JP2005180911A - Refrigeration equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioning unit 1 capable of preventing a reduction in refrigeration capacity by using an evaporation pressure and nozzle efficiency of a refrigeration cycle 9 at optimum values.
A compressor 11, a condenser 12, an ejector 13 and a gas-liquid separator 14 are annularly connected by a refrigerant pipe 17, and a liquid refrigerant outlet portion 26 of the gas-liquid separator 14 and a suction portion 22 of the ejector 13 are bypassed. In the refrigeration cycle 9 which is connected by the pipe 27 and the evaporator 16 is installed in the middle of the bypass pipe 27, in the middle of the bypass pipe 27 connecting the liquid refrigerant outlet portion 26 of the gas-liquid separator 14 and the inlet side of the evaporator 16. A refrigerant pump 15 for forcibly supplying liquid refrigerant to the evaporator 16 was installed. Then, the flow rate of the refrigerant sucked into the compressor 11 is set to a constant value by controlling the rotation speed of the refrigerant pump 15 according to the rotation speed of the compressor 11.
[Selection] Figure 2

Description

  The present invention relates to a refrigeration apparatus having a refrigeration cycle incorporating an ejector.

  Conventionally, in Japanese Patent Laid-Open No. 5-31421, a refrigerant compressor, a refrigerant condenser, an ejector, a first refrigerant evaporator and a gas-liquid separator are connected in an annular shape by a refrigerant pipe, and the gas-liquid separator uses a gas phase. There has been proposed a refrigeration apparatus having a refrigeration cycle in which a liquid phase refrigerant separated from a refrigerant is sucked into a suction part of an ejector through a decompression device and a bypass pipe provided with a second refrigerant evaporator.

  And, the refrigeration cycle of the conventional refrigeration apparatus, as shown in FIG. 5, adjusts the flow rate of refrigerant passing through the nozzle 102 of the ejector 101 to increase the refrigeration capacity during low-speed operation of the refrigerant compressor, Alternatively, a variable throttle valve 103 for increasing or decreasing the nozzle diameter is provided in the nozzle 102 in the ejector 101 in order to optimize the refrigerating capacity with a margin during high-speed operation.

  However, in the conventional technique, the variable throttle valve 103 is installed in the nozzle 102 of the ejector 101, and the refrigerant flow rate is controlled by adjusting the inlet dryness (or subcooling degree) of the nozzle 102. The outlet diameter is not always the optimum outlet diameter with respect to the refrigerant flow rate, which causes a problem that the nozzle efficiency is lowered (see FIG. 6) and sufficient refrigeration capacity cannot be obtained.

  Therefore, as shown in FIG. 7, a nozzle 105 whose nozzle outlet diameter can be varied by the needle valve 104 has also been proposed. However, since the needle valve 104 also serves as a resistance member for the refrigerant flowing in the nozzle 105, the same as described above. In addition, the nozzle outlet diameter is not always the optimum outlet diameter with respect to the refrigerant flow rate, and the nozzle efficiency is reduced (see FIG. 8). Further, when the nozzle efficiency is lowered, the flow rate of the refrigerant supplied to the second refrigerant evaporator cannot be obtained sufficiently, and the pressure increase in the ejector 101 is lowered (see FIG. 9). Thereby, since the suction pressure of the refrigerant compressor is lowered, there is a problem that the circulation amount of the refrigerant circulating in the refrigeration cycle is lowered and the refrigeration capacity of the refrigeration cycle is lowered.

  An object of the present invention is to provide a refrigeration apparatus that can secure sufficient refrigeration capacity even when nozzle efficiency is reduced by installing a refrigerant pump on the suction side of an ejector that does not affect nozzle efficiency. is there.

  Another object of the present invention is to provide a refrigeration apparatus that can prevent the refrigeration cycle from being reduced in refrigeration cycle by using the evaporation pressure and nozzle efficiency of the refrigeration cycle at optimum values.

  It is another object of the present invention to provide a refrigeration apparatus capable of maintaining the refrigeration capacity of the refrigeration cycle at a substantially constant value regardless of increase or decrease in the rotational speed of the refrigerant compressor.

  According to the first aspect of the present invention, the refrigerant compressor, the refrigerant condenser, the ejector, and the gas-liquid separator are annularly connected by the refrigerant flow path, and the liquid-phase refrigerant side of the gas-liquid separator and the suction of the ejector are connected. In a refrigeration apparatus having a refrigeration cycle in which a refrigerant evaporator is installed in the middle of the bypass flow path, and provided in the middle of the bypass flow path. A refrigerant pump that pumps the liquid-phase refrigerant in the liquid separator, a rotation speed detection means that detects the rotation speed of the refrigerant compressor, and the detection value detected by the rotation speed detection means increases as the refrigerant increases. There is provided a refrigeration apparatus comprising air conditioning control means for slowing the rotational speed of the pump.

  According to the invention of claim 2, in the refrigeration apparatus of claim 1, the refrigerant pump is connected between a liquid phase refrigerant side of the gas-liquid separator and an inlet side of the refrigerant evaporator, The air conditioning control means has superheat degree detection means for detecting the superheat degree on the outlet side of the refrigerant evaporator, and the rotational speed of the refrigerant pump is set so that the detection value detected by the superheat degree detection means becomes a set value. There is provided a refrigeration apparatus characterized by increasing or decreasing the value.

  According to the third aspect of the present invention, the refrigerant compressor, the refrigerant condenser, the ejector, and the gas-liquid separator are connected in an annular manner through the refrigerant flow path, and the liquid-phase refrigerant side of the gas-liquid separator and the suction of the ejector are connected. In a refrigeration apparatus having a refrigeration cycle in which a refrigerant evaporator is installed in the middle of the bypass flow path, installed upstream of the refrigerant evaporator in the bypass flow path, In order to use the refrigerant pump forcibly pumping the liquid phase refrigerant in the gas-liquid separator to the refrigerant evaporator, and the nozzle efficiency of the ejector and the evaporation pressure of the refrigeration cycle at optimum values, the refrigerant compressor There is provided a refrigeration apparatus comprising air conditioning control means for controlling the rotational speed of the refrigerant pump so as to keep the sucked refrigerant flow rate at a substantially constant value.

  According to a fourth aspect of the present invention, in the refrigeration apparatus according to the third aspect of the present invention, the refrigerating apparatus further comprises a rotational speed detecting means for detecting a rotational speed of the refrigerant compressor, and the air conditioning control means is configured to detect the rotational speed. There is provided a refrigeration apparatus comprising controlling the rotational speed of the refrigerant pump according to the rotational speed of the refrigerant compressor detected by the means.

  According to a fifth aspect of the present invention, in the refrigeration apparatus according to the third aspect of the present invention, the refrigerating apparatus further comprises a superheat degree detecting means for detecting a superheat degree on the outlet side of the refrigerant evaporator, and the air conditioning control means There is provided a refrigeration apparatus characterized in that the rotational speed of the refrigerant pump is increased or decreased so that the detection value detected by the superheat degree detection means becomes a set value.

  According to the sixth aspect of the present invention, the refrigerant compressor, the refrigerant condenser, the ejector, and the gas-liquid separator are connected in an annular manner through the refrigerant flow path, and the liquid-phase refrigerant side of the gas-liquid separator and the suction of the ejector are connected. In a refrigeration apparatus having a refrigeration cycle in which a refrigerant evaporator is installed in the middle of the bypass flow path, installed upstream of the refrigerant evaporator in the bypass flow path, A refrigerant pump that forcibly pumps the liquid-phase refrigerant in the gas-liquid separator to the refrigerant evaporator, a rotation speed detection means that detects a rotation speed of the refrigerant compressor, and an increase / decrease in the rotation speed of the refrigerant compressor. Regardless of this, air conditioning control means for controlling the rotational speed of the refrigerant pump according to the rotational speed of the refrigerant compressor detected by the rotational speed detection means so as to keep the refrigeration capacity of the refrigeration cycle at a substantially constant value. Specially A freezing device is provided.

  According to the invention described in claim 7, in the refrigeration apparatus according to claim 6, further comprising superheat degree detection means for detecting the superheat degree on the outlet side of the refrigerant evaporator, the air conditioning control means is There is provided a refrigeration apparatus characterized in that the rotational speed of the refrigerant pump is increased or decreased so that the detection value detected by the superheat degree detection means becomes a set value.

  According to the embodiment of the present invention, the refrigerant flow rate adjusting means is not provided in the ejector nozzle, but in the middle of the bypass flow path connecting the liquid refrigerant side of the gas-liquid separator of the refrigeration cycle and the suction part of the ejector. By providing the refrigerant evaporator with a refrigerant pumping means for pumping the liquid phase refrigerant in the gas-liquid separator, the nozzle efficiency is not significantly affected. Further, by forcibly circulating the refrigerant in the refrigerant evaporator, the pressure increase performance is improved and the evaporating pressure and nozzle efficiency of the refrigeration cycle become optimum values, so that a decrease in the refrigeration capacity of the refrigeration cycle can be suppressed.

  According to the embodiment of the present invention, by increasing or decreasing the rotational speed of the refrigerant pump so that the superheat degree on the outlet side of the refrigerant evaporator detected by the superheat degree detection means becomes a set value, Since the change in the flow rate of the supplied refrigerant is suppressed, the heat transfer coefficient in the refrigerant evaporator does not decrease significantly.

  According to the embodiment of the present invention, the more the rotational speed of the refrigerant compressor detected by the rotational speed detecting means increases, the slower the rotational speed of the refrigerant pump, thereby changing the refrigerant supplied to the refrigerant evaporator. Can absorb minutes. Thereby, by controlling the suction pressure of the refrigerant compressor, the suction specific volume of the refrigerant compressor can be changed, and the flow rate of the refrigerant sucked into the refrigerant compressor can be kept at a substantially constant value.

[Configuration of Example]
1 to 4 show an embodiment of the present invention. FIG. 1 (a) shows a refrigeration cycle of a vehicle air conditioner, and FIG. 1 (b) shows a ventilation of the vehicle air conditioner. FIG. 2 is a diagram showing a control system of the vehicle air conditioner.

  The air conditioning apparatus for a vehicle according to the present embodiment is an air conditioner that controls each air-conditioning means of an air-conditioning unit 1 that air-conditions a passenger compartment of a vehicle on which a power engine for driving a vehicle is mounted, by an air-conditioning control device 10 described later. is there. The air conditioning unit 1 includes an air conditioning case 2 that forms an air passage that guides conditioned air into the vehicle compartment, and a blower 3 that is coupled to the upstream end of the air conditioning case 2.

  In the air conditioning case 2, there are provided an evaporator that constitutes one configuration of the refrigeration cycle 9 described later, and a heater core 4 that reheats the cold air that has passed through the evaporator. Two air mix doors 5 for adjusting the amount of air passing through the heater core 4 and the amount of air bypassing the heater core 4 are attached to the upstream side and the downstream side of the heater core 4.

  The blower 3 includes a centrifugal fan 6 that generates an air flow toward the passenger compartment in the air passage of the air conditioning case 2, a blower motor 7 that rotationally drives the centrifugal fan 6, and a scroll that rotatably accommodates the centrifugal fan 6. It is comprised from the casing 8 grade | etc.,. The scroll casing 8 is integrally coupled to the upstream end of the air conditioning case 2, for example.

  Next, the configuration of the refrigeration cycle 9 of the present embodiment will be described with reference to FIG. The refrigeration cycle 9 is a so-called ejector cycle, and includes a compressor (refrigerant compressor) 11 that compresses a gas-phase refrigerant (hereinafter referred to as a gas refrigerant) by a driving force of a power engine mounted on a vehicle, and a compressed gas refrigerant. A condenser (refrigerant condenser) 12 for condensing and liquefying, an ejector 13 for decompressing and expanding the condensed liquid-phase refrigerant (hereinafter referred to as liquid refrigerant), and gas for separating the gas-liquid two-phase refrigerant that has been decompressed and expanded A liquid separator 14, a refrigerant pump 15 that sucks liquid refrigerant, and an evaporator (refrigerant evaporator) 16 that evaporates and evaporates the refrigerant that flows in.

  The compressor 11, together with the condenser 12, the ejector 13, and the gas-liquid separator 14, is connected in a ring shape by a refrigerant pipe (refrigerant flow path) 17. The compressor 11 is connected to an electromagnetic clutch (see FIG. 2) 18 that intermittently transmits rotational power from the power engine to the compressor 11. When the electromagnetic clutch 18 is energized, the rotational power of the power engine is transmitted to the compressor 11 and the evaporator 16 performs an air cooling action. In the vicinity of the condenser 12, a cooling fan 19 for sending cooling air for cooling the refrigerant flowing in the condenser 12 is installed.

  The ejector 13 atomizes the liquid refrigerant flowing in from the condenser 12 by spraying from the nozzle 21, and sucks the gas refrigerant from the suction unit 22 to mix the liquid refrigerant and the gas refrigerant in the diffuser 23. The pressure reducing means sends the gas-liquid two-phase refrigerant to the gas-liquid separator 14 after increasing the pressure. The gas-liquid separator 14 includes a refrigerant inlet 24, a gas refrigerant outlet 25, and a liquid refrigerant outlet (liquid phase refrigerant side) 26.

  The refrigerant pump 15 is a component corresponding to the refrigerant pressure feeding means of the present invention, and is an evaporator in a bypass pipe (bypass passage) 27 that connects the liquid refrigerant outlet portion 26 of the gas-liquid separator 14 and the suction portion 22 of the ejector 13. It is installed on the upstream side (the entrance side) from 16. The refrigerant pump 15 is a component that adjusts the flow rate of refrigerant flowing into the evaporator 16 by changing the ON / OFF interval. For example, the longer the ON time of the refrigerant pump 15 is, the longer the refrigerant flow rate flowing into the evaporator 16 is. The evaporator 16 is an air cooling unit that is installed in the middle of the bypass pipe 27 and cools the air by exchanging heat between the refrigerant flowing inside and the air passing through the air conditioning case 2.

  The air-conditioning control device 10 is a component corresponding to the air-conditioning control means of the present invention, and is supplied with power from the battery 30 when the ignition switch is turned on, and from each switch on the operation panel provided on the front surface of the vehicle interior. A switch signal is input and various control processes are performed. In the air conditioning control device 10, a known microcomputer including a CPU, ROM, RAM, and the like is provided. When the relay coil 34 is energized, the relay switch 35 is closed and the refrigerant pump 15 is energized, and the relay coil 36. Is closed, the relay switch 37 is closed and the electromagnetic clutch 18 is energized.

  In addition, the air-conditioning control device 10 includes an outlet temperature sensor 31 that detects the temperature on the outlet side of the evaporator 16, an outlet pressure sensor 32 that detects pressure on the outlet side of the evaporator 16 (low pressure pressure and evaporation pressure of the refrigeration cycle 9), and Sensor signals are input from sensors such as a rotation speed sensor 33 that detects the rotation speed of the compressor 11. The outlet temperature sensor 31 and the outlet pressure sensor 32 are parts corresponding to the superheat degree detecting means of the present invention, and the rotational speed sensor 33 is a part corresponding to the rotational speed detecting means of the present invention.

  The air conditioning controller 10 calculates the degree of superheat on the outlet side of the evaporator 16 from the temperature on the outlet side of the evaporator 16 detected by the outlet temperature sensor 31 and the pressure on the outlet side of the evaporator 16, and this degree of superheat is a set value. The flow rate of the refrigerant flowing into the evaporator 16 is adjusted by controlling the rotational speed of the refrigerant pump 15 so as to be (for example, 1 ° C. to 2 ° C.). Further, the air conditioning control device 10 inputs the rotational speed of the compressor 11 detected by the rotational speed sensor 33, and controls the rotational speed of the refrigerant pump 15 in order to absorb the change in the refrigerant flow rate due to the rotational speed of the compressor 11. Thus, the flow rate of the refrigerant flowing into the compressor 11 and the evaporator 16 is adjusted.

(Effects of Example)
Next, the operation of the air conditioning unit 1 of this embodiment will be briefly described with reference to FIGS. Here, FIG. 3 shows the state of the refrigerant in the refrigerant circuit of the refrigeration cycle 9 in FIG. 1A on the Mollier diagram, and a to b on the refrigerant circuit of the refrigeration cycle 9 in FIG. The state of the refrigerant of f corresponds to a to f on the Mollier diagram of FIG.

  3, PH is the high pressure (condensation pressure) of the refrigeration cycle 9, PD is the suction pressure of the compressor 11, PL is the low pressure (evaporation pressure) of the refrigeration cycle 9, and PS is the outlet pressure of the nozzle 21. It is. In FIG. 3, Ge is a refrigerant flow rate that flows into the evaporator 16 due to the suction force of the refrigerant pump 15, and Gn is a refrigerant flow rate due to the suction force of the compressor 11. ΔP is the pressure increase of the ejector 13, Δie is the adiabatic heat drop at the nozzle 21, and Δir is the amount of compression work recovered by the compressor 11 by the ejector 13.

  The gas refrigerant (state point b) that has been compressed by the compressor 11 to become a high-temperature and high-pressure is condensed and liquefied by the condenser 12 to become a high-temperature and high-pressure liquid refrigerant (state point c) and flows into the ejector 13. The liquid refrigerant that has flowed into the ejector 13 is reduced in pressure when passing through the nozzle 21 and reaches the state point d2, and further increased in pressure when passing through the diffuser 23 to reach the state point d.

  At this time, the gas refrigerant at the state point d1 is sucked into the suction portion 22 of the ejector 13 from the bypass pipe 27 by using the pressure drop around the refrigerant that is ejected from the nozzle 21 at a high speed when the liquid refrigerant passes through the nozzle 21. The For this reason, the liquid refrigerant flowing from the condenser 12 and the gas refrigerant sucked from the bypass pipe 27 are mixed in the diffuser 23. As a result, the gas-liquid two-phase refrigerant flowing out of the ejector 13 becomes the state point d determined by the state points d1 and d2, the refrigerant flow rate from the condenser 12 and the refrigerant flow rate from the evaporator 16.

  Thereafter, the gas-liquid two-phase refrigerant flows into the gas-liquid separator 14 from the refrigerant inlet 24 through the refrigerant pipe 17 and is separated into gas refrigerant and liquid refrigerant. Of these, the gas refrigerant (state point a) flows out of the gas refrigerant outlet 25 of the gas-liquid separator 14 by the suction force of the compressor 11 and is sucked into the compressor 11 through the refrigerant pipe 17.

  The liquid refrigerant (state point e) in one gas-liquid separator 14 is sucked into the refrigerant pump 15 and flows out from the liquid refrigerant outlet portion 26 of the gas-liquid separator 14 and flows into the bypass pipe 27. Then, the liquid refrigerant that has flowed into the bypass pipe 27 is increased in pressure by the suction effect of the refrigerant pump 15 (state point f) and then flows into the evaporator 16. The liquid refrigerant that has flowed into the evaporator 16 evaporates and passes through the evaporator 16 (state point d1), and is then sucked into the suction portion 22 of the ejector 13.

  Here, in order to use the nozzle efficiency of the ejector 13 at the optimum value, it is necessary to keep the flow rate of the refrigerant flowing into the evaporator 16 at a constant value. However, since the compressor 11 is driven to rotate by the power engine, the compressor 11 As shown in the graph of FIG. 4, the rotational speed of fluctuates from an idle rotational speed (for example, 800 rpm) to a rotational speed (for example, 200 rpm) that matches the normal traveling speed.

  Therefore, in this embodiment, the rotation of the compressor 11 is absorbed in order to absorb the fluctuation amount of the refrigerant flow rate flowing into the evaporator 16 (refer to the conventional example in FIG. 4C) caused by the fluctuation of the rotation speed of the compressor 11. By controlling the rotational speed of the refrigerant pump 15 in accordance with the speed, the suction pressure of the compressor 11 is lowered (see the embodiment in FIG. 4B). As a result, the suction specific volume of the compressor 11 is increased, so that the flow rate of the refrigerant sucked into the compressor 11 is maintained at a constant value (see the example in FIG. 4C).

[Effects of Examples]
All of the air conditioning units 1 that use the compressor 11 that is rotationally driven by a power engine for running a vehicle have a problem that the cooling capacity is low when idling (idle speed). As a countermeasure, the ejector 13 can recover the energy loss at the expansion valve, reduce the work of the compressor 11, and improve the cooling capacity by increasing the refrigerant flow rate.

  However, since the refrigeration cycle 9 provided with the ejector 13 relies heavily on the nozzle efficiency of the ejector 13, as described above, if the nozzle efficiency and the evaporation pressure are not used at the optimum values, the cooling capacity is reduced. There is a worry to do. In the present embodiment, this problem is solved in order to circulate the liquid refrigerant to the evaporator 16 forcibly by the refrigerant pump 15 regardless of the rotational speed of the power engine (compressor 11). And the evaporation pressure is used at an optimum value (see FIG. 4A). Thereby, as shown in FIG.4 (d), the fall of the cooling capability can be suppressed. In particular, the present embodiment can improve the cooling capacity in the low speed region of the compressor 11 as compared with the conventional example.

  The operation of the refrigerant pump 15 is based on the normal superheat amount (set value: 10 ° C., for example) with respect to the superheat degree (superheat amount) on the outlet side of the evaporator 16 calculated from the outlet temperature sensor 31 and the outlet pressure sensor 32. ) And the ON / OFF control at + -1 ° C. Note that the amount of superheat is not limited to 10 ° C., and the smaller the heat amount, the better the heat transfer rate to the air.

[Modification]
In the present embodiment, the present invention is applied to a vehicle air conditioner (air conditioner), but the present invention may be applied to a vehicle cooling device, a vehicle refrigeration device, or a vehicle refrigeration device. Further, the present invention may be applied to a stationary refrigeration apparatus.

  In this embodiment, the compressor 11 is rotationally driven by a power engine for vehicle travel, but the compressor 11 may be rotationally driven by an auxiliary engine (sub engine) different from the power engine for vehicle travel. Further, the compressor 11 may be rotationally driven by other driving means such as an electric motor.

  In the present embodiment, the ejector 13 and the gas-liquid separator 14 are connected by the refrigerant pipe 17, but a first refrigerant evaporator may be installed in the middle of the refrigerant pipe 17. In this case, the evaporator 16 becomes a second refrigerant evaporator. Further, if necessary, a decompression device (fixed throttle) may be installed between the gas-liquid separator 14 and the refrigerant pump 15.

  In the present embodiment, the refrigerant pump 15 is installed in the bypass pipe 27 on the upstream side of the evaporator 16, but refrigerant pumping means such as an electric compressor may be installed in the bypass pipe 27 on the downstream side of the evaporator 16.

(A) is the circuit diagram which showed the refrigerant circuit of the refrigerating cycle, (b) is the schematic which showed the ventilation system of the air conditioning apparatus for vehicles (Example). It is the electric circuit diagram which showed the control system of the air conditioning apparatus for vehicles (Example). It is a Mollier diagram of a refrigeration cycle (Example). It is the graph which showed the relationship of the evaporating pressure with respect to the rotation speed of a compressor, the suction pressure of a compressor, a refrigerant | coolant suction flow rate, and cooling capacity (Example). It is sectional drawing which showed the conventional ejector (conventional example). It is the graph which showed the relationship between nozzle entrance dryness and nozzle efficiency (conventional example). It is sectional drawing which showed the conventional ejector (conventional example). It is the graph which showed the relationship between a nozzle exit diameter and nozzle efficiency (conventional example). It is the graph which showed the relationship between the refrigerant | coolant flow volume of an evaporator, and the pressure | voltage rise performance in an ejector (conventional example).

Explanation of symbols

1 Air-conditioning unit 9 Refrigeration cycle 10 Air-conditioning control device (air-conditioning control means)
11 Compressor (refrigerant compressor)
12 Condenser (refrigerant condenser)
13 Ejector 14 Gas-liquid separator 15 Refrigerant pump (refrigerant pressure feeding means)
16 Evaporator (refrigerant evaporator)
17 Refrigerant piping (refrigerant flow path)
21 Nozzle 22 Suction part 26 Liquid refrigerant outlet (liquid phase refrigerant side)
27 Bypass piping (bypass flow path)
31 Outlet temperature sensor (superheat detection means)
32 Outlet pressure sensor (superheat detection means)
33 Rotational speed sensor (rotational speed detection means)

Claims (7)

A refrigerant compressor, a refrigerant condenser, an ejector and a gas-liquid separator are connected in an annular shape with a refrigerant flow path, and a liquid phase refrigerant side of the gas-liquid separator and a suction part of the ejector are connected with a bypass flow path, In a refrigeration apparatus equipped with a refrigeration cycle in which a refrigerant evaporator is installed in the middle of the bypass flow path,
A refrigerant pump that is provided in the middle of the bypass flow path and pumps the liquid-phase refrigerant in the gas-liquid separator to the refrigerant evaporator;
A rotational speed detecting means for detecting the rotational speed of the refrigerant compressor;
A refrigeration apparatus comprising: an air-conditioning control unit that slows down the rotation speed of the refrigerant pump as the detection value detected by the rotation speed detection unit increases. The refrigeration apparatus according to claim 1,
The refrigerant pump is connected between a liquid phase refrigerant side of the gas-liquid separator and an inlet side of the refrigerant evaporator,
The air conditioning control means has superheat degree detection means for detecting the superheat degree on the outlet side of the refrigerant evaporator, and the rotational speed of the refrigerant pump is set so that the detection value detected by the superheat degree detection means becomes a set value. A refrigeration apparatus characterized by increasing or decreasing the value. A refrigerant compressor, a refrigerant condenser, an ejector and a gas-liquid separator are connected in an annular shape with a refrigerant flow path, and a liquid phase refrigerant side of the gas-liquid separator and a suction part of the ejector are connected with a bypass flow path, In a refrigeration apparatus equipped with a refrigeration cycle in which a refrigerant evaporator is installed in the middle of the bypass flow path,
A refrigerant pump that is installed upstream of the refrigerant evaporator in the bypass flow path and forcibly pumps the liquid-phase refrigerant in the gas-liquid separator to the refrigerant evaporator;
In order to use the nozzle efficiency of the ejector and the evaporating pressure of the refrigeration cycle at optimum values, air conditioning that controls the rotational speed of the refrigerant pump so as to keep the refrigerant flow rate sucked into the refrigerant compressor at a substantially constant value. A refrigeration apparatus comprising a control means. The refrigeration apparatus according to claim 3,
Furthermore, it has a rotation speed detection means for detecting the rotation speed of the refrigerant compressor,
The refrigeration apparatus characterized in that the air conditioning control means controls the rotational speed of the refrigerant pump according to the rotational speed of the refrigerant compressor detected by the rotational speed detection means. The refrigeration apparatus according to claim 3,
Furthermore, it has superheat degree detection means for detecting the superheat degree on the outlet side of the refrigerant evaporator,
The refrigeration apparatus, wherein the air conditioning control means increases or decreases the rotational speed of the refrigerant pump so that a detection value detected by the superheat degree detection means becomes a set value. A refrigerant compressor, a refrigerant condenser, an ejector and a gas-liquid separator are connected in an annular shape with a refrigerant flow path, and a liquid phase refrigerant side of the gas-liquid separator and a suction part of the ejector are connected with a bypass flow path, In a refrigeration apparatus equipped with a refrigeration cycle in which a refrigerant evaporator is installed in the middle of the bypass flow path,
A refrigerant pump that is installed upstream of the refrigerant evaporator in the bypass flow path and forcibly pumps the liquid-phase refrigerant in the gas-liquid separator to the refrigerant evaporator;
A rotational speed detecting means for detecting the rotational speed of the refrigerant compressor;
The rotational speed of the refrigerant pump according to the rotational speed of the refrigerant compressor detected by the rotational speed detecting means so that the refrigeration capacity of the refrigeration cycle is maintained at a substantially constant value regardless of the increase or decrease of the rotational speed of the refrigerant compressor. A refrigeration apparatus comprising an air-conditioning control means for controlling the air conditioner. The refrigeration apparatus according to claim 6,
Furthermore, it has superheat degree detection means for detecting the superheat degree on the outlet side of the refrigerant evaporator,
The refrigeration apparatus, wherein the air conditioning control means increases or decreases the rotational speed of the refrigerant pump so that a detection value detected by the superheat degree detection means becomes a set value.

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