KR102039170B1 - Heat Pump For a Vehicle - Google Patents

Abstract

The present invention relates to a heat pump for an automobile, and more particularly, having a first diverter valve, a second diverter valve, a third diverter valve, a dehumidification line, and the like, for cooling / heating / defrost / The present invention relates to a heat pump for a vehicle performing dehumidifying operation.

Description

Heat Pump For a Vehicle

The present invention relates to a heat pump for an automobile, and more particularly, having a first diverter valve, a second diverter valve, a third diverter valve, a dehumidification line, and the like, for cooling / heating / defrost / The present invention relates to a heat pump for a vehicle performing dehumidifying operation.

Under the keynote of environmentally friendly industrial development and the development of energy sources to replace fossil raw materials, electric vehicles and hybrid vehicles are the most attentionable areas in the automobile industry in recent years. These electric vehicles and hybrid vehicles are equipped with batteries to provide driving power. The batteries are used not only for driving but also for heating and cooling.

When the battery is used as a heat source during the heating and cooling means that the mileage is reduced by that, in order to overcome the above problem, a method of applying a heat pump mainly used as a home air conditioning device in the car has been proposed.

The heat pump is to absorb the heat of low temperature to move the absorbed heat to high temperature. An example heat pump has a cycle in which a liquid refrigerant evaporates in the evaporator, takes heat away from the surroundings, becomes a gas, and again liquefies while releasing heat to the surroundings by the condenser. When applied to an electric vehicle or a hybrid vehicle, there is an advantage that can secure a heat source lacking in the conventional general air conditioning apparatus.

However, when the outside air temperature is too low during heating operation of the vehicle, frost occurs in the external heat exchanger, which requires defrosting operation. At this time, most of the prior art has adopted a method of switching the refrigerant flow in the reverse direction of the refrigerant circulation in the heating operation during the defrosting operation of the heat pump.

However, such a change in the refrigerant circulation direction causes a decrease in the heating performance of the internal heat exchanger at the time of the switching, and in some cases, the heating cannot be provided during the defrosting operation. It is against the purpose of introducing a heat pump system. Therefore, this problem is recognized as the biggest factor to be solved by a vehicle equipped with a heat pump system.

Various studies have been conducted to solve this problem by automobile manufacturers in various countries, but there are still insufficient effective measures to solve the problem of lowering heating performance when defrosting a heat pump.

Republic of Korea Patent Publication No. 10-0556116 Republic of Korea Patent Publication No. 10-2004-0103596

When the heating operation is operated when the outside temperature is low temperature, frost occurs in the external heat exchanger, and the heat exchange in the external heat exchanger is not smoothed by the frost, which leads to a problem in that the heating performance is deteriorated.

The present invention proposes a heat pump configuration and a method of operating a heat pump to prevent frost on the external heat exchanger while maintaining maximum heating performance when the outside air temperature is low.

According to an embodiment of the present invention for solving the above problems a compressor for compressing and discharging the refrigerant; An internal heat exchanger configured to heat exchange the refrigerant discharged from the compressor with the air in the vehicle compartment; First expansion means disposed on a refrigerant line between the internal heat exchanger and the external heat exchanger and provided to expand the refrigerant; An external heat exchanger for exchanging refrigerant with outside air; An evaporator circulating a refrigerant line to heat-exchange the refrigerant supplied to the compressor with air in the vehicle compartment; A second expansion means disposed on a refrigerant line and provided to expand the refrigerant before entering the evaporator; An automotive heat pump comprising: an accumulator for introducing a gaseous refrigerant into the compressor among liquid and gaseous refrigerants on a refrigerant line.

A first direction switching valve for supplying the refrigerant discharged from the compressor to the internal heat exchanger according to the air conditioning mode of the vehicle or to the external heat exchanger side without passing through the internal heat exchanger; Gas-liquid separation means for introducing a liquid phase refrigerant from the refrigerant passing through the first expansion means into the external heat exchanger, and discharging the gaseous refrigerant onto a refrigerant line at a rear end of the external heat exchanger; A second direction switching valve for supplying the refrigerant having passed through the first expansion means to the external heat exchanger through the gas-liquid separation means or directly to the external heat exchanger without passing the gas-liquid separation means; And a third direction switch for supplying the refrigerant passing through the external heat exchanger and the refrigerant passing through the gas-liquid separation means to the second expansion means according to the air conditioning mode of the vehicle, or to the accumulator side without passing through the second expansion means. It provides a vehicle heat pump further comprising a valve.

Here, the heat pump may be used in an electric vehicle or a hybrid vehicle.

And a third heat exchanger disposed in parallel with the evaporator on a refrigerant line between the accumulator and the third direction switching valve, the third heat exchanger being configured to exchange heat with the waste heat recovery unit.

Here, the waste heat recovery unit may include an electric field waste heat recovery unit and a cabin room waste heat recovery unit.

According to one embodiment, the first expansion means may be an electronic expansion means, which is formed to selectively open the refrigerant line (full open) selectively.

According to one embodiment, the dehumidification line for directly supplying the refrigerant from the rear end of the first expansion means to the second expansion means may further include an opening and closing valve for opening and closing the dehumidification line.

According to another embodiment of the present invention, a compressor, a first divert valve, an internal heat exchanger, a first expansion means, a second divert valve, a gas-liquid separator, an external heat exchanger, a third diverter valve, and a second valve on a refrigerant line In the operation method of the heat pump, the expansion means, the evaporator, the accumulator is arranged,

The refrigerant discharged from the compressor by the first direction switching valve is supplied to the internal heat exchanger according to the air conditioning mode of the vehicle, or to the external heat exchanger side without passing through the internal heat exchanger, and the second direction switching valve The refrigerant passing through the first expansion means is supplied to the gas-liquid separation means according to the air conditioning mode of the vehicle, or directly to the external heat exchanger without passing through the gas-liquid separation means, and passes through the external heat exchanger by the third direction switching valve. The refrigerant and the refrigerant passing through the gas-liquid separation means are supplied to the second expansion means according to the air conditioning mode of the vehicle, or to the accumulator side without passing through the second expansion means, and the second expansion means is provided at the rear end of the first expansion means. A dehumidification line for directly supplying refrigerant to the rear end of the expansion means and an on / off valve for opening and closing the dehumidification line, Cooling operation, heating operation, defrosting operation, dehumidification-heating operation are performed by the behavior of the first direction switching valve, the second direction switching valve, the third direction switching valve and the switching valve located on the dehumidification line. It provides a method of operating a heat pump for a vehicle.

According to one embodiment, the third heat exchanger is disposed in parallel with the evaporator on the refrigerant line between the accumulator and the third direction switching valve, the heat exchanger is provided to heat exchange with the waste heat recovery unit.

According to an embodiment, as a cooling operation method, the refrigerant is passed through a compressor, a first expansion means, an external heat exchanger, a second expansion means, an evaporator, an accumulator, a compressor, and the first expansion means is completely opened. It can be characterized.

In addition, the heating operation method may be characterized in that the refrigerant is passed through the compressor, the internal heat exchanger, the first expansion means, the gas-liquid separation means, the external heat exchanger, the accumulator, the compressor in order.

And a defrosting operation, wherein the refrigerant is passed through a compressor, an internal heat exchanger, a first expansion means, an external heat exchanger, a second expansion means, an evaporator, an accumulator, and a compressor, and the first expansion means is completely opened. can do.

In addition, as a dehumidification-heating operation method, the refrigerant is passed through a compressor, an internal heat exchanger, a first expansion means, a gas-liquid separation means, an external heat exchanger, an accumulator, and a compressor, and branched the flow of the refrigerant to the dehumidification line by the branch. It may be characterized by supplying to the evaporator side.

According to an embodiment of the present invention can provide heating even during defrosting operation. More specifically, according to the heat pump system of the present invention, when the defrosting operation is required, the defrosting operation is possible without switching the refrigerant circulation direction during the heating operation to the reverse direction. This can prevent deterioration in heating performance during defrosting.

First of all, according to an embodiment of the present invention, when the heating operation is performed at low temperature, the refrigerant passing through the first expansion means passes through the gas-liquid separation means, and the liquid refrigerant is supplied to the external heat exchanger. The coolant may be discharged on the coolant line at the rear end of the external heat exchanger. As a result, only the liquid refrigerant flows to the external heat exchanger, thereby raising the evaporation temperature in the external heat exchanger to delay the conception.

In addition, according to an embodiment of the present invention has an effect of improving the heating capacity by replenishing the insufficient heat source when the outside temperature is low temperature using waste heat, such as electrical equipment, cabins.

In addition, according to an embodiment of the present invention, the refrigerant of high temperature and high pressure does not pass through the internal heat exchanger during the cooling operation, thereby preventing heat pick-up.

In addition, by providing a separate dehumidification line, it is possible to maximize the effect of dehumidification during dehumidification-heating.

1 is a diagram illustrating a circulation path of a refrigerant in a cooling operation mode in a heat pump system according to an embodiment of the present invention.
FIG. 2 is a view illustrating a circulation path of a refrigerant in a heating operation mode in a heat pump system according to an embodiment of the present invention.
3 is a view illustrating a circulation path of the refrigerant in the defrosting operation mode in the configuration of the heat pump system according to an embodiment of the present invention.
4 is a diagram illustrating a circulation path of a refrigerant in a dehumidification-heating operation mode in the configuration of a heat pump system according to an embodiment of the present invention.

Hereinafter, with reference to the accompanying drawings will be described in detail with respect to the 'heat pump for automobiles' of the present invention. The described embodiments are provided to enable those skilled in the art to easily understand the technical spirit of the present invention, and thus the present invention is not limited thereto. In addition, the matters represented in the accompanying drawings may be different from the form actually embodied in the schematic drawings in order to easily explain the embodiments of the present invention.

The expression 'comprising' certain components merely refers to the presence of the components as an 'open' expression, and should not be understood as excluding additional components.

Further, when a component is referred to as being connected or connected to another component, it should be understood that there may be a direct connection or connection to that other component, but there may be other components in between.

Also, expressions such as 'first, second, third', etc. are used only for distinguishing a plurality of configurations, and do not limit the order or other features between the configurations.

With reference to Figures 1 to 4 will be described for the automotive heat pump system and heat pump operating method of the present invention.

1 is a diagram illustrating a circulation path of a refrigerant in a cooling operation mode in a heat pump system according to an embodiment of the present invention. FIG. 2 is a view illustrating a circulation path of a refrigerant in a heating operation mode in a heat pump system according to an embodiment of the present invention. 3 is a view illustrating a circulation path of the refrigerant in the defrosting operation mode in the configuration of the heat pump system according to an embodiment of the present invention. 4 is a diagram illustrating a circulation path of a refrigerant in a dehumidification-heating operation mode in the configuration of a heat pump system according to an embodiment of the present invention.

First, the configuration of a heat pump for an automobile according to an embodiment of the present invention is as follows.

The heat pump system of the present invention may be applied to an electric vehicle driven only by a battery without an internal combustion engine using fossil fuel, and a hybrid vehicle equipped with an internal combustion engine and a battery at the same time.

Automotive heat pump according to an embodiment of the present invention, the compressor 110, the first direction switching valve 210, the internal heat exchanger 110, the first expansion means 220, the second direction switching on the refrigerant line The valve 240, the external heat exchanger 120, the third direction switching valve 250, the second expansion means 230, and the accumulator (ACC) may be disposed.

And a third heat exchanger 130 disposed in parallel with the evaporator on a refrigerant line between the accumulator ACC and the third direction switching valve 250 to exchange heat with the waste heat recovery unit. have.

More specifically, on the refrigerant line through which the refrigerant flows, a compressor (COMP) for compressing and discharging the refrigerant; An internal heat exchanger (110) for exchanging refrigerant with air in the vehicle compartment; An external heat exchanger (120) for exchanging refrigerant with outside air; An external heat exchanger disposed on a refrigerant line between the internal heat exchanger and the external heat exchanger, and configured to heat-exchange the refrigerant with external air, the first expansion means 220 provided to expand the refrigerant; An evaporator 140 configured to circulate a refrigerant line to heat-exchange the refrigerant supplied to the compressor with air in the vehicle compartment; A second expansion means (230) disposed on the refrigerant line and provided to expand the refrigerant before entering the evaporator (220); An accumulator (ACC) for introducing a gaseous refrigerant into the compressor 110 among liquid and gaseous refrigerants on the refrigerant line.

In addition, the heat pump of the present invention may include a first direction switching valve 210 for switching the flow direction of the refrigerant discharged from the compressor (COMP).

As shown in the figure, the refrigerant line may be branched into line 1-1 and line 1-2 by the first direction switching valve 210.

The first direction switching valve 210 provided on the refrigerant line supplies the refrigerant discharged from the compressor COMP to the internal heat exchanger 110 side or the external heat exchanger 110 without passing through the internal heat exchanger 110 according to the air conditioning mode of the vehicle. Supply to the side of the machine (120). To this end, the first direction switching valve 210 may be formed of a 3-way valve. When the first direction switching valve 210 is a 3-way valve, the operation of supplying the refrigerant to the external heat exchanger 120 and the operation of supplying the refrigerant to the internal heat exchanger 110 may be selectively performed.

 In a conventional heat pump system, when the refrigerant flows into the expansion means through the internal heat exchanger, heat pick-up may occur due to the heat remaining in the internal heat exchanger. Since the 210 immediately discharges the high temperature and high pressure refrigerant to the external heat exchanger 120, the cooling performance is prevented from being lowered due to the heat pickup phenomenon. In other words, the heat pickup may be prevented by using the configuration of the first diverter valve 210 and the path 1-1 through which the refrigerant flows directly to the external heat exchanger 120.

A pressure sensor (not shown) may be mounted on the refrigerant line connecting the compressor COMP and the first direction switching valve 210 to detect the pressure of the refrigerant discharged from the compressor COMP. The first direction switching valve 210 may be controlled based on the sensed pressure information of the refrigerant.

The first direction switching valve 210, the refrigerant of the high temperature and high pressure in the cooling operation mode does not pass through the internal heat exchanger (110). At this time, the high-temperature, high-pressure refrigerant discharged from the compressor (COMP) is condensed in the external heat exchanger 120 after passing through the first expansion means 220 is completely opened.

On the other hand, in the heating operation mode, the defrosting operation mode and the dehumidification-heating operation mode, the first direction switching valve 210 is supplied to the first expansion means 220 after the refrigerant passes through the internal heat exchanger 110. do. At this time, the high temperature and high pressure refrigerant discharged from the compressor (COMP) is condensed while passing through the internal heat exchanger (110), the temperature is lowered, and the refrigerant after condensation passes through the first expansion means (220), and the external heat exchanger (120). Inflow to the side.

On the other hand, the first expansion means 220 according to an embodiment of the present invention may be an electronic expansion means formed to selectively open the refrigerant line (full open). The opening amount of the refrigerant line can be freely adjusted according to the input of the user or the controller. The opening amount is determined according to the pipe shape, which is different from the mechanical expansion means in which the pressure in the refrigerant line cannot be freely adjusted.

Furthermore, the heat pump according to an embodiment of the present invention introduces a liquid refrigerant from the refrigerant passing through the first expansion means 220 into the external heat exchanger 120, and the refrigerant in the gas phase is the external heat exchanger 120. It may further include a gas-liquid separation means for discharging on the refrigerant line of the rear end. Here, the gas-liquid separation means 300 serves to divide the refrigerant into the gas phase and the liquid phase similarly to the accumulator (ACC) described above. However, if the accumulator (ACC) is a configuration focused on supplying the refrigerant in the gas phase to the compressor, the gas-liquid separation means 300 may be said to focus on both the discharge of the gas phase refrigerant and the discharge of the liquid refrigerant.

When the heating operation is performed when the outside temperature is low, the refrigerant passing through the first expansion means passes through the gas-liquid separation means 300, and the liquid refrigerant is supplied to the external heat exchanger 120, and the refrigerant in the gas phase is external heat exchange. It is to be discharged on the refrigerant line of the rear end of the machine (120). As a result, only the liquid refrigerant flows through the external heat exchanger, thereby increasing the evaporation temperature in the external heat exchanger, thereby delaying the conception.

According to an embodiment of the present invention, the refrigerant passing through the first expansion means 220 passes through the gas-liquid separating means 300 to be supplied to the external heat exchanger 120, or the gas-liquid separating means 300. It may further include a second direction switching valve 240 for supplying directly to the external heat exchanger 120 without passing through. Like the first direction switching valve 210, the second direction switching valve 240 may correspond to a 3-way valve.

The second direction switching valve 240 allows the refrigerant passing through the first expansion means 220 to be directly supplied to the external heat exchanger 120 in the cooling operation mode and the defrosting operation mode. In the heating operation mode, the refrigerant passing through the first expansion means 220 is supplied to the external heat exchanger 120 through the gas-liquid separation means 300. In the heating operation mode and the dehumidification-heating operation mode, the second direction switching valve 240 is interlocked with the gas-liquid separation means 300.

In addition, the heat pump of the present invention may further include a third direction switching valve 250 for switching the flow direction of the refrigerant passing through the external heat exchanger 120. The third diverter valve 250 according to an embodiment of the present invention is located between the external heat exchanger 120 and the second expansion means 230.

The third direction switching valve 250 serves to introduce the refrigerant passing through the external heat exchanger 120 to the accumulator (ACC) side or to the second expansion means 230. Like the first diverter valve 210, the third diverter valve 250 may correspond to a three-way valve. When the third diverter valve 250 is a three-way valve, the refrigerant may accumulate (ACC). And supplying the refrigerant to the second expansion means 240 may be selectively performed.

Here, the second expansion means 230 may be a mechanical expansion means, and the pressure difference before and after the second expansion means 230 is set constant according to the pipe shape. In view of cost reduction, in the present invention, only the first expansion means 220 is sufficient as the electric expansion means.

Specifically, the third direction switching valve 250 is supplied to the accumulator (ACC) after the refrigerant passes through the second expansion means 230 and the evaporator 140 in the cooling operation mode and the defrost operation mode. The refrigerant condensed after passing through the external heat exchanger 120 is expanded under reduced pressure while passing through the second expansion means 230, and flows into the accumulator ACC through the evaporator 140.

On the other hand, the third diverter valve 250 allows the refrigerant to be supplied to the accumulator (ACC) side without passing through the second expansion means 230 and the evaporator 140 in the heating operation mode and the dehumidification-heating operation mode.

When the third heat exchanger 130 is disposed between the accumulator ACC and the third direction switching valve 250, the refrigerant flows into the accumulator ACC through the third heat exchanger 130. The refrigerant that is evaporated while passing through the external heat exchanger 120 and mixed with the low-temperature low-pressure gas phase and the liquid phase may pass through the third heat exchanger 130 to receive secondary heat to evaporate.

In other words, the accumulator (ACC) is a structure in which only the gaseous refrigerant in the gaseous phase and the liquid phase refrigerant can be introduced into the compressor (COMP), and in some cases, the liquid phase refrigerant may be formed to be stored.

The behavior of the refrigerant caused by the first direction switching valve 210, the second direction switching valve 240, and the third direction switching valve 250 will be described later in detail in the method of operating the heat pump.

On the other hand, the heat pump according to an embodiment of the present invention may further include a heat core 310 in the air conditioning case 10 to compensate for the heat source lacking during the heating operation. The heat core 310 is connected to a battery provided in the vehicle to receive the energy required for heat generation. The heat core 310 may correspond to the PTC heater 310. If necessary, the inside of the air conditioning case is heated to a temperature desired by the vehicle occupant. The heat core 310 assists in heating operation mode of the heat pump of the present invention and contributes to raising the heating temperature to a desired temperature within a short time.

Next, a third heat exchanger 130 according to an embodiment of the present invention will be described in detail. The third heat exchanger 130 of the present invention is positioned between the third direction switching valve 250 and the accumulator (ACC) to supply waste heat to the refrigerant line.

The third heat exchanger 130 receives waste heat from the waste heat recovery unit 150. The waste heat recovery unit 150 may include an electric field waste heat recovery unit or a cabin room waste heat recovery unit. That is, the waste heat of the electrical equipment and / or the cabin is provided on the refrigerant line through the third heat exchanger 130. By using the waste heat provided on the refrigerant line, the temperature of the refrigerant flowing into the compressor (COMP) can be increased, thereby reducing the power required for driving the compressor, and also improving the heating capacity at low ambient temperatures. .

More specifically, the third heat exchanger 130 of the present invention may be divided into a waste heat side part 131 and a refrigerant side part 132. The third heat exchanger 130 meets two different fluids and transfers heat energy of each fluid. Since the third heat exchanger 130 is not connected to a separate heat providing means, the third heat exchanger 130 is based on the third law of thermodynamics. This will transfer heat from the fluid with the hotter temperature to the fluid with the colder temperature. The fluids encountered in the third heat exchanger 130 are configured not to be mixed with each other.

According to an embodiment, the third heat exchanger 130 may be formed in the same function and shape as a conventional chiller commonly used as a cooler.

Hereinafter, the operation method of the heat pump for a vehicle of the present invention will be described in more detail with reference to the drawings.

Cooling operation mode, heating operation mode, defrosting operation mode and dehumidification-heating operation mode of the present invention on / off, the temperature control of the vehicle according to the air conditioning mode, the behavior of the valve for switching between the air conditioning mode and the user's choice or vehicle It can be adjusted and operated automatically by the controller. Here, the controller may mean a conventional vehicle control unit (VCU) provided in a vehicle.

The controller senses the pressure information of the refrigerant received through the pressure sensor (not shown) and the temperature of the refrigerant received through the temperature sensor (not shown) to drive the compressor in each air conditioning mode described below. The opening degree of the expansion means (220, 230) and the opening degree of the opening and closing valve 260 is adjusted. On the other hand, as described above, the first expansion means 220 is configured by the electronic expansion means can be reflected very quickly the control input of the controller to the heat pump system of the present invention. In addition, the controller may also play a role of controlling the air volume of the opening and closing door and the blowing fan. In addition, the controller may determine whether the waste heat recovery unit recovers waste heat and provides calories, a calorie providing time, and the like according to a heating load required for a vehicle or a vehicle air conditioning mode.

According to the operating method of the automotive heat pump of the present invention on the refrigerant line compressor (COMP), the first direction switching valve 210, the internal heat exchanger 110, the first expansion means 220, the second direction switching valve ( 240, operation of the heat pump in which the gas-liquid separation means 300, the external heat exchanger 120, the third direction switching valve 250, the second expansion means 230, the evaporator 140, the accumulator (ACC) is disposed In the method,

The refrigerant discharged from the compressor COMP by the first direction switching valve 210 is supplied to the internal heat exchanger 110 according to the air conditioning mode of the vehicle, or the external heat exchanger 120 does not pass through the internal heat exchanger 110. Supply to the gas-liquid separating means 300 according to the air-conditioning mode of the vehicle or the refrigerant passing through the first expansion means 220 by the second direction switching valve 240, or the gas-liquid separating means Directly supplied to the external heat exchanger 120 without passing through the 300, the refrigerant passing through the external heat exchanger 120 and the gas-liquid separation means 300 by the third direction switching valve 250 The refrigerant is supplied to the second expansion means 230 according to the air conditioning mode of the vehicle, or the refrigerant is supplied to the accumulator (ACC) side without passing through the second expansion means 230, and at the rear end of the first expansion means 220. The refrigerant is directly directed to the rear end of the second expansion means 230. A dehumidification line to be supplied to the air and an on / off valve 260 to open and close the dehumidification line, wherein the first direction switching valve 210, the second direction switching valve 240, the third direction switching valve 250 and the Cooling operation, heating operation, defrosting operation, dehumidification-heating operation is performed by the behavior of the on-off valve 260 located on the dehumidification line.

In the operating method of the heat pump according to an embodiment of the present invention is disposed in parallel with the evaporator 140 on the refrigerant line between the accumulator (ACC) and the third direction switching valve 250, waste heat recovery unit ( The third heat exchanger 130 is provided to heat exchange with the 150; In this case, the refrigerant flowing out to the accumulator (ACC) side of the third direction switching valve 250 is the third heat exchanger (130) It may be passed through the accumulator (ACC) side.

Next, a cooling operation mode of the present invention will be described with reference to FIG. 1.

As the cooling operation method, the refrigerant is compressed into a compressor (COMP), a first expansion means 220, an external heat exchanger 120, a second expansion means 230, an evaporator 140, an accumulator (ACC) and a compressor (COMP). Pass in order, the first expansion means 220 is characterized in that the full open (Full open).

Here, the path line 1-2 of the first direction switching valve 210 toward the internal heat exchanger 110 is closed and only the path line 1-1 directly connected to the external heat exchanger 120 is opened. In the present invention, directly connected to the external heat exchanger 120 may mean that the external heat exchanger 120 is connected to the external heat exchanger 120 through the first expansion means 220 in a fully open state.

At this time, the first expansion means 220 is fully open to minimize the pressure drop and the state change of the refrigerant. Therefore, the refrigerant of the high temperature, high pressure, and gaseous phase discharged from the compressor COMP passes through the first expansion means 220 as it is, and then condenses as it exchanges heat with cold air in the external heat exchanger 120. The refrigerant converts into a liquid refrigerant.

In this process, the second direction switching valve 240 opens a path (line 1-3) for supplying the refrigerant to the external heat exchanger (120), and a path (line 1-4) for supplying the gas-liquid separation means (300). Closes.

Subsequently, the refrigerant passing through the external heat exchanger 120 passes through the third direction switching valve 250 and expands under reduced pressure in the course of passing through the second expansion means 230 to become a low temperature low pressure liquid refrigerant. It is introduced to the evaporator 140 side. At this time, the third direction switching valve 250 closes the path (line 1-8) for supplying the refrigerant to the accumulator (ACC) side, and opens only the path (line 1-7) of the second expansion means 230 side.

The low temperature low pressure liquid refrigerant introduced into the evaporator 140 cools the air supplied by the blower fan 11 inside the air conditioning case 10, thereby cooling the vehicle interior. In this process, the door 12 closes the air flow of the internal heat exchanger 110 and flows into the air conditioning case 10 to meet the evaporator 140 to immediately discharge the cool air into the cabin.

Thereafter, the refrigerant mixed with the low-temperature, low-pressure gaseous phase and the liquid phase passed through the evaporator 140 passes through the accumulator ACC and flows back into the compressor COMP. Here, the accumulator ACC separates the liquid refrigerant and the gaseous refrigerant from the refrigerant supplied to the compressor COMP so that only the gaseous refrigerant may be supplied to the compressor COMP. The separated liquid refrigerant can be stored.

In the cooling operation, the refrigerant is circulated in this manner.

That is, in the cooling operation mode, the refrigerant is discharged from the compressor and passes through the first expansion means 220 which is full open as it is, and the condensation in the external heat exchanger 120, the second expansion means 230. In the process of evaporation under reduced pressure, the evaporator 140 is sequentially evaporated, and the coolant coolant meets the air introduced into the air conditioning case 10 to cool the inside of the compartment.

Referring to Figure 2, the heating operation mode will be described.

As the heating operation method, the refrigerant is compressed into a compressor (COMP), an internal heat exchanger (110), a first expansion means (220), a gas-liquid separation means (300), an external heat exchanger (120), an accumulator (ACC), and a compressor (COMP). It is characterized by passing in order.

Here, the path (line 1-2) to the internal heat exchanger 110 side is opened and the path (line 1-1) directly connected to the external heat exchanger 120 side is closed by the driving of the first direction switching valve 210. . Therefore, the high temperature, high pressure, and gaseous refrigerant discharged from the compressor flow into the internal heat exchanger 110.

The refrigerant of high temperature, high pressure, and gaseous phase introduced into the internal heat exchanger 110 is condensed while exchanging heat with the air introduced into the air conditioning case 10 through the blower fan 11 to convert the refrigerant in the gas phase into a liquid refrigerant. In addition, the air passing through the internal heat exchanger 110 is converted into a warm air, and is supplied to the vehicle interior to heat the interior of the vehicle compartment. In this process, the door 12 opens the air flow on the internal heat exchanger 110 and heats the air by flowing into the air-conditioning case 10 and then encountering the internal heat exchanger 110 to discharge hot air into the cabin. .

The refrigerant passing through the internal heat exchanger 110 is suitably opened under the first expansion means 220 to become a low pressure refrigerant. The refrigerant is supplied to the external heat exchanger 120. However, the refrigerant passing through the first expansion means 220 passes through the gas-liquid separation means 300 by the second direction switching valve 240 before entering the external heat exchanger 120. Here, the second direction switching valve 240 is a path for supplying the refrigerant directly to the external heat exchanger 120 (line 1-3) is closed, the path for supplying the gas-liquid separation means 300 (line 1-4 Open). Only the refrigerant in the liquid phase passing through the gas-liquid separation means 300 passes through the external heat exchanger 120, and the refrigerant in the gas phase is separated from the liquid refrigerant and supplied to the rear end side of the external heat exchanger 120. This maximizes the evaporation in the external heat exchanger (120).

 In the external heat exchanger 120, the liquid refrigerant evaporates, changes into a refrigerant in a gas and liquid state, and then flows to the accumulator (ACC) side. At this time, the path (line 1-8) for supplying to the accumulator (ACC) side is provided with a third direction switching valve 250 is open, the path (line 1-7) of the second expansion means 230 side is closed.

According to an embodiment, when the third third heat exchanger 130 is provided between the accumulator ACC and the third direction switching valve 250, the refrigerant may be secondarily evaporated by the third heat exchanger 130. have.

The refrigerant introduced into the third heat exchanger 130 may exchange heat with the fluid line separately provided on the waste heat recovery unit. Here, the heat exchange may be selectively performed. The heat exchange may be performed in such a way that the refrigerant is provided with heat from the fluid line on the waste heat recovery part when the heat is increased to improve the heating performance. For example, when the outdoor temperature is a low temperature below a predetermined temperature (for example, -10 ° C), in addition to the heating performance by the flow of a normal refrigerant, an operation mode in which waste heat is actively supplied from the waste heat recovery unit (high ( High heating mode) to satisfy the heating load required for the vehicle.

Refrigerant with a relatively low temperature, low pressure, and a mixture of gaseous and liquid phases when introduced into the third heat exchanger 130 is a refrigerant having a relatively high temperature, low pressure, and a mixture of gas and liquid phases while passing through the third heat exchanger 130. Flows into the accumulator (ACC) side. This action, in turn, increases the efficiency of the compressor (COMP) to increase the heating efficiency.

When the heating operation mode is summarized once again, the refrigerant is discharged from the compressor COMP, condensed in the internal heat exchanger 110, expanded under reduced pressure in the first expansion means 220, and evaporated in the external heat exchanger 120. In turn, the accumulator (ACC) passes through the compressor back into the compressor. However, in this process, only the liquid refrigerant is supplied to the external heat exchanger 120 by the gas-liquid separation means 300, thereby increasing the evaporation efficiency. Thus, when the outdoor temperature is a low temperature state, the external heat exchanger 120 is provided. It is possible to delay the phenomenon of frost formation.

Referring to FIG. 3, the defrosting operation mode will be described.

In the defrosting operation method shown in FIG. 3, the refrigerant is compressed into a compressor (COMP), an internal heat exchanger 110, a first expansion means 220, an external heat exchanger 120, a second expansion means 230, and an evaporator 140. ), The accumulator (ACC), the compressor (COMP) in order to pass through, the first expansion means 220 is characterized in that it is fully open.

When defrosting is required during the heating operation, defrosting is prevented without interrupting the heating operation, so that the heating calorific value is prevented.

Here, the path (line 1-2) to the internal heat exchanger 110 side is opened and the path (line 1-1) directly connected to the external heat exchanger 120 side by the driving of the first direction switching valve 210 is closed. do. Therefore, the high temperature, high pressure, and gaseous refrigerant discharged from the compressor flow into the internal heat exchanger 110.

The high temperature, high pressure, and gaseous refrigerant introduced into the internal heat exchanger 110 is condensed while exchanging heat with the air introduced into the air conditioning case through the blower fan 11 to convert the refrigerant in the gas phase into a liquid refrigerant. The air passing through the internal heat exchanger 110 is changed to warm air and then supplied to the vehicle interior to heat the interior of the vehicle compartment.

Subsequently, the first expansion means 220 positioned on the path through which the refrigerant flows is fully open to minimize the pressure drop and the change of state of the refrigerant. The refrigerant passing through the internal heat exchanger 110 may be condensed once again while exchanging heat with the outside air in the external heat exchanger 120.

At this time, since the refrigerant maintains the heat when discharged from the compressor COMP to some extent (approximately 40 ° C. to 50 ° C.), it is possible to prevent frost from forming in the external heat exchanger 120 or to remove the frost formed. Will be. In other words, the defrosting ability is improved by circulating the external heat exchanger 120 at a medium temperature and high pressure without expanding the refrigerant passing through the internal heat exchanger 110. It has the advantage of defrosting effect through simple valve operation while maintaining heating performance.

At this time, the second direction switching valve 240 opens the path (line 1-3) for directly supplying the refrigerant to the external heat exchanger side, the path (line 1-4) for supplying the gas-liquid separation means 300 is closed. do.

Subsequently, the refrigerant passing through the external heat exchanger 120 passes through the third direction switching valve 250 and expands under reduced pressure in the course of passing through the second expansion means 230 to become a low temperature low pressure liquid refrigerant. It is introduced to the evaporator 140 side. At this time, the third direction switching valve 250 closes the path (line 1-8) for supplying the refrigerant to the accumulator (ACC) side, and opens only the path (line 1-7) of the second expansion means 230 side.

The refrigerant passing through the external heat exchanger 120 passes through the third direction switching valve 250 and expands under reduced pressure while passing through the second expansion means 230 to become a state of low temperature, low pressure, and gas phase, and then the evaporator 140. Flows into. In the evaporator 140, the evaporator 140 meets the air introduced from the outside to be evaporated, thereby converting the gas into a low-temperature, low-pressure gas phase and a liquid state, and flowing to the accumulator (ACC) side. Since the air introduced into the air conditioning case 11 and cooled in the evaporator 140 is heated again while passing through the internal heat exchanger 110, the heating performance can be properly maintained.

That is, in the defrosting operation mode, the refrigerant is discharged from the compressor, condensed in the internal heat exchanger 110, passes through the first expansion means 220 which is completely open, and recondensed in the external heat exchanger 120, and The expansion step under reduced pressure in the second expansion means 230, the evaporator 140 passes through the process sequentially.

Next, the dehumidification-heating operation mode will be described with reference to FIG. 4.

As a dehumidification-heating operation method, the refrigerant is compressed into a compressor (COMP), an internal heat exchanger 110, a first expansion means 220, a gas-liquid separation means 300, an external heat exchanger 120, an accumulator (ACC), and a compressor ( COMP) in order to pass, characterized in that for supplying part of the flow of the refrigerant to the dehumidification line (line 1-9) to the evaporator side.

Here, the path line 1-2 of the first direction switching valve 210 toward the internal heat exchanger 110 is opened and the path line 1-1 directly connected to the external heat exchanger 120 is closed. Therefore, the high temperature, high pressure, and gaseous refrigerant discharged from the compressor flow into the internal heat exchanger 110.

The high temperature, high pressure, and gaseous refrigerant introduced into the internal heat exchanger 110 is condensed while exchanging heat with the air introduced into the air conditioning case through the blower fan 11 to convert the refrigerant in the gas phase into a liquid refrigerant. The air passing through the internal heat exchanger 110 is changed to warm air and then supplied to the vehicle interior to heat the interior of the vehicle compartment. In this process, the door 12 opens the air flow on the internal heat exchanger 110 and heats the air by flowing into the air-conditioning case 10 and then encountering the internal heat exchanger 110 to discharge hot air into the cabin. .

The refrigerant passing through the internal heat exchanger 110 is suitably opened under the first expansion means 220 to become a low pressure refrigerant. The refrigerant is supplied to the external heat exchanger 120. However, the refrigerant passing through the first expansion means 220 passes through the gas-liquid separation means 300 by the second direction switching valve 240 before entering the external heat exchanger 120. Here, the second direction switching valve 240 is a path for supplying the refrigerant directly to the external heat exchanger 120 (line 1-3) is closed, the path for supplying the gas-liquid separation means 300 (line 1-4 Open). Only the refrigerant in the liquid phase passing through the gas-liquid separation means 300 passes through the external heat exchanger 120, and the refrigerant in the gas phase is separated from the liquid refrigerant and supplied to the rear end side of the external heat exchanger 120. This maximizes the evaporation in the external heat exchanger (120).

 In the external heat exchanger 120, the liquid refrigerant evaporates, changes into a refrigerant in a gas and liquid state, and then flows to the accumulator (ACC) side. At this time, the path (line 1-8) for supplying to the accumulator (ACC) side is provided with a third direction switching valve 250 is open, the path (line 1-7) of the second expansion means 230 side is closed.

According to an embodiment, when the third third heat exchanger 130 is provided between the accumulator ACC and the third direction switching valve 250, the refrigerant may be secondarily evaporated by the third heat exchanger 130. have.

On the other hand, in the dehumidification-heating operation mode according to an embodiment of the present invention, the dehumidification line (line 1-6) and the opening and closing valve 260 for opening and closing the dehumidification line is formed, the first expansion means ( Some of the refrigerant expanded under reduced pressure by 220 may directly flow into the evaporator 140.

The refrigerant having a high temperature flows into the evaporator 140, and thus may perform a dehumidification function.

Specifically, when it is determined that the humidity is high by the humidity sensor not shown in the air conditioning case, the wet air introduced by the blower fan is condensed to come into contact with the surface of the evaporator 140, and then the evaporator (using the door 12) The air in contact with 140 is transferred to the internal heat exchanger 110 which is exothermic so that dry air from which moisture is removed is discharged into the cabin.

In the above detailed description of the present invention, only specific embodiments thereof have been described. It is to be understood, however, that the present invention is not to be limited to the specific forms referred to in the description, but rather includes all modifications, equivalents, and substitutions within the spirit and scope of the invention as defined by the appended claims. It must be understood.

10: air conditioning case (duct) 210: first direction switching valve
11: blowing fan 220: first expansion means
12: door 240: second direction switching valve
110: internal heat exchanger 250: on-off valve
120: external heat exchanger 260: third direction switching valve
130: third heat exchanger 300: gas-liquid separation means
140: evaporator 230: second expansion means
150: electric field waste heat recovery unit 310: heat core
320: battery

Claims (11)

A compressor for compressing and discharging the refrigerant; An internal heat exchanger configured to heat exchange the refrigerant discharged from the compressor with the air in the vehicle compartment; First expansion means disposed on a refrigerant line between the internal heat exchanger and the external heat exchanger and provided to expand the refrigerant; An external heat exchanger for exchanging refrigerant with outside air; An evaporator circulating a refrigerant line to heat-exchange the refrigerant supplied to the compressor with air in the vehicle compartment; A second expansion means disposed on a refrigerant line and provided to expand the refrigerant before entering the evaporator; An automotive heat pump comprising: an accumulator provided to introduce a refrigerant in a liquid phase and a refrigerant in a refrigerant line into the compressor.
A first direction switching valve for supplying the refrigerant discharged from the compressor to the internal heat exchanger in the heating operation mode, the defrosting operation mode, and the dehumidification-heating operation mode, or to the external heat exchanger side without passing through the internal heat exchanger in the cooling operation mode;
Gas-liquid separation means for introducing a liquid phase refrigerant from the refrigerant passing through the first expansion means into the external heat exchanger, and discharging the gaseous refrigerant onto the refrigerant line at the rear end of the external heat exchanger;
In the heating operation mode or the dehumidification-heating operation mode, the refrigerant passing through the first expansion means is supplied to the external heat exchanger through the gas-liquid separation means, and in the cooling operation mode or the defrost operation mode, the refrigerant is passed through the first expansion means. A second diverter valve for directly supplying a refrigerant to an external heat exchanger without passing through the gas-liquid separation means;
The refrigerant passing through the external heat exchanger is supplied to the accumulator after passing through the second expansion means and the evaporator in the cooling operation mode or the defrosting operation mode, or the gas-liquid separation means in the heating operation mode or the dehumidification-heating operation mode. A third direction switching valve for supplying a refrigerant to the accumulator side without passing through the second expansion means; And
And a third heat exchanger disposed in parallel with the evaporator on the refrigerant line between the accumulator and the third directional valve, the heat exchanger being configured to exchange heat with the waste heat recovery unit.
The method of claim 1,
The heat pump is a vehicle heat pump, characterized in that used in electric vehicles or hybrid vehicles.
delete The method of claim 1,
The first expansion means is a vehicle heat pump, characterized in that the electronic expansion means, which is formed to selectively open the refrigerant line (full open).
The method of claim 1,
And a dehumidification line for directly supplying refrigerant from the rear end of the first expansion means to the rear end of the second expansion means, and an on / off valve for opening and closing the dehumidification line.
Compressor, first direction switching valve, internal heat exchanger, first expansion means, second direction switching valve, gas-liquid separation means, external heat exchanger, third direction switching valve, second expansion means, evaporator and accumulator are arranged on the refrigerant line. In the operation method of the heat pump,
The refrigerant discharged from the compressor by the first direction switching valve is supplied to the internal heat exchanger in the heating operation mode, the defrosting operation mode, and the dehumidification-heating operation mode, or in the cooling operation mode without passing through the internal heat exchanger side. Supplies to,
In the heating operation mode or the dehumidification-heating operation mode by the second direction switching valve, the refrigerant passing through the first expansion means is supplied to the external heat exchanger through the gas-liquid separation means, or in the cooling operation mode or the defrost operation mode. Supplying the refrigerant having passed through the first expansion means directly to the external heat exchanger without passing through the gas-liquid separation means,
In the cooling operation mode or the defrost operation mode by the third direction switching valve, the refrigerant passing through the external heat exchanger is supplied to the accumulator after passing through the second expansion means and the evaporator, or the heating operation mode or the dehumidification-heating operation. In the mode, the refrigerant passing through the gas-liquid separation means is supplied to the accumulator without passing through the second expansion means and the evaporator,
A dehumidification line for directly supplying refrigerant from the rear end of the first expansion means to the rear end of the second expansion means, and an on / off valve for opening and closing the dehumidification line,
A third heat exchanger disposed in parallel with the evaporator on a refrigerant line between the accumulator and the third direction switching valve to provide heat exchange with the waste heat recovery unit,
Cooling operation, heating operation, defrosting operation, dehumidification-heating operation is performed by the behavior of the first direction switching valve, the second direction switching valve, the third direction switching valve and the switching valve located on the dehumidification line. Method of operation of a car heat pump
delete The method of claim 6,
A cooling operation method, wherein the refrigerant is passed through a compressor, a first expansion means, an external heat exchanger, a second expansion means, an evaporator, an accumulator, and a compressor, and the first expansion means is completely opened. How to operate the pump.
The method of claim 6,
A heating operation method, wherein the refrigerant is passed through a compressor, an internal heat exchanger, a first expansion means, a gas-liquid separation means, an external heat exchanger, an accumulator, and a compressor in order.
The method of claim 6,
As the defrosting method, the refrigerant is passed through a compressor, an internal heat exchanger, a first expansion means, an external heat exchanger, a second expansion means, an evaporator, an accumulator, and a compressor, and the first expansion means is completely opened. Method of operation of automotive heat pump.
The method of claim 6,
A dehumidification-heating operation method, wherein the refrigerant is passed through a compressor, an internal heat exchanger, a first expansion means, a gas-liquid separation means, an external heat exchanger, an accumulator, and a compressor, and a branch of the refrigerant flows through the dehumidification line to partially evaporate. Method for operating a heat pump for a vehicle, characterized in that the supply to.

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