 Compressor 4 Expansion valve 5 Blower fan 6 Refrigerant path 7 Refrigeration cycle system 10 Design support device 11 Central processing unit 12 Main storage device 13 Auxiliary storage device 14 Input device 15 Output device 16 Recording device 17 Internal bus 18 Recording medium 20 program 21 storage unit 22 setting unit 23 optimization calculation unit
K ₁ first coefficient
K ₂ second coefficient
K ₃ third coefficient

Claims (4)

A design support device that supports the design of a refrigeration cycle system in which a condenser, an evaporator, and a compressor are interposed on a refrigerant circulation path,
A storage unit for storing a reference model of the refrigeration cycle system in which a plurality of heat exchange characteristics of the condenser and the evaporator and performance characteristics of the compressor are defined;
Based on the reference model, the heat exchange amount or pressure loss in any one of the plurality of heat exchange characteristics of the condenser is multiplied by a first coefficient, and the plurality of the heat exchange characteristics of the evaporator A setting unit for setting a calculation model having a characteristic obtained by multiplying the heat exchange amount or pressure loss in any one of the characteristics by a second coefficient, and having a characteristic obtained by multiplying the operating efficiency of the compressor by a third coefficient; ,
An optimization calculation is performed using the value of performance desired to be satisfied in the refrigeration cycle system to be designed as an objective function of the calculation model, and using the first coefficient, the second coefficient, and the third coefficient as design variables. The optimization calculation unit for calculating a combination of the first coefficient, the second coefficient, and the third coefficient satisfying the performance,
The design support apparatus for a refrigeration cycle system, wherein the type of characteristic multiplied by the first coefficient and the second coefficient is determined to correspond to the performance related to the objective function. The refrigeration cycle system is a refrigeration cycle system mounted on a vehicle,
The refrigeration according to claim 1, wherein the reference model is defined in a refrigeration cycle system of an existing vehicle having a size comparable to the vehicle on which the refrigeration cycle system to be designed is mounted. Design support device for cycle system. The refrigeration cycle system according to claim 2, wherein the reference model is defined in a refrigeration cycle system of an existing vehicle having the same vehicle rating as the vehicle on which the refrigeration cycle system to be designed is mounted. Design support device. A computer-aided design support method for supporting the design of a refrigeration cycle system in which a condenser, an evaporator, and a compressor are interposed on a refrigerant circulation path,
Creating a reference model of the refrigeration cycle system in which a plurality of heat exchange characteristics of the condenser and the evaporator and performance characteristics of the compressor are defined;
With respect to the reference model, the heat exchange amount or pressure loss in any one of the plurality of heat exchange characteristics of the condenser is multiplied by a first coefficient, and the plurality of heat exchange characteristics of the evaporator A heat exchange amount or pressure loss in any one of the characteristics is multiplied by a second coefficient, a calculation model having a characteristic obtained by multiplying the operating efficiency of the compressor by a third coefficient,
An optimization calculation is performed using the value of performance desired to be satisfied in the refrigeration cycle system to be designed as an objective function of the calculation model, and using the first coefficient, the second coefficient, and the third coefficient as design variables. By calculating the combination of the first coefficient, the second coefficient, and the third coefficient that satisfy the performance, the type of characteristic that is multiplied by the first coefficient and the second coefficient is calculated as the objective function. A design support method for a refrigeration cycle system, in which a computer executes a procedure for determining so as to correspond to the performance.

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