TWM604873U - Air Conditioning System - Google Patents

Abstract

An air conditioning system, an air conditioning system suitable for using a refrigerant as a working fluid, and comprising a pressurizing unit, a condensing unit connected to the pressurizing unit, a pressure reducing unit connected to the condensing unit, and a pressure reducing unit connected to the pressure reducing unit An evaporation unit forming a fluid circulation with the pressurizing unit, and a fluid control unit communicating between the pressurizing unit and the condensing unit. The fluid control unit includes an inlet pipe, a sensing element connected to the inlet pipe, at least one pressure reducing element connected to the inlet pipe, and a solenoid valve connected to the at least one pressure reducing element and connected to the sensing element. The sensing element can set a preset value to control the solenoid valve to open to allow the refrigerant to circulate, so as to mix the refrigerant discharged from the condensing unit and lower the temperature so that the system circulates stably.

Description

Air Conditioning System

This new model relates to an air-conditioning system, in particular to an air-conditioning system that responds to a use environment with a large temperature difference.

Referring to Fig. 1, a conventional refrigerant air-conditioning system is suitable for installation on a mobile crane, and uses a refrigerant 10 as a working fluid, and includes a compressor 11 and a condenser 12 connected to the outlet end of the compressor 11 , An accumulator 13 communicating with the outlet end of the condenser 12, a pump 14 communicating with the outlet end of the accumulator 13, an expansion valve 15 communicating with the outlet end of the pump 14, an expansion valve 15 communicating with the An evaporator 16 for fluid circulation is formed between the compressors 11, and an injection member 17 connected from the outlet end of the pump 14 to the outlet end of the compressor 11. The injection member 17 includes a flow control valve 171 connected to the pump 14, and an outlet port connecting the flow control valve 171 and the compressor 11, and only allows the refrigerant 10 to flow through the flow control valve 171 in one direction To the check valve 172 at the outlet end of the compressor 11. Wherein, the inlet end and the outlet end of the aforementioned element are used to represent the flow direction of the refrigerant 10 passing through the element.

For the convenience of description, the refrigerant 10 is in two different phases of liquid state and gas state, which are respectively labeled as the refrigerant 10(l) and the refrigerant 10(g) in FIG. 1. When the refrigerant air-conditioning system is started, the refrigerant 10(l) stored in the accumulator 13 acts through the pump 14, and will be transported to a first flow path of the expansion valve 15 and the evaporator 16, respectively. A second flow path to the injection member 17. Among them, most of the refrigerant 10(l) will be transported to the first flow path, and the pressure will be reduced sequentially and the ambient heat of the mobile crane will be absorbed to achieve the air-conditioning cooling effect, and finally the refrigerant will evaporate due to the increase in temperature. 10 (g) and discharged from the outlet end of the evaporator 16 to the compressor 11 for pressurization treatment. In addition, a small part of the refrigerant 10(1) is transported to the second flow path, and is directly guided to the outlet end of the compressor 11 through the injection member 17, and is combined with the refrigerant 10 that is discharged from the compressor 11 and has a higher temperature. (g) Mix and cool the refrigerant 10(g) below its critical temperature, and be transported to the condenser 12 for heat exchange with the external environment to be completely condensed, and finally cool down and condense into the refrigerant 10 (1) and transported to the reservoir 13 for storage for the pump 14 to use. Accordingly, the purpose of the injection member 17 is to lower the temperature of the refrigerant 10(g) discharged from the compressor 11, so that the temperature of the refrigerant 10 after mixing is lower than the critical temperature and can be normally condensed so that it can be in the system Stable circulation.

However, the pressure of the refrigerant 10(g) discharged from the compressor 11 is usually higher than the pressure of the refrigerant 10(l) discharged from the injection member 17, and the pressure difference causes the refrigerant 10(l) to be relatively high. It is difficult to discharge stably, and even unable to pass the check valve 172 to mix with the refrigerant 10(g) to cool down. Therefore, the pump 14 needs to be pressurized, but it also increases the cost of extra electricity. In addition, since the mobile crane often has to move back and forth between positions with a large temperature difference, the temperature and pressure of the refrigerant 10(g) discharged from the compressor 11 are also constantly changing, so it is necessary to constantly adjust the help Only the Pu 14 and the flow control valve 171 can inject an appropriate amount of the refrigerant 10(l) into the outlet end of the compressor 11 to mix the refrigerant 10(g), and make the mixed refrigerant 10 reach the desired level. The temperature is set so that it can be completely condensed in the condenser 12, but it also causes inconvenience in control, and it is impossible to control the flow in time.

Therefore, the purpose of the present invention is to provide an air conditioning system that can achieve a stable condensation cycle even in a use environment with large temperature differences.

Therefore, the new air conditioning system is suitable for using a refrigerant as a working fluid, and includes a pressurizing unit, a condensing unit connected to the relatively downstream of the pressurizing unit, a depressurizing unit connected to the relatively downstream of the condensing unit, and a pressure reducing unit connected to the condensing unit. An evaporation unit between the pressure unit and the pressure unit, and a fluid control unit arranged between the relatively downstream of the condensing unit and the relatively upstream of the pressure unit.

The pressurizing unit is suitable for increasing the pressure of the refrigerant. The condensing unit is suitable for receiving the refrigerant and reducing the temperature of the refrigerant. The pressure reducing unit is adapted to receive the refrigerant and reduce the pressure of the refrigerant and discharge it. The evaporation unit is adapted to receive the refrigerant, raise the temperature of the refrigerant, and introduce it into the pressurizing unit to form a fluid circulation. The fluid control unit is suitable for conveying the refrigerant discharged from the condensing unit to the pressurizing unit, and includes an inlet pipe connected to the pressure reducing unit, and an inlet pipe connected to the inlet pipe suitable for sensing the refrigerant located in the inlet pipe A sensor for a property parameter of the refrigerant, at least one pressure-reducing component connected to the inlet pipe and suitable for decompressing and throttling the refrigerant, and a pressure-reducing component connected to the at least one pressure-reducing component and connected to the inlet end of the pressurizing unit, And connect the solenoid valve of the sensing element. The sensing element can be set with a preset value. When the property parameter is greater than the preset value, the solenoid valve is opened to allow the refrigerant to circulate.

The effect of the present invention is that during the operation of the system, since the pressure of the liquid refrigerant in the fluid control unit is greater than the pressure at the inlet of the pressurizing unit, the liquid refrigerant does not require the action of a pump. It can transmit, coupled with the pressure-reducing parts whose inner diameter of the tube is small and the pipeline is curled to extend the substantial path, can have the function of pressure-reduction and throttling, so that the fluid regulating unit can stably and safely dissipate the lower temperature refrigerant Transported to the inlet end of the pressurizing unit, mixed with the higher temperature refrigerant discharged from the evaporation unit, lowering the temperature of the mixed refrigerant and transporting to the condensing unit through the pressurizing unit, because the temperature of the refrigerant is low It can be completely condensed at the critical temperature, thereby preventing the refrigerant from affecting the operation of subsequent units due to insufficient condensation margin.

Referring to Figure 2, an embodiment of the new air conditioning system is suitable for using a refrigerant 2 as a working fluid, and includes a pressurizing unit 3, a condensing unit 4 connected to the relatively downstream of the pressurizing unit 3, and a condensing unit connected to the condensing unit 4 A pressure-reducing unit 5 relatively downstream, an evaporation unit 6 connected between the pressure-reducing unit 5 and the pressurizing unit 3, and a fluid control unit connected to the relatively downstream of the condensing unit 4 and the relatively upstream of the pressurizing unit 3 Unit 7. The present embodiment is described in a situation where it is installed in a crane (not shown in FIG. 2), where the crane will move back and forth between a high temperature environment with a large temperature difference and a normal temperature environment.

In order to clearly illustrate the flow path of the refrigerant 2 in this embodiment, referring to the arrow shown in the drawing, it is used to show the moving route of the refrigerant 2.

The pressurizing unit 3 is preferably a gas compressor, which is suitable for sucking the refrigerant 2 in a gaseous state at the inlet end, and boosting the pressure through different mechanisms such as compression space or impeller rotation, thereby generating a higher pressure After the refrigerant 2, it is discharged from the outlet end.

The condensing unit 4 includes a heat exchanger 41 connected to the outlet end of the pressurizing unit 3 and suitable for reducing the temperature of the refrigerant 2 discharged from the pressurizing unit 3, and an outlet end connected to the heat exchanger 41, and It is suitable for storing the accumulator 42 of the liquid refrigerant 2 discharged from the heat exchanger 41. In addition, it should be noted that because the accumulator 42 is only a transition device for stable downstream conveying, it prevents the downstream unit from idling. Therefore, in this embodiment, the configuration or storage capacity of the accumulator 42 can be adjusted according to the usage conditions. Even if the accumulator 42 is missing, the embodiment can still operate in a cycle.

The pressure reducing unit 5 is an expansion valve in this embodiment, which is suitable for reducing the pressure of the liquid refrigerant 2 discharged from the condensing unit 4 so that the refrigerant 2 is discharged in a wet vapor state for downstream cooling use.

The evaporation unit 6 is adapted to receive the refrigerant 2 discharged from the depressurization unit 5, and evaporate by absorbing the ambient heat of the overhead crane through the refrigerant 2, so as to relatively reduce the ambient temperature of the overhead crane, thereby The air conditioning effect of the overhead crane is achieved, and the refrigerant 2 is discharged to the inlet end of the pressurizing unit 3 to complete the fluid circulation.

The fluid control unit 7 is suitable for conveying the refrigerant 2 discharged from the condensing unit 4 to the inlet end of the pressurizing unit 3, and includes an inlet pipe 71 formed by a branch pipe at the outlet end of the condensing unit 4, and a connecting pipe The sensing element 72 of the inlet pipe 71, a one-way valve 73 connected to the inlet pipe 71, several pressure-reducing elements 74 connected to the inlet pipe 71 and arranged to be separated from each other, and a one-way valve 73 connected to the pressure-reducing components. The outlet end of the element 74 is connected to the inlet end of the pressurizing unit 3 and is electrically connected to the solenoid valve 75 of the sensing element 72. Wherein, the sensing element 72 is used to sense a property parameter of the refrigerant 2 located in the inlet pipe 71. In this embodiment, the sensing element 72 is a pressure sensor, and the measured The property parameter is the pressure value. The one-way valve 73 is preferably a back pressure valve, but it is not limited to this, and can be adjusted as a check valve or other flow regulating valve with back pressure function according to requirements. The decompression members 74 are preferably spiral capillaries, but not limited to this, they can also be linear capillaries, as long as the pressure of the refrigerant 2 in the tube can be reduced. The pressure reducing elements 74 are used to increase the flow path of a single pipeline, and by adjusting the number of the pressure reducing elements 74, the environment with different flow requirements can be met.

In particular, the solenoid valve 75 can be driven by the sensing element 72 to switch its valve. When the property parameter measured by the sensing element 72 is greater than a preset value set in advance, the solenoid valve 75 opens the valve port to allow the refrigerant 2 to circulate. Conversely, when the property parameter measured by the sensing element 72 is less than the preset value, the solenoid valve 75 closes the valve port.

In addition, the material of the pipes between the condensing unit 4, the evaporation unit 6, the fluid control unit 7 and each element of this embodiment is preferably unified to copper pipes, which not only has better heat transfer capacity and higher materials The strength can also make the present embodiment have consistent potential energy, prevent activation due to potential difference and be prone to corrosion, and increase the service life. In terms of material selection in this embodiment, other metal materials with better thermal conductivity can also be used, as long as the pipeline material types are unified to avoid potential differences.

The following will describe the flow of this embodiment when used. For the convenience of description, the refrigerant 2 is in two different phases of liquid state and gas state, which are marked as the refrigerant 2 (1) in FIGS. 3 and 4, respectively. ) And the refrigerant 2(g).

3 and 4, when this embodiment is started, the refrigerant 2(l) stored in the accumulator 42 is pushed through the pressurizing unit 3 arranged relatively upstream of the condensing unit 4, and then the refrigerant The branched flow discharged from the outlet end of the device 42 flows to the inlet end of the depressurization unit 5 and is used for a first flow path P1 of the cooling room, and flows to the inlet pipe 71 of the fluid control unit 7 and is used to reconcile the cooling room. A second flow path P2 of the temperature of the refrigerant 2(g) finally converges at the inlet end of the pressurizing unit 3 to complete the fluid circulation. In the normal operation of the system, the flow rate of the refrigerant 2 in the first flow path P1 is greater than the flow rate of the refrigerant 2 in the second flow path P2, so as to maintain the cooling capacity of the air conditioner for the overhead crane in this embodiment.

When the crane is in the high-temperature environment such as the processing area or refining area of the factory, the temperature of the refrigerant 2(g) at the inlet of the pressurizing unit 3 will be too high, which will affect the ability of subsequent condensation, making the fluid required The control unit 7 injects the refrigerant 2(l) at a lower temperature to mix. Therefore, when the refrigerant 2(l) in this embodiment is transported along the first flow path P1 as shown in FIG. 3, the refrigerant 2(l) It flows into the pressure reduction unit 5 first, and then reduces the pressure through the expansion valve, and then discharges to the evaporation unit 6. Then the evaporation unit 6 absorbs the heat from the environment of the crane and converts it into the refrigerant 2(g) It is discharged to the inlet end of the pressurizing unit 3 and converted into the refrigerant 2(g) to achieve an air-conditioning cooling effect on the crane.

When the refrigerant 2(l) is transported along the second flow path P2 as shown in FIG. 4, the refrigerant 2(l) first flows into the inlet pipe 71, and flows through the sensing element 72 for pressure measurement. , It flows to the inlet ends of the pressure reducing parts 74 and the one-way valve 73. Wherein, because the pressure value of the refrigerant 2(l) is positively correlated with the ambient temperature of the crown block, when in the high temperature environment, the property parameter measured by the sensing element 72 will be greater than the preset value. The solenoid valve 75 is driven to open, so that the refrigerant 2(1) flows to the solenoid valve 75 from the pressure reducing components 74. When the refrigerant 2(l) flows through the decompression parts 74, it passes through the smaller pipe diameters of the decompression parts 74 and cooperates with the auxiliary pressure drop design of extending the length of the pipeline in a spiral shape to achieve a reduction The effect of pressure and throttling not only reduces the pressure of the refrigerant 2(l) and reduces the damage to the solenoid valve 75, but also provides a stable flow through the solenoid valve 75 to the inlet end of the pressurizing unit 3, and The evaporation unit 6 discharges the higher-temperature refrigerant 2 (g) for mixing and cooling. The pressurizing unit 3 pressurizes the mixed refrigerant 2(g) and discharges it to the condensing unit 4 for cooling. Since the temperature of the refrigerant 2(g) is lower than the critical temperature, the refrigerant 2(g) can be The refrigerant 2(1) is completely condensed in the heat exchanger 41 to prevent the heat exchanger 41 from being blocked and affecting the subsequent cooling capacity. The refrigerant 2(1) finally flows back to the accumulator 42 for storage to complete the overall fluid circulation.

When the crane moves from the high temperature environment to the normal temperature environment, the process of the refrigerant 2 along the first flow path P1 is the same as described above, and the difference from the second flow path P2 is: because it is located in the inlet pipe 71 The pressure value decreases as the temperature decreases, so that the property parameter measured by the sensing element 72 is lower than the preset value, and then the solenoid valve 75 is driven to close the valve and stop the refrigerant 2(l) from being delivered to the pressurization Entrance end of unit 3. Wherein, when the solenoid valve 75 is about to be closed, the fluid control unit 7 will quickly close the valve and produce water hammer phenomenon of the fluid, and the pipeline will vibrate due to the increase in pressure, especially the decompression parts 74 vibrate more. As strong. However, when the pressure at the inlet of the one-way valve 73 is greater than a preset back pressure value in the one-way valve 73, the diaphragm in the one-way valve 73 will be pushed open to supply the refrigerant 2(l) Circulation can not only relieve the vibration behavior of the pressure reducing parts 74, but also balance the pressure flowing at the inlet and outlet of the solenoid valve 75, so that the solenoid valve 75 can close the valve immediately and completely, so that the system The flow path of the refrigerant 2 is only the first flow path P1 shown in FIG. 3.

In addition, since the property parameter of the inlet pipe 71 measured by the sensor 72 can be used to indicate what environment the crown block is in, when the property parameter exceeds the preset value, it means that this embodiment It is necessary to turn on the fluid control unit 7 and provide the refrigerant 2(1) to reduce the temperature of the inlet end of the pressurizing unit 3. The property parameters such as fluid pressure, temperature, density, etc. will all change with the change of ambient temperature. For example, the fluid temperature mentioned above is located in the copper tube and has good heat transfer with the external environment, making the fluid temperature easier to increase with the external temperature When the fluid temperature increases, the fluid density will reduce the cohesion due to the increase of molecular vibration, so that the density gradually decreases with the increase in temperature. Finally, the fluid pressure and density are mutually influenced by the Bernoulli relationship and have a numerical value. The change. Therefore, the measurement type of the sensing element 72 is not limited to the pressure, as long as the property parameter can have a significant difference with the environmental temperature change, and the environmental temperature of the crane is calculated, the sensing element 72 It is sufficient to drive the solenoid valve 75 to open and close according to whether the property parameter exceeds the preset value.

In summary, the air conditioning system of the present invention controls the solenoid valve 75 according to the data measurement of the sensor 72, thereby automatically opening or closing the valve according to different ambient temperatures. When the crane is in a high-temperature environment, the fluid regulating unit 7 can provide a steady flow and lower pressure of the refrigerant 2(l) to the inlet end of the pressurizing unit 3 by the decompression elements 74 to control the condensing The temperature of the refrigerant 2(g) of the unit 4 is lower than its critical temperature, so that the refrigerant 2(g) can be completely cooled into the refrigerant 2(l) in the condensing unit 4, ensuring the air conditioning cooling capacity of the subsequent units, Therefore, it can indeed achieve the purpose of cost and new style.

However, the above-mentioned are only examples of the present model, and should not be used to limit the scope of implementation of the present model, all simple equivalent changes and modifications made in accordance with the patent scope of the present model application and the contents of the patent specification still belong to This new patent covers the scope.

2: refrigerant 2(l): refrigerant 2(g): refrigerant 3: Pressure unit 4: Condensing unit 41: heat exchanger 42: reservoir 5: Step-down unit 6: Evaporation unit 7: Fluid control unit 71: inlet pipe 72: sensor 73: Check valve 74: Decompression parts 75: Solenoid valve P1: First flow route P2: Second flow route

Other features and effects of the present invention will be clearly presented in the embodiments with reference to the drawings, in which: Figure 1 is a schematic flow diagram illustrating a conventional refrigerant air conditioning system; Figure 2 is a schematic flow chart illustrating an embodiment of the new air conditioning system; Figure 3 is a schematic flow chart illustrating a first flow route of this embodiment; and Figure 4 is a schematic flow diagram illustrating a second flow route of this embodiment.

2: refrigerant

3: Pressure unit

4: Condensing unit

41: heat exchanger

42: reservoir

5: Step-down unit

6: Evaporation unit

7: Fluid control unit

71: inlet pipe

72: sensor

73: Check valve

74: Decompression parts

75: Solenoid valve

P1: First flow route

P2: Second flow route

Claims (10)

An air conditioning system suitable for using a refrigerant as a working fluid and containing: A pressurizing unit, suitable for increasing the pressure of the refrigerant; A condensing unit connected to the relatively downstream of the pressurizing unit and adapted to receive the refrigerant and reduce the temperature of the refrigerant; A pressure reducing unit connected to the relatively downstream of the condensing unit and adapted to receive the refrigerant and reduce the pressure of the refrigerant and discharge; An evaporation unit connected between the depressurization unit and the pressurization unit, and is suitable for receiving the refrigerant and raising the temperature of the refrigerant and then introducing it into the pressurizing unit to form a fluid circulation; and A fluid control unit, which connects the relatively downstream of the condensing unit and the relatively upstream of the pressurizing unit, and is suitable for conveying the refrigerant discharged from the condensing unit to the pressurizing unit, and includes an inlet pipe connected to the depressurizing unit, A sensor connected to the inlet pipe and suitable for sensing a property parameter of the refrigerant located in the inlet pipe, at least one decompression piece connected with the inlet pipe and suitable for decompressing and throttling the refrigerant, and a communicating The at least one pressure reducing element is connected to the inlet end of the pressurizing unit and connected to the solenoid valve of the sensing element. The sensing element can be set with a preset value. When the property parameter is greater than the preset value, the electromagnetic valve The valve is opened to allow the refrigerant to circulate. The air conditioning system according to claim 1, wherein the pipe diameter of the pressure reducing element is smaller than the pipe diameter of the inlet pipe. The air-conditioning system according to claim 1 or 2, wherein the at least one pressure reducing member is a capillary tube in a spiral shape to increase the flow path and enhance the pressure reduction effect. The air conditioning system according to claim 1, wherein the decompression unit further includes a one-way valve arranged in parallel with the decompression member to communicate with the inlet pipe and the solenoid valve. The air conditioning system according to claim 1, wherein the sensing element is a pressure sensor, and the property parameter is a pressure value. The air conditioning system according to claim 1, wherein the pressurizing unit is a compressor. The air conditioning system according to claim 1, wherein the condensing unit includes a heat exchanger connected to the outlet of the pressurizing unit and adapted to lower the temperature of the refrigerant. The air conditioning system according to claim 7, wherein the condensing unit further includes a liquid reservoir connected to the heat exchanger and connecting the pressure reducing unit and the inlet of the fluid regulating unit. The air conditioning system according to claim 1, wherein the pressure reducing unit is an expansion valve. The air conditioning system according to claim 4, wherein the one-way valve is a back pressure valve for balancing the pressure in the pipe of the fluid control unit, and can better assist the solenoid valve to close under pressure imbalance.

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