JP2011220559A - Refrigerating/air conditioning device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerating/air conditioning device of high reliability which is controllable and can maintain its performance even when a plurality of use-side units are applied.SOLUTION: This refrigerating/air conditioning device 1000 includes: a heat source unit 100 constituted of a compressor 1 and a heat source-side heat exchanger 2; two or more use units 200a, 200b constituted of expanding mechanisms 5a, 5b, use-side heat exchangers 6a, 6b, and internal heat exchangers 4a, 4b; a suction pressure sensor 12 and a discharge pressure sensor 11 constituted of liquid extension piping 3 and gas extension piping 7 and respectively disposed at an inlet and an outlet of the compressor 1; internal heat exchange low-pressure outlet temperature sensors 13a, 13b disposed at low pressure-side outlets of the use-side heat exchangers 6a, 6b; use-side heat exchange inlet temperature sensors 14a, 14b disposed at inlets of the use-side heat exchangers 6a, 6b; and sucked air temperature sensors 15a, 15b for detecting temperatures of load use fluids flowing into the use-side heat exchangers 6a, 6b.

Description

  The present invention relates to a refrigeration air conditioner, and more particularly to a refrigeration air conditioner that executes a refrigeration cycle and includes a heat source unit and a plurality of utilization units.

  A conventional refrigeration air conditioner has a compressor that compresses refrigerant, a condenser, a decompression device, an evaporator, and a refrigerant pipe that circulates the refrigerant by connecting them in a ring shape, and executes a refrigeration cycle. Was. And the warm heat discharge | released in a condenser was utilized, or the cold heat discharge | released in an evaporator was utilized. At this time, for the purpose of increasing the efficiency of the refrigeration cycle, heat exchange is performed between the refrigerant that exits the condenser and enters the decompression device, and the refrigerant that exits the evaporator and enters the compressor. And a control device that adjusts the flow rate of the decompression device so that the superheat degree of the refrigerant at the inlet of the compressor becomes a desired target superheat degree is disclosed (for example, see Patent Document 1).

JP 2009-162388 A (page 5-7, FIG. 1)

However, the refrigeration air conditioner disclosed in Patent Document 1 has the following problems.
(A) Although control is possible when there is one usage-side unit, when there are multiple usage-side units, it is necessary to change the opening area of the decompression device according to the cooling target load of each usage-side unit Therefore, it cannot respond and the temperature of the cooling target cannot be individually controlled to the set temperature.
(Ii) Also, when the refrigerant state at the compressor inlet is controlled to a predetermined target superheat degree, depending on the case, the refrigerant has two phases in the refrigerant pipe (gas extension pipe part). When it is long, the pressure loss becomes large with respect to the gas single phase. For this reason, the pressure (low pressure) of the refrigerant sucked by the compressor is lowered, and there is a possibility that performance and reliability are lowered.

  In view of the above problems, an object of the present invention is to obtain a highly reliable refrigeration air conditioner that can be controlled even when there are a plurality of usage-side units, maintains performance, and has high reliability.

The refrigerating and air-conditioning apparatus according to the present invention has a heat source unit and at least two utilization units,
The heat source unit is composed of a compressor that compresses the refrigerant, and a heat source side heat exchanger into which the high-pressure refrigerant discharged from the compressor flows,
The utilization unit is connected to the outlet of the heat source side heat exchanger by a liquid extension pipe, and an expansion mechanism into which the high pressure refrigerant flowing out from the heat source side heat exchanger flows, and the low pressure refrigerant flowing out from the expansion mechanism flows in Heat exchange between the use-side heat exchanger, the high-pressure refrigerant flowing into the expansion mechanism and the low-pressure refrigerant flowing out from the use-side heat exchanger, and connected to the inlet of the compressor by a gas extension pipe It consists of a heat exchanger and
Superheat degree detection means for detecting the superheat degree of the low-pressure refrigerant at the outlet of the use side heat exchanger;
Inflow utilization fluid temperature detection means or outflow utilization fluid that detects the temperature at the inlet or the outlet of the utilization side heat exchanger of the utilization fluid that passes through the utilization side heat exchanger and exchanges heat with the low-pressure refrigerant. Temperature detection means;
Inflow utilization fluid temperature setting means or outflow utilization fluid temperature setting means for setting the temperature at the inlet of the utilization side heat exchanger or the temperature at the outlet of the utilization fluid;
The target refrigerant state quantity for setting the target superheat degree or the target dryness at the low-pressure side outlet of the internal heat exchanger according to the size of each cooling load obtained from the inflow utilization fluid temperature setting means or the outflow utilization fluid temperature setting means Computing means;
Flow rate adjustment control means for adjusting the flow rate of the expansion mechanism so as to achieve the superheat or target dryness at the low pressure side outlet of the internal heat exchanger;
It is provided with.

Since the present invention is configured as described above, by controlling the refrigerant state quantity at the low-pressure side outlet of the internal heat exchanger according to the cooling load of each of the plurality of utilization units, by preventing frequent start and stop, It is possible to realize an operation with high controllability with a small temperature fluctuation with respect to the set temperature of the object to be cooled (used fluid).
In addition, since the evaporation temperature of the use side heat exchanger can be kept high, highly efficient operation can be realized. Furthermore, in a low temperature environment where the evaporation temperature is negative (below freezing point), the amount of frost formation is reduced, and the energy required for defrosting can be reduced.
And by appropriately controlling the refrigerant state quantity in the gas extension pipe and minimizing the pressure loss, it is possible to realize a highly reliable operation maintaining the cooling performance.

The block diagram which shows the refrigerant circuit of the refrigerating air-conditioning apparatus which concerns on Embodiment 1 of this invention. The ph diagram explaining the effect of the internal heat exchanger of the refrigeration air conditioner shown in FIG. The characteristic view showing the relationship of the cooling capacity with respect to the dryness in a use side heat exchanger exit. The characteristic view showing the relationship of the heat transfer coefficient with respect to the refrigerant | coolant mass flow rate of an internal heat exchanger. The ph diagram showing the part from the inlet_port | entrance in the low voltage | pressure side of an internal heat exchanger to an exit. The ph diagram showing the refrigerating cycle of the refrigerating air-conditioner shown in FIG. The characteristic view showing the effect | action by the opening degree of the expansion mechanism of a low load side utilization unit. The block diagram which shows the refrigerant circuit of the refrigerating air conditioning apparatus which concerns on Embodiment 2 of this invention. The block diagram which shows the refrigerant circuit of the refrigerating air conditioning apparatus which concerns on Embodiment 3 of this invention. The characteristic view which shows the relationship between the dryness in the refrigeration air conditioner shown in FIG. 9, and a pressure loss.

[Embodiment 1]
1 to 7 illustrate a refrigerating and air-conditioning apparatus according to Embodiment 1 of the present invention. FIG. 1 is a configuration diagram illustrating a refrigerant circuit, and FIG. 2 is a p-type illustrating the effect of an internal heat exchanger. h diagram (Mollier diagram), FIG. 3 is a characteristic diagram showing the relationship of the cooling capacity to the dryness at the outlet of the use side heat exchanger, and FIG. 4 is a heat transfer coefficient (liquid side) with respect to the refrigerant mass flow rate of the internal heat exchanger. Fig. 5 is a characteristic diagram showing the relationship between the heat transfer rate, the gas side heat transfer rate, and the heat transfer rate. Fig. 5 is a ph diagram showing an enlarged portion from the inlet to the outlet on the low pressure side of the internal heat exchanger. 6 is a ph diagram representing the refrigeration cycle, and FIG. 7 is an action when the opening degree of the expansion mechanism of the low load side use unit is changed (cooling capacity and use side heat exchanger outlet overheating). It is a characteristic view showing the relationship between the degree of pressure and the low pressure side outlet superheat degree of the internal heat exchanger. In the drawings, the same or corresponding parts are denoted by the same reference numerals, and a part of the description is omitted.

(Refrigerant circuit)
FIG. 1 includes a refrigerating and air-conditioning apparatus 1000, a heat source unit 100, and utilization units 200a and 200b installed in parallel, and both are connected in an annular shape by a liquid extension pipe 3 and a gas extension pipe 7. The heat source unit 100 includes a compressor 1 and a heat source side heat exchanger 2. The usage units 200a and 200b are installed in the refrigerator compartments 300a and 300b, respectively, and are configured by internal heat exchangers 4a and 4b, expansion mechanisms 5a and 5b, and usage-side heat exchangers 6a and 6b, respectively. The expansion mechanisms 5a and 5b are electronic expansion valves whose opening degrees are variably controlled.

The heat source side heat exchanger 2 and the use side heat exchangers 6a and 6b are fluids such as air, water or brine supplied by a fan, a pump or the like (not shown) (referred to as “use fluid” in the present invention). ) To exchange heat. In addition, although Embodiment 1 demonstrates as a structure what heat-exchanges between air, this invention does not limit a utilization fluid to this.
Moreover, although the case where the heat source unit 100 is connected to one unit and the two usage units 200a and 200b are connected will be described, it goes without saying that the same can be implemented even when three or more usage units are connected. The refrigerant used in the refrigerating and air-conditioning apparatus 1000 is, for example, an HFC refrigerant such as R410A, R407C, or R404A, an HCFC refrigerant such as R22 or R134a, or a natural refrigerant such as hydrocarbon or helium.

(sensor)
Further, as a sensor for detecting the pressure and temperature of the refrigerant circuit, the heat source unit 100 includes a discharge pressure sensor 11 for detecting the pressure of the discharge portion of the compressor 1 and a suction pressure for detecting the pressure of the suction portion of the compressor 1. A sensor 12 is installed.
The utilization units 200a and 200b include an internal heat exchanger low-pressure outlet temperature sensor 13a that detects a refrigerant temperature at the low-pressure outlet of each of the internal heat exchangers 4a and 4b (hereinafter referred to as “internal heat exchanger low-pressure outlet temperature”). , 13b, and utilization side heat exchange inlet temperature sensors 14a, 14b for detecting refrigerant temperatures at the inlets of the utilization side heat exchangers 6a, 6b (same as the evaporation temperature, hereinafter referred to as “use side heat exchange inlet temperature”); , Is provided.
Furthermore, in each of the refrigerator compartments 300a and 300b, suction air temperature sensors 15a and 15b for detecting the temperature of the use fluid (same as the inside air) flowing into the use side heat exchangers 6a and 6b, and a use temperature (warehouse). In-chamber temperature setting means 24a and 24b are set so as to set the desired temperature to be the same as the temperature of the internal air.

(Measurement control device)
In the heat source unit 100, the measurement control device 20 connected to the sensors, the internal temperature setting means 24a and 24b, and the expansion mechanisms 5a and 5b is installed.
The measurement control device 20 receives measurement information (pressure and temperature) at each location detected by each sensor and setting information (in-house set temperature and operation details) set by the user. Based on the setting information, such as the operation method of the compressor 1, the air flow rate of each fan blown toward the heat source side heat exchanger 2 and the use side heat exchangers 6a and 6b, and the opening degrees of the expansion mechanisms 5a and 5b, etc. A control signal is output.

  The measurement control device 20 not only functions as the control device as described above, but also functions as a calculation processing unit of the refrigerant state quantity calculation means 21, the target refrigerant state quantity calculation means 22, and the correction means 23 ( However, in FIG. 1, they are described for convenience as if they were incorporated.

(Refrigerant state quantity calculation means)
The refrigerant state quantity calculation means 21 includes internal heat exchange low-pressure outlet temperature sensors 13a and 13b, use side heat exchange inlet temperature sensors 14a and 14b, and a measurement control device 20, and the internal heat exchange low-pressure outlet temperature sensors 13a and 13b. The degree of superheat at the outlets of the internal heat exchangers 4a and 4b is obtained based on the outputs of the use side heat exchange inlet temperature sensors 14a and 14b. Details of the calculation process of the refrigerant state quantity calculation means 21 will be described later.

(Target refrigerant state quantity calculation means)
The target refrigerant state quantity calculation means 22 is composed of intake air temperature sensors 15a and 15b, internal temperature setting means 24a and 24b, and a measurement control device 20, and the temperatures detected by the intake air temperature sensors 15a and 15b, The target refrigerant state quantity is set based on the deviation from the temperature set by the internal temperature setting means 24a, 24b and the result of the refrigerant state quantity calculating means 21. Details of the calculation process of the target refrigerant state quantity calculation means 22 will be described later.

(Correction means)
The correction unit 23 includes the expansion mechanisms 5a and 5b and the measurement control device 20. Based on the opening degree of the expansion mechanisms 5a and 5b and the result of the refrigerant state quantity calculation unit 21, all of the expansion mechanisms 5a and 5b are corrected. Correct the opening. The details of the calculation process of the correction means 23 will be described later.

  In addition, although FIG. 1 demonstrates the case where the heat source unit 100 is connected to one unit and two usage units 200a and 200b arranged in parallel are connected, it can be similarly implemented even when three or more usage units are connected. Needless to say. The refrigerant used in the refrigerating and air-conditioning apparatus 1000 includes, for example, HFC refrigerants such as R410A, R407C, and R404A, HCFC refrigerants such as R22 and R134a, or natural refrigerants such as hydrocarbon and helium.

(Driving operation without internal heat exchanger)
Next, the difference of the driving | operation operation | movement by the presence or absence of the internal heat exchangers 4a and 4b of the refrigerating and air-conditioning apparatus 1000 is demonstrated based on a ph diagram (Mollier diagram).
In FIG. 2A, when there are no internal heat exchangers 4a and 4b, the high-pressure and high-temperature gas refrigerant discharged from the compressor 1 (state B0, hereinafter referred to as “high-pressure and high-temperature refrigerant”) is a heat source side heat exchanger. 2 is condensed and liquefied while dissipating heat to become a high-pressure medium-temperature refrigerant (state C0, hereinafter referred to as “high-pressure medium-temperature refrigerant”).
Then, the refrigerant that has exited the heat source side heat exchanger 2 passes through the liquid extension pipe 3 and is divided into use units 200a and 200b, and is decompressed to a low pressure in the expansion mechanisms 5a and 5b, respectively, to become a two-phase refrigerant (state D0, Hereinafter referred to as “low pressure low temperature refrigerant”). After that, it flows into the use side heat exchangers 6a and 6b, absorbs heat there, and supplies cold energy to the use fluid (load side medium such as air or water) while evaporating gas (state A0, hereinafter referred to as “low pressure medium temperature refrigerant”) Called).

Since the heat transfer coefficient of the refrigerant is generally higher in the two-phase refrigerant than in the gas refrigerant, the heat exchange performance is improved and the performance of the refrigeration air conditioner is improved.
Further, the low-pressure intermediate temperature refrigerant (same as the intake refrigerant) sucked by the compressor 1 expands to become “positive value” in order to prevent the compressor 1 from being damaged due to a compressor failure caused by liquid compression. It is necessary to adjust the flow rate in the mechanisms 5a and 5b.
When the internal heat exchangers 4a and 4b are not provided, the “superheat degree SHe (temperature difference between the state E0 that is an intersection with the saturated gas line and the state A0)” at the outlets of the use side heat exchangers 6a and 6b is illustrated. As shown in (a) of 2, for example, the opening degree of the expansion mechanisms 5a and 5b is controlled with “SHe = 5 ° C.” as a control target.

At this time, if the temperature difference between “internal temperature RT” and “evaporation temperature Te” is “utilization temperature difference TD”, there is a relationship of “TD> SHe”.
For this reason, the evaporation temperature Te is lower than the internal temperature RT by at least the degree of superheat SHe. That is, when the internal temperature RT = −30 ° C. and the superheat degree SHe = 5 ° C., the evaporation temperature Te is a temperature of −35 (= −30−5) ° C. or lower. FIG. 2 (a) shows the evaporation temperature Te = −40 (−30−10) ° C. with the use temperature difference TD = 10 ° C.

Further, the low-pressure and medium-temperature refrigerants that have exited from the use side heat exchangers 6 a and 6 b join together and are sucked into the compressor 1 through the gas extension pipe 7. Therefore, a refrigeration cycle (refrigerant is a circulation circuit) that returns to state A0 again through state A0, state B0, state C0, and state D0 is formed.
In FIG. 2B, when there is no internal heat exchanger 4a, 4b, the state change of the refrigerant in the use side heat exchangers 6a, 6b is caused by the degree of superheat at the outlets of the use side heat exchangers 6a, 6b. The opening degree of the expansion mechanisms 5a and 5b is adjusted and controlled so as to be secured. For this reason, a part of utilization side heat exchanger 6a, 6b becomes superheated gas.

(Operations when there is an internal heat exchanger)
In FIG. 2C, when there are internal heat exchangers 4a and 4b, the refrigerant cooled in the heat source side heat exchanger 2 (hereinafter referred to as “high pressure / intermediate temperature refrigerant”) is used in each of the usage units 200a and 200b. Then, in the internal heat exchangers 4a and 4b, heat is exchanged with the refrigerant evaporated in the use side heat exchangers 6a and 6b (hereinafter referred to as “low-pressure low-temperature refrigerant”) (cooling is received), and cooling is performed. (State C1).
The low-pressure cold / warm refrigerant (state D1) adiabatically expanded in the expansion mechanisms 5a, 5b flows into the use-side heat exchangers 6a, 6b and evaporates to become low-pressure medium-temperature refrigerant (state E1). Further, the internal heat exchangers 4a and 4b exchange heat with the high-pressure intermediate-temperature refrigerant (receive the heat) and are heated (state A1).

Here, when there are the internal heat exchangers 4a and 4b, the “superheat degree SHL” of the low-pressure intermediate temperature refrigerant at the outlet of the internal heat exchangers 4a and 4b is controlled to, for example, “SHL = 5 ° C.”. At this time, the superheat degree of the low-pressure intermediate temperature refrigerant at the outlets of the use side heat exchangers 6a and 6b becomes smaller than the “superheat degree SHL”, and a state close to saturated gas can be realized.
Therefore, the evaporating temperature Te is equal to or lower than the internal temperature RT-0 ° C., that is, the evaporating temperature Te is increased to near the internal temperature, so that the low-pressure pressure is increased, and a highly efficient operation can be realized on the refrigeration cycle. In addition, when the refrigeration air conditioner 1000 is used in an environment where the evaporation temperature Te is below freezing (0 ° C. or lower) as in a refrigerated warehouse, frost formation occurs on the use side heat exchangers 6a and 6b. Since the evaporating temperature Te is increased by the internal heat exchangers 4a and 4b, the amount of frost formation is reduced, and the energy required for defrosting by a heater or the like can be reduced.

  In addition, in the internal heat exchangers 4a and 4b, the high-pressure intermediate temperature refrigerant is cooled, so that the enthalpy is reduced, and “the degree of supercooling SC (the temperature difference between the state C0 that is the intersection with the saturated gas line and the state C1). ) "Increases. For this reason, since the refrigerating effect is increased and the refrigerant circulation amount necessary for exhibiting the same cooling capacity can be reduced, a highly efficient operation can be realized by reducing the operating capacity of the compressor.

  In FIG. 2D, when there are internal heat exchangers 4a and 4b, the opening degree of the expansion mechanisms 5a and 5b is adjusted and controlled so that the degree of superheat is secured at the outlets of the internal heat exchangers 4a and 4b. By doing so, it is possible to realize a refrigerant state in which the entire use side heat exchangers 6a and 6b are in two phases.

(Expansion mechanism control method)
Next, a method for controlling the expansion mechanisms 5a and 5b in the refrigerant circuit equipped with the internal heat exchangers 4a and 4b will be described. The expansion mechanisms 5a and 5b are connected to the "internal heat exchanger low pressure outlet temperature (state A1)" detected by the internal heat exchanger low pressure outlet temperature sensors 13a and 13b and "low pressure" detected by the use side heat exchanger inlet temperature sensors 14a and 14b. The “superheat degree SHL at the outlet of the internal heat exchanger”, which is a temperature difference from the saturation temperature of the low-temperature refrigerant (state E1), becomes a preset “control target value SHLm”, for example, “SHLm = 5 ° C.” Controlled.
When the degree of superheat SHL is larger than the control target value SHLm (SHL> SHLm), the opening degree of the expansion mechanisms 5a and 5b is large, and conversely, when the degree of superheat SHL is smaller than the control target value SHLm (SHL> SHLm). The opening degree of the expansion mechanisms 5a and 5b is controlled to be small.

That is, when the target value of the refrigerant superheat degree, which is the control target of the expansion mechanisms 5a and 5b, is set larger than the refrigerant superheat degree generated by the heat exchange in the internal heat exchangers 4a and 4b, the use side heat The outlet refrigerant state of the exchangers 6a and 6b becomes a superheated gas state (x> 1.0) in which “dryness x” is greater than 1, and performance is deteriorated.
On the other hand, when the target value of the refrigerant superheat degree is set to be small, the refrigerant state at the outlet of the use side heat exchangers 6a and 6b is a two-phase state (x <1.0) with a dryness x of 1 or less. Become.

In the relationship between the dryness and the cooling capacity at the outlets of the use side heat exchangers 6a and 6b shown in FIG. 3, the refrigerant state at the outlet of the use side heat exchangers 6a and 6b is “two-phase (x <1.0) ", the cooling capacity is maximized. For this reason, from the viewpoint of increasing the efficiency of the refrigeration cycle, the refrigerant is overheated so that the refrigerant state at the outlets of the use side heat exchangers 6a and 6b becomes “dryness x is 1 or less” according to the internal heat exchange amount. It is desirable to set a target value for the degree.
In this refrigeration cycle, the degree of superheat SHL at the outlets of the internal heat exchangers 4a and 4b is generated by heat exchange with the high-pressure medium-temperature refrigerant in the internal heat exchangers 4a and 4b, and thus changes according to the amount of heat exchange. .

(Temperature efficiency of internal heat exchanger)
Next, the temperature efficiency ε of the internal heat exchangers 4a and 4b will be described. The temperature efficiency of the internal heat exchanger can generally be defined by (Equation 1). Also, it can be expressed by (Expression 2), and the heat transmission rate K in (Expression 2) is expressed by (Expression 3).

here,
TLO: Internal heat exchange low pressure side outlet temperature,
TLI: Internal heat exchange low pressure side inlet temperature,
THI: Internal heat exchange high pressure inlet temperature,
A: Heat transfer area in which heat exchange is performed between the high-pressure intermediate temperature refrigerant and the low-pressure intermediate temperature refrigerant in the internal heat exchanger
[m2],
K: heat passage rate of internal heat exchanger [kW / m2K],
Gr: refrigerant circulation amount of low-pressure gas refrigerant [kg / s],
Cpg: constant-pressure gas specific heat [kJ / kgK] on the low-pressure side.

That is, as shown in (Equation 3), the heat transfer rate K includes the high pressure liquid side heat transfer rate α1 [kW / m2K], the low pressure gas side heat transfer rate αg [kW / m2K], and the heat transfer rate of the internal heat exchanger. It is defined by the thickness L [m] of the surface and the thermal conductivity λ [kW / mK] of the heat transfer surface.
In FIG. 4, the heat passage rate K is substantially proportional to the refrigerant circulation amount Gr. That is, the value of K / Gr is constant. The constant-pressure gas specific heat can be assumed to be a constant value because the evaporation temperature Te is substantially constant if the use environment conditions in the storage are the same. Further, since the heat transfer area A is determined by the specifications of the internal heat exchanger, it is a constant value. Therefore, the temperature efficiency ε in (Equation 2) is always a constant value.

(Saturated gas state)
Here, the state in the case where “the dryness x is a saturated gas of 1” at the outlets of the use side heat exchangers 6a and 6b capable of realizing the highly efficient operation of the refrigeration air conditioner 1000 will be described.
In (Expression 1), THI is the temperature of the high-pressure intermediate temperature refrigerant (internal heat exchange high-pressure inlet temperature) at the high-pressure side inlets of the internal heat exchangers 4a and 4b, and this is the saturation converted from the discharge pressure sensor 11. Approximately equal to temperature. TLI is the temperature of the low-pressure intermediate temperature refrigerant at the low-pressure side inlets of the internal heat exchangers 4a and 4b (internal heat exchange low-pressure side inlet temperature), but the “dryness x” at the outlets of the use-side heat exchangers 6a and 6b. Is equal to 1 ”, which is equal to the saturation temperature detected by the use side heat exchange inlet temperature sensors 14a and 14b.

  From the above, since the temperature efficiency ε is constant, the temperature change amount ΔSH (= TLO−TLI) on the low pressure side of the internal heat exchanger is calculated using (Expression 4) from the pressure and temperature information attached to the refrigeration cycle apparatus. be able to.

As shown in FIG. 5, the superheat degree of the outlets of the use side heat exchangers 6a and 6b is “SHe”, and the superheat degree of the low pressure side outlets of the internal heat exchangers 4a and 4b is “low pressure side outlet superheat degree SHL”. In this case, if the control target value of the low pressure side outlet superheat degree SHL is controlled to be “control target value ΔSH”, the cooling capacity of the use side heat exchangers 6a and 6b can be maximized, and the efficiency can be improved. High driving can be realized.
In FIG. 5, since “SHL> ΔSH” is satisfied, in order to set the superheat degree SHe at the outlets of the use side heat exchangers 6a and 6b to 0 (zero), the opening degrees of the expansion mechanisms 5a and 5b. You can open it.

(When the load on the used unit is different)
Next, a control method in the case where there are a plurality of utilization units, which is a feature of the present invention, and the cooling load of each utilization liquid (cooling target) is different will be described with reference to FIGS. Here, for the sake of convenience, a description will be given assuming an operating state when the load to be cooled of the usage unit 200b is small with respect to the usage unit 200a.

First, the high-pressure intermediate temperature refrigerant that has exited the heat source side heat exchanger 2 and passed through the liquid extension pipe 3 is divided and flows into the utilization units 200a and 200b, respectively. Since the low pressures are equal, the use unit 200a side with a large cooling load needs to exhibit the maximum cooling capacity, so the degree of superheat SHLa at the outlet of the internal heat exchanger 4a is controlled by controlling the opening of the expansion mechanism 5a. The target value ΔSH may be controlled (SHLa≈ΔSH).
On the other hand, in order to reduce the cooling capacity, the utilization unit 200b having a small cooling load controls the superheat degree SHLb at the outlet of the internal heat exchanger 4b to be equal to or greater than the control target value ΔSH (SHLa> ΔSH), thereby expanding the expansion mechanism. What is necessary is just to restrict | squeeze the opening degree of 5b, to reduce a refrigerant | coolant circulation amount, and to reduce cooling capacity.

  Here, the magnitude of the cooling load is determined by the temperature detected by the current intake air temperature sensors 15a and 15b with respect to the temperature set by the internal temperature setting means 24a and 24b. For example, when the intake air temperature is higher than the internal set temperature, the cooling load is large, and the larger the deviation amount, the larger the load.

(Control method to reduce cooling capacity)
Next, a control method for reducing the cooling capacity will be described with reference to FIG. FIG. 7 shows the relationship of the opening degree of the expansion mechanism 5b, the use side heat exchanger outlet superheat degree SHe, and the internal heat exchanger outlet superheat degree SHL with respect to the cooling capacity of the use unit 200b.
From FIG. 7, it can be seen that if the opening of the expansion mechanism 5b is reduced and the refrigerant flow rate is reduced, the cooling capacity is reduced. The cooling capacity is maximized when the utilization side heat exchanger outlet superheat degree SHe is 0 (zero), and the cooling capacity decreases as the utilization side heat exchanger outlet superheat degree SHe increases.

  The upper limit value of the use side heat exchanger outlet superheat degree She is “use temperature difference TD = internal temperature RT−evaporation temperature Te” shown in FIG. In addition, the internal heat exchanger outlet superheat degree SHL changes while satisfying the relationship of “SHL = SHe + ΔSH”, but in the state where the cooling capacity is 0 (zero), that is, the refrigerant circulation amount hardly flows, the temperature efficiency Since ε is close to 1, the internal heat exchanger low pressure side outlet temperature TLO rises to the internal heat exchanger high pressure side inlet temperature THI from (Equation 3). Therefore, the upper limit value of the internal heat exchanger outlet superheat degree SHL is “utilization temperature difference TD = internal heat exchange high pressure side inlet temperature THI−evaporation temperature Te” shown in the figure.

  Thus, since it becomes possible to control cooling capacity according to superheat degree SHL in the exit of internal heat exchanger 6a, 6b, when the required cooling capacity ratio with respect to maximum cooling capacity is set to QR [%], superheat degree The SHL target superheat degree SHLm is defined by (Equation 5), and if the superheat degree is controlled to the target, the cooling capacity can be controlled according to the cooling load.

Further, as can be seen from FIG. 7, when the opening degree of the expansion mechanism 5b is close to closing, the relationship of “SHL> TD + ΔSH” is established, and therefore, the command opening degree of the measurement control device 20 is “SHL”. When the relationship of “> TD + ΔSH” is satisfied, the opening ratio of the expansion mechanism 5b can be determined to be an opening degree that closes.
Therefore, if the opening degree SJ of the expansion mechanism 5b satisfying such a condition is stored as “closing opening degree SJmin”, the opening degree at which the cooling capacity becomes 0 (zero) is the closing opening degree SJmin. Since the cooling capacity is proportional to the refrigerant circulation amount, that is, the opening degree, when it is desired to set the cooling capacity ratio to the required cooling capacity ratio QR [%] with respect to the current cooling capacity, the opening degree SJnow of the current expansion mechanism. On the other hand, the opening degree SJ defined by (Equation 6) may be set.

  Since the closing opening SJmin of the expansion mechanisms 5a and 5b has a product variation, a predetermined value is set in advance, and the opening when the superheat degree satisfies the condition of “SHL> TD + ΔSH” is SJmin. By correcting, it is possible to realize an operation with high controllability of cooling capacity that eliminates product variations.

  As described above, according to the first embodiment, by controlling the expansion mechanisms 5a and 5b according to the degree of superheat of the low-pressure intermediate temperature refrigerant at the outlets of the use side heat exchangers 6a and 6b, the load to be cooled is reduced. When the load is large, high-efficiency operation is performed, and when the load is small, the cooling capacity can be adjusted to the load. For this reason, by preventing frequent start / stop, it is possible to obtain a refrigeration air conditioner 1000 that can suppress temperature fluctuation with respect to the set temperature of the cooling target to be small and can realize highly controllable operation.

[Embodiment 2]
FIG. 8 is a configuration diagram showing a refrigerant circuit for explaining a refrigerating and air-conditioning apparatus according to Embodiment 2 of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals, and a part of the description is omitted. In FIG. 8, the refrigerating and air-conditioning apparatus 2000 is different from the refrigerating and air-conditioning apparatus 1000 according to the first embodiment in that the internal heat exchangers 4a and 4b have internal heat exchange high-pressure inlet temperature sensors 16a and 16b at the high-pressure side inlet and the high-pressure side outlet. Heat exchanger high pressure outlet temperature sensors 17a and 17b are added. The heat exchange amount QH [kW] on the high pressure side can be obtained from (Equation 7), and the heat exchange amount QL [kW] on the low pressure side can be obtained from (Equation 8). In the internal heat exchangers 4a and 4b, since the relationship of “QH = QL” is established, (Equation 9) is derived.

here,
GrH: High-pressure side refrigerant circulation rate [kg / s],
hHO: Internal heat exchange high pressure side outlet enthalpy [kJ / kg],
hHI: Internal heat exchange high pressure side inlet enthalpy [kJ / kg],
GrL: Low-pressure side refrigerant circulation rate [kg / s],
hLO: Internal heat exchange low pressure side outlet enthalpy [kJ / kg]
TLI: Internal heat exchange low pressure side inlet enthalpy [kJ / kg].

hLO is a refrigerant physical property formula based on the pressure or suction pressure converted from the evaporation temperature detected by the use side heat exchange inlet temperature sensors 14a and 14b and the temperature detected by the internal heat exchange low pressure outlet temperature sensors 13a and 13b. It is possible to calculate with. The hHI can be calculated from the discharge pressure and the temperature detected by the internal heat exchange high pressure inlet temperature sensors 16a and 16b by the refrigerant physical property formula. Further, hHO can be calculated from the discharge pressure and the temperature detected by the internal heat exchange high pressure outlet temperature sensors 17a and 17b by the refrigerant physical property formula.
Therefore, the internal heat exchange inlet enthalpy, that is, the outlet enthalpy hLI of the use side heat exchangers 6a and 6b can be calculated from the above. If the exit enthalpy hLI is obtained, the internal heat exchange inlet dryness x, that is, the “exit dryness xLO” of the use side heat exchangers 6a and 6b can be calculated by (Equation 10).

ここで、
ｈｓｌ：蒸発温度に対する飽和液エンタルピー、
ｈｓｇ：蒸発温度に対する飽和ガスエンタルピー、を表す。

here,
hsl: saturated liquid enthalpy with respect to the evaporation temperature,
hsg: Saturated gas enthalpy with respect to the evaporation temperature.

As described above, according to the second embodiment, the temperature sensors are arranged at the high-pressure side inlet and the outlet of the internal heat exchangers 4a and 4b, respectively, and the heat balance between the high-pressure side and the low-pressure side in the internal heat exchangers 4a and 4b. From the equation, since the “dryness x state” of the refrigerant at the outlet of the use side heat exchangers 6a and 6b can be measured, even when the operation state varies depending on the load, the use side heat exchangers 6a and 6b The expansion mechanisms 5a and 5b can be controlled in accordance with the state of the dryness x at the outlet.
As a result, when the load to be cooled is large, high-efficiency operation is performed, and when the load is small, operation that matches the cooling capacity to the load is possible. For this reason, the refrigeration air conditioner 2000 which can implement | achieve operation with high controllability with small temperature fluctuation with respect to preset temperature of cooling object can be obtained by preventing frequent start / stop.

[Embodiment 3: Refrigeration air conditioner]
9 and 10 illustrate a refrigeration and air-conditioning apparatus according to Embodiment 3 of the present invention. FIG. 9 is a configuration diagram showing a refrigerant circuit, and FIG. 10 is a relationship between the dryness of the refrigerant and the pressure loss of the piping. FIG. The same parts as those in the first embodiment are denoted by the same reference numerals, and a part of the description is omitted.

  In FIG. 9, the refrigeration air conditioner 3000 adds a heat source side internal heat exchanger 9 between the heat source side heat exchanger 2 and the liquid extension pipe 3 to the refrigeration air conditioner 1000 (Embodiment 1). A heat source side internal heat exchanger high pressure inlet temperature sensor 18 is added to the inlet, a heat source side internal heat exchanger high pressure outlet temperature sensor 19 is added to the high pressure side outlet, and a heat source side internal heat exchanger low pressure outlet temperature sensor 30 is connected to the low pressure side outlet. It is added.

  In the relationship between the pressure loss of the pipe with respect to the dryness of the refrigerant at the pipe inlet shown in FIG. 10, it can be seen that when the dryness of the refrigerant is near 1, the pressure loss is the smallest when the dryness of the refrigerant is 1. Therefore, when the dryness of the inlet of the gas extension pipe 7 is set to 1, a highly efficient operation with little pressure loss can be realized.

In the refrigerating and air-conditioning apparatuses 1000 and 2000 (Embodiments 1 and 2), the gas extension pipe 7 has a dryness greater than 1 because the superheated gas refrigerant of the use units 200a and 200b merges. For this reason, the pressure loss becomes larger than the case where the pressure loss flows into the gas extension pipe 7 with “dryness x = 1”.
Therefore, by adding the heat source side internal heat exchanger 9, the heat source side internal heat exchange high pressure inlet temperature sensor 18 and the heat source side internal heat exchange high pressure outlet temperature are obtained in the same manner as in the refrigeration air conditioner 2000 (Embodiment 2). The dryness of the gas extension pipe 7 can be measured based on the temperatures detected by the sensor 19 and the heat source side internal heat exchanger low-pressure outlet temperature sensor 30, respectively.

Therefore, the inflow dryness of the gas extension pipe 7 is controlled so that the utilization side heat exchanger outlet dryness of the utilization unit 200a having a large cooling load is less than 1, and merged with the superheated gas flowing out from the utilization unit 200b having a small cooling load. The most efficient operation can be achieved by controlling the expansion mechanisms 5a and 5b so that the “dryness x of the refrigerant is 1”.
In the refrigeration air conditioner 3000, it goes without saying that the longer the gas extension pipe 7, the greater the control effect.

  As described above, according to the refrigeration air conditioner 3000, the expansion mechanism 5a, the “dryness x of the refrigerant flowing through the gas extension pipe 7 from the heat balance type in the heat source side internal heat exchanger 9 is 1”, By controlling 5b, a highly efficient operation with little pressure loss in the gas extension pipe 7 can be realized.

  1: compressor, 2: heat source side heat exchanger, 3: liquid extension pipe, 4a: internal heat exchanger, 4b: internal heat exchanger, 5a: expansion mechanism, 5b: expansion mechanism, 6a: utilization side heat exchanger 6b: use side heat exchanger, 7: gas extension pipe, 9: heat source side internal heat exchanger, 11: discharge pressure sensor, 12: suction pressure sensor, 13a: internal heat exchanger low pressure outlet temperature sensor, 13b: internal heat AC low pressure outlet temperature sensor, 14a: user side heat exchanger inlet temperature sensor, 14b: user side heat exchanger inlet temperature sensor, 15a: air temperature sensor, 15b: air temperature sensor, 16a: internal heat exchanger high pressure inlet temperature sensor, 16b: Internal heat exchanger high pressure inlet temperature sensor, 17a: Internal heat exchanger high pressure outlet temperature sensor, 17b: Internal heat exchanger high pressure outlet temperature sensor, 18: Heat source side internal heat exchanger high pressure inlet temperature sensor, 19: Heat source side internal heat High pressure outlet temperature sensor, 20: measurement control device, 21: refrigerant state quantity calculating means, 22: target refrigerant state quantity calculating means, 23: correcting means, 24a: inside temperature setting means, 24b: inside temperature setting means, 30 : Heat source side internal heat exchange low pressure outlet temperature sensor, ΔSH: control target value (temperature change amount), α1: high pressure liquid side heat transfer coefficient, αg: low pressure gas side heat transfer coefficient, ε: temperature efficiency, λ: heat conductivity , 100: heat source unit, 200a: utilization unit, 200b: utilization unit, 300a: refrigerator compartment, 300b: refrigerator compartment, 1000: refrigeration air conditioner, 2000: refrigeration air conditioner, 3000: refrigeration air conditioner, A: heat transfer area, Gr: refrigerant circulation rate, K: heat passage rate, QH: heat exchange rate, QL: heat exchange rate, QR: required cooling capacity ratio, RT: internal temperature, SC: supercooling degree, SHL: internal heat exchanger outlet Superheat, SHL : Superheat degree, SHLb: superheat degree, SHLm: target superheat degree (control target value), SHe: utilization side heat exchanger outlet superheat degree, SJ: opening degree, SJmin: closed opening degree, SJnow: current opening degree, TD : Use temperature difference, THI: internal heat exchange high pressure side inlet temperature, TLO: internal heat exchange low pressure side outlet temperature, Te: evaporation temperature, hLI: outlet enthalpy, x: dryness.

Claims (9)

A heat source unit and at least two or more utilization units;
The heat source unit is composed of a compressor that compresses the refrigerant, and a heat source side heat exchanger into which the high-pressure refrigerant discharged from the compressor flows,
The utilization unit is connected to the outlet of the heat source side heat exchanger by a liquid extension pipe, and an expansion mechanism into which the high pressure refrigerant flowing out from the heat source side heat exchanger flows, and the low pressure refrigerant flowing out from the expansion mechanism flows in Heat exchange between the use-side heat exchanger, the high-pressure refrigerant flowing into the expansion mechanism and the low-pressure refrigerant flowing out from the use-side heat exchanger, and connected to the inlet of the compressor by a gas extension pipe It consists of a heat exchanger and
Superheat degree detection means for detecting the superheat degree of the low-pressure refrigerant at the outlet of the use side heat exchanger;
Inflow utilization fluid temperature detection means or outflow utilization fluid that detects the temperature at the inlet or the outlet of the utilization side heat exchanger of the utilization fluid that passes through the utilization side heat exchanger and exchanges heat with the low-pressure refrigerant. Temperature detection means;
Inflow utilization fluid temperature setting means or outflow utilization fluid temperature setting means for setting the temperature at the inlet of the utilization side heat exchanger or the temperature at the outlet of the utilization fluid;
The target refrigerant state quantity for setting the target superheat degree or the target dryness at the low-pressure side outlet of the internal heat exchanger according to the size of each cooling load obtained from the inflow utilization fluid temperature setting means or the outflow utilization fluid temperature setting means Computing means;
Flow rate adjustment control means for adjusting the flow rate of the expansion mechanism so as to achieve the superheat or target dryness at the low pressure side outlet of the internal heat exchanger;
A refrigeration air conditioner characterized by comprising: From the superheat degree of the refrigerant at the low pressure side outlet of the internal heat exchanger, the use side heat exchanger outlet refrigerant state quantity calculating means for calculating the superheat degree or dryness of the refrigerant at the outlet of the use side heat exchanger;
Cooling load calculating means for calculating a cooling load for heat exchange between the refrigerant and the use fluid in the use side heat exchanger,
The target refrigerant state quantity calculation means sets the degree of superheat or the target dryness of the low-pressure side outlet of the internal heat exchanger from the calculation result of the cooling load calculation means instead of the magnitude of the respective cooling loads. The refrigerating and air-conditioning apparatus according to claim 1. A temperature difference detecting means for detecting a temperature difference between the refrigerant temperature at the high-pressure side inlet of the internal heat exchanger and the refrigerant temperature at the high-pressure side outlet;
The enthalpy or dryness of the internal heat exchanger is calculated as the refrigerant state quantity at the outlet of the use side heat exchanger based on the temperature difference detected by the temperature difference detecting means. The refrigeration air conditioner described in 1.   In each of the two or more usage units, the temperature difference between the inflow temperature detected by the inflow utilization fluid temperature detection means and the inflow temperature set by the inflow utilization fluid temperature setting means, or the outflow utilization fluid temperature detection means A temperature difference between the detected outflow temperature and the outflow temperature set by the outflow utilization fluid temperature setting means is obtained, and for the utilization unit having the largest temperature difference, the target superheat or dryness of the low pressure side outlet of the internal heat exchanger The refrigeration air conditioner according to any one of claims 1 to 3, wherein is set to be the smallest.   In the utilization unit with the largest temperature difference, the target superheat degree or dryness of the low-pressure side outlet of the internal heat exchanger is such that the refrigerant at the outlet of the utilization side heat exchanger has a dryness of 1 or less. Item 5. A refrigeration air conditioner according to item 4.   In each of the two or more usage units, the temperature difference between the inflow temperature detected by the inflow utilization fluid temperature detection means and the inflow temperature set by the inflow utilization fluid temperature setting means, or the outflow utilization fluid temperature detection means The temperature difference between the detected outflow temperature and the outflow temperature set by the outflow utilization fluid temperature setting means is obtained, and the target superheat or dryness of the low-pressure side outlet of the internal heat exchanger is determined for the utilization unit having the smallest temperature difference. The refrigerating and air-conditioning apparatus according to any one of claims 1 to 3, wherein is set to a maximum.   The target superheat degree at the low-pressure side outlet of the internal heat exchanger is the temperature detected by the inflow utilization fluid temperature detection means or the temperature detected by the outflow utilization fluid temperature detection means, and the temperature of the utilization side heat exchanger. The refrigerating and air-conditioning apparatus according to claim 6, wherein the temperature difference is smaller than the temperature difference between the refrigerating and air-conditioning apparatus. A heat source unit and at least two or more utilization units;
The heat source unit is composed of a compressor that compresses the refrigerant, and a heat source side heat exchanger into which the high-pressure refrigerant discharged from the compressor flows,
The utilization unit is connected to the outlet of the heat source side heat exchanger by a liquid extension pipe, and an expansion mechanism into which the high pressure refrigerant flowing out from the heat source side heat exchanger flows, and the low pressure refrigerant flowing out from the expansion mechanism flows in Heat exchange between the use-side heat exchanger, the high-pressure refrigerant flowing into the expansion mechanism and the low-pressure refrigerant flowing out from the use-side heat exchanger, and connected to the inlet of the compressor by a gas extension pipe It consists of a heat exchanger and
A heat source side internal heat exchanger that exchanges heat between the high pressure refrigerant that has flowed out of the heat source side heat exchanger and the low pressure refrigerant that flows into the compressor;
Superheat degree detecting means for detecting the degree of superheat of the low pressure refrigerant at the low pressure side outlet of the heat source side internal heat exchanger;
Calculation means for calculating the degree of superheat or dryness of the low-pressure refrigerant at the low-pressure side inlet of the heat source-side heat exchanger from the amount of heat exchange in the heat source-side internal heat exchanger;
Inflow utilization fluid temperature detection means or outflow utilization fluid that detects the temperature at the inlet or the outlet of the utilization side heat exchanger of the utilization fluid that passes through the utilization side heat exchanger and exchanges heat with the low-pressure refrigerant. Temperature detection means;
Flow rate adjustment control means for adjusting the flow rate of the expansion mechanism,
The flow rate adjustment control means is configured such that, in each of the two or more usage units, the temperature difference between the inflow temperature detected by the inflow utilization fluid temperature detection means and the inflow temperature set by the inflow utilization fluid temperature setting means, or The temperature difference between the outflow temperature detected by the outflow use fluid temperature detection means and the outflow temperature set by the outflow use fluid temperature setting means is obtained, and the use unit having the largest temperature difference is used for the low pressure side of the heat source side heat exchanger. A refrigerating and air-conditioning apparatus, wherein the flow rate of the expansion mechanism is adjusted so that the degree of superheat or dryness of the refrigerant at the inlet approaches 1. The flow rate adjustment control means determines whether the opening area of the expansion mechanism is closed depending on the degree of superheat of the low-pressure refrigerant at the outlet of the use side heat exchanger or the degree of superheat of the low-pressure refrigerant at the low-pressure side outlet of the internal heat exchanger. The refrigerating and air-conditioning apparatus according to claim 1, wherein the refrigerating and air-conditioning apparatus according to any one of claims 1 to 8, wherein the refrigerating and air-conditioning apparatus corrects an opening area of the expansion mechanism based on the estimated state.

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