KR101587108B1 - Control method of heat pump system for vehicle and its system - Google Patents

Abstract

The present invention relates to a control method and system for a vehicular heat pump system, and more particularly, to a control method and system for a vehicular heat pump system. More specifically, in order to satisfy a target discharge temperature in a heat pump mode, when the compressor rotational speed is smaller than an upper limit value And the electric heater is operated only when the number of revolutions of the compressor reaches the upper limit value of the maximum number of revolutions of the compressor. By thus controlling the compressor and the electric heater in the variable control simultaneously to satisfy the target discharge temperature, It is possible to solve the problem that the convergence of temperature is lowered or unstable and the upper limit value of the maximum number of revolutions of the compressor is differentiated according to the condition without operating the compressor at the maximum number of revolutions in the maximum heating mode to reduce the complaints of the passenger due to the noise of the compressor Of course, improve the durability of the compressor and the stability of the system. Which it relates to a control method for a vehicle heat pump system and a system.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control method of a heat pump system for a vehicle,

The present invention relates to a control method and system for a vehicular heat pump system, and more particularly, to a control method and system for a vehicular heat pump system. More specifically, in order to satisfy a target discharge temperature in a heat pump mode, when the compressor rotational speed is smaller than an upper limit value In the maximum heating mode, the compressor is operated only at the maximum number of revolutions, and the upper limit of the maximum number of revolutions of the compressor is set according to the conditions. When the maximum number of revolutions of the compressor reaches the upper limit of the maximum number of revolutions of the compressor, And more particularly, to a control method and system for a differentiated heat pump system for a vehicle.

Background Art [0002] A vehicle air conditioner generally includes a cooling system for cooling the interior of a vehicle and a heating system for heating the interior of the vehicle. Wherein the cooling system is configured to cool air in the vehicle interior by exchanging air passing through the outside of the evaporator at the evaporator side of the refrigerant cycle with the refrigerant flowing in the evaporator to convert into cool air, The air passing through the outside of the core is exchanged with the cooling water flowing in the inside of the heater core to warm the inside of the vehicle.

A heat pump system which can selectively perform cooling and heating by switching the flow direction of refrigerant by using one refrigerant cycle is different from the above vehicle air conditioning system. For example, two heat exchangers (That is, an indoor heat exchanger installed inside the air conditioner case for exchanging heat with air blown into the vehicle interior, and an outdoor heat exchanger for exchanging heat outside the air conditioner case), and a direction control valve for switching the flow direction of the refrigerant do. Therefore, when the cooling mode is operated according to the flow direction of the refrigerant by the direction control valve, the indoor heat exchanger functions as a cooling heat exchanger. When the heating mode is activated, the indoor heat exchanger functions as a heating heat exchanger .

Various kinds of such a heat pump system for vehicles have been proposed, and a representative example thereof is shown in Fig.

1 includes a compressor 30 for compressing and discharging a refrigerant, a high-pressure side heat exchanger 32 for dissipating the refrigerant discharged from the compressor 30, A first expansion valve 34 and a first bypass valve 36 for selectively passing the refrigerant passed through the high pressure side heat exchanger 32 and a second expansion valve 34 and a first bypass valve 36 Pressure side heat exchanger (60) for evaporating the refrigerant that has passed through the outdoor heat exchanger (48), and a low-pressure side heat exchanger (60) for evaporating the refrigerant that has passed through the outdoor heat exchanger An accumulator 62 for separating the refrigerant having passed through it into a gas phase and a liquid phase refrigerant, an internal heat exchanger 50 for exchanging heat between the refrigerant supplied to the low pressure side heat exchanger 60 and the refrigerant returning to the compressor 30, Pressure side heat exchanger (60), and a low-pressure side heat exchanger The second expansion valve 56 and the second expansion valve 56 are provided in parallel with each other so as to selectively connect the outlet side of the outdoor heat exchanger 48 and the inlet side of the accumulator 62, 2 bypass valve (58).

1, reference numeral 10 denotes an air conditioning case in which the high-pressure side heat exchanger 32 and the low-pressure side heat exchanger 60 are incorporated, reference numeral 12 denotes a temperature control door for controlling the mixing amount of cold air and warm air, And an air blower installed at the entrance of the air conditioning case.

On the other hand, an electric heater (not shown) is installed inside the air conditioner case 10 to secure the heating performance.

The first bypass valve 36 and the second expansion valve 56 are closed and the first expansion valve (heating mode) 34 and the second bypass valve 58 are opened. In addition, the temperature control door 12 operates as shown in Fig. Therefore, the refrigerant discharged from the compressor 30 flows through the high-pressure side heat exchanger 32, the first expansion valve 34, the outdoor heat exchanger 48, the high-pressure portion 52 of the internal heat exchanger 50, The accumulator 62 and the low pressure section 54 of the internal heat exchanger 50 in this order. That is, the high-pressure side heat exchanger 32 serves as a radiator and the outdoor heat exchanger 48 serves as an evaporator.

When the air conditioning mode (cooling mode) is activated, the first bypass valve 36 and the second expansion valve 56 are opened, and the first expansion valve 34 and the second bypass valve 58 are closed do. Further, the temperature control door 12 closes the high-pressure side heat exchanger 32 passage. Therefore, the refrigerant discharged from the compressor 30 flows through the high-pressure side heat exchanger 32, the first bypass valve 36, the outdoor heat exchanger 48, the high-pressure portion 52 of the internal heat exchanger 50, The low pressure side heat exchanger 60, the accumulator 62 and the low pressure portion 54 of the internal heat exchanger 50 in this order. That is, the low-pressure side heat exchanger 60 serves as an evaporator, and the high-pressure side heat exchanger 32 closed by the temperature control door 12 serves as a radiator as in the heat pump mode do.

However, in the conventional vehicular heat pump system, the rotational speed of the compressor 30 and the calorific value of the electric heater are controlled to be variable at the same time in order to satisfy the target discharge temperature during the heat pump mode (heating mode) There is a problem that the convergence of the indoor air discharge temperature is deteriorated or unstable due to the variable control of the rotational speed of the electric heater 30 and the calorific value of the electric heater.

In addition, in the maximum heating mode, there is a problem that the compressor 30 is operated only at the maximum number of revolutions, resulting in a dissatisfaction of the passenger due to the increase in noise of the compressor 30. [

In order to satisfy the target discharge temperature in the heat pump mode, the object of the present invention to solve the above problems is to provide a compressor capable of performing variable control only when the number of revolutions of the compressor is smaller than the upper limit value of the maximum number of revolutions of the compressor, A problem that the convergence of the air discharge temperature of the vehicle inside the vehicle occurs when the compressor and the electric heater are controlled at the same time to satisfy the target discharge temperature by making the electric heater operate only when the upper limit of the number is reached, And the upper limit value of the maximum number of revolutions of the compressor is differentiated according to the conditions without operating the compressor at the maximum number of revolutions in the maximum heating mode to reduce the complaints of the passenger due to the noise of the compressor and also to improve the durability of the compressor and the stability of the system Control method of vehicle heat pump system capable of improving To provide the system.

According to another aspect of the present invention, there is provided a control method for a vehicle heat pump system, including: a first step of receiving various sensor values of a vehicle and calculating a target discharge temperature; A second step of determining whether the vehicle is in an air conditioner mode or a heat pump mode according to a discharge temperature or an occupant selection; and a second step of calculating a deviation between the target discharge temperature and a vehicle interior air discharge temperature A fourth step of calculating the number of revolutions of the compressor in accordance with the deviation of the third step after the third step and the third step; and a fourth step of calculating the maximum number of revolutions of the compressor, If the compressor rotational speed is smaller than the upper limit value of the maximum rotational speed of the compressor, a fifth step of determining whether the compressor rotational speed is smaller than the upper limit value of the compressor maximum rotational speed, A second step of controlling the compressor by a predetermined number of revolutions, and a sixth step of variably controlling the compressor by a predetermined number of revolutions when the compressor rotational speed is not smaller than the upper limit value of the compressor maximum rotational speed, And an eighth step of controlling operation of the electric heater in a state where the operation of the compressor is maintained when the target discharge temperature is higher than the indoor air discharge temperature as a result of the determination of the seventh step .

The compressor further includes a compressor connected to the refrigerant circulation line for compressing and discharging the refrigerant, an evaporator and an indoor heat exchanger disposed inside the air conditioning case, and an outdoor heat exchanger disposed outside the air conditioning case, And a control unit for receiving the various sensor values of the vehicle and calculating a target discharge temperature to control the heat pump system, wherein the control unit includes a heat pump mode Variable control is performed on the compressor with the compressor rotational speed according to the deviation when the compressor rotational speed calculated according to the deviation between the target discharge temperature and the car indoor air discharge temperature is smaller than the upper limit value of the compressor maximum rotational speed, The target discharge temperature is equal to or larger than the upper limit value of the maximum number of revolutions of the compressor, And the operation of the electric heater is controlled in a state where the operation of the compressor is maintained.

In order to satisfy the target discharge temperature in the heat pump mode, only the compressor is variably controlled when the number of rotations of the compressor is smaller than the upper limit value of the maximum number of rotations of the compressor, and only when the number of rotations of the compressor reaches the upper limit of the maximum number of rotations of the compressor It is possible to solve the problem that the convergence of the indoor air discharge temperature occurring in the case of variable control of the compressor and the electric heating heater simultaneously to satisfy the target discharge temperature becomes unstable or unstable.

In addition, in the maximum heating mode, the upper limit of the maximum number of revolutions of the compressor is differentiated according to conditions without operating the compressor at the maximum number of revolutions, thereby reducing the complaints of the passenger due to the noise of the compressor and improving the durability and system stability of the compressor .

The minimum value among the upper limit values of the maximum compressor revolutions per factor according to the outside temperature, the refrigerant pressure, the vehicle speed, the blower air flow rate, the cooling fan rotation speed of the outdoor heat exchanger, and the traveling drive source on / off condition is set as an upper limit value By setting and controlling it, there is no need for a complex additional operation taking into account variable external conditions.

1 is a schematic view showing a conventional heat pump system for a vehicle,
FIG. 2 is a diagram showing an air conditioner mode in a heat pump system for a vehicle according to the present invention,
3 is a view showing a first heating mode of a heat pump mode in a vehicle heat pump system according to the present invention;
4 is a view showing a second heating mode of the heat pump mode in the vehicle heat pump system according to the present invention.
5 is a flowchart showing a control method of a heat pump system for a vehicle according to the present invention,
6 is a flowchart showing a method of controlling the operation of the electric heater in the control method of the vehicle heat pump system according to the present invention.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

First, a heat pump system for a vehicle according to the present invention includes a compressor 100, an indoor heat exchanger 110, a second expansion means 120, an outdoor heat exchanger 130, The first expansion means 140 and the evaporator 160 are sequentially connected to each other and are preferably applied to an electric vehicle or a hybrid vehicle.

A first bypass line R1 for bypassing the first expansion means 140 and the evaporator 160 and a second bypass line R1 for bypassing the outdoor heat exchanger 130 are provided on the refrigerant circulation line R. [ And a first direction switching valve 191 is connected to a branch point of the first bypass line R1 and a second direction switching valve 191 is connected to a branch line of the first bypass line R1, A second direction switching valve 192 is provided at a branch point of the second bypass line R2 and the third direction switching valve 193 is installed at a branch point of the expansion line R3. do.

In addition, a branch line R4 is provided to connect the outlet side refrigerant circulation line R of the first expansion means 140 and the first bypass line R1, and on the branch line R4, A valve 195 is provided.

2, the refrigerant discharged from the compressor 100 flows through the indoor heat exchanger 110, the outdoor heat exchanger 130, the first expansion device 140, the evaporator 160, the compressor The indoor heat exchanger 110 serves as a condenser and the evaporator 160 serves as an evaporator.

Meanwhile, the outdoor heat exchanger 130 functions as a condenser as the indoor heat exchanger 110.

3, the refrigerant discharged from the compressor 100 is supplied to the indoor heat exchanger 110, the second expansion means 120, the outdoor heat exchanger 130, the outdoor heat exchanger 130, 1 bypass line R1 and the compressor 100. The indoor heat exchanger 110 serves as a condenser and the outdoor heat exchanger 130 serves as an evaporator, 1 Refrigerant is not supplied to the expansion means 140 and the evaporator 160.

As described above, the heat pump system of the present invention can share the refrigerant circulation line R with the same refrigerant circulation direction in the air conditioner mode and the heat pump mode, prevents the refrigerant stagnation phenomenon that occurs when the refrigerant does not flow, The circulation line (R) can also be simplified.

In the present invention, the heat pump mode is diversified as the first heating mode and the second heating mode.

At this time, if the outdoor temperature is higher than the reference temperature, the first heating mode is performed in the heat pump mode, and when the outdoor temperature is lower than the reference temperature, the second heating mode is performed in the heat pump mode.

Here, the first heating mode is performed when the outdoor temperature is 0 ° C or higher (image), and the second heating mode is performed when the outdoor temperature is lower than 0 ° C (minus).

Of course, the reference temperature of the outdoor temperature for distinguishing the first and second heating modes is not limited to 0 ° C, but may be changed according to the purpose.

Meanwhile, when dehumidifying the car interior during the first and second heating mode operations, the dehumidifying mode for supplying some refrigerant to the evaporator 160 through the branch line R4 is performed.

Hereinafter, each component of the heat pump system will be described in detail.

First, the compressor 100 installed on the refrigerant circulation line R receives power from a driving source (such as an internal combustion engine or a motor), sucks the refrigerant, compresses the refrigerant, and discharges the compressed refrigerant in a state of high temperature and high pressure.

The compressor 100 sucks and compresses the refrigerant discharged from the evaporator 160 in the air conditioning mode and supplies the compressed refrigerant to the indoor heat exchanger 110. In the heat pump mode, The refrigerant having passed through the first bypass line R1 is sucked, compressed, and supplied to the indoor heat exchanger 110 side.

The indoor heat exchanger 110 is installed inside the air conditioning case 150 and is connected to the refrigerant circulation line R at the outlet side of the compressor 100 and is connected to the air flowing in the air conditioning case 150 The refrigerant discharged from the compressor 100 is heat-exchanged.

The evaporator 160 is installed inside the air conditioning case 150 and is connected to the refrigerant circulation line R at the inlet side of the compressor 100 so that the air flowing in the air conditioning case 150 And the refrigerant supplied to the compressor 100 is heat-exchanged.

The indoor heat exchanger 110 functions as a condenser in both the air conditioning mode and the heat pump mode,

The evaporator 160 serves as an evaporator in the air conditioner mode, and is not operated in the heat pump mode.

The indoor heat exchanger 110 and the evaporator 160 are installed in the air conditioner case 150 at a predetermined distance from the air conditioner case 150, And an indoor heat exchanger 110 are sequentially installed.

2, the low-temperature and low-pressure refrigerant discharged from the first expansion means 140 is supplied to the evaporator 160. At this time, the blower (not shown) Air flowing through the air conditioning case 150 through the evaporator 160 is exchanged with the low temperature low pressure refrigerant in the evaporator 160 to be converted into cool air and then discharged to the vehicle interior The inside of the car is cooled.

3, the high-temperature and high-pressure refrigerant discharged from the compressor 100 is supplied to the indoor heat exchanger 110 and the refrigerant discharged from the outdoor heat exchanger 110 to the indoor heat exchanger 110. In the heat pump mode (first heating mode) in which the indoor heat exchanger 110 functions as a condenser, The air flowing inside the air conditioning case 150 through the blower (not shown) flows through the indoor heat exchanger 110, and the refrigerant in the indoor heat exchanger 110 is heat- And then it is discharged to the inside of the vehicle to heat the inside of the vehicle.

The size of the evaporator 160 may be larger than the size of the indoor heat exchanger 110.

The amount of air passing through the indoor heat exchanger 110 and the amount of air passing through the indoor heat exchanger 110 are adjusted between the evaporator 160 and the indoor heat exchanger 110 in the air conditioning case 150 A temperature control door 151 is provided.

The temperature control door 151 adjusts the amount of air passing through the indoor heat exchanger 110 and the amount of air passing through the indoor heat exchanger 110 to control the temperature of the air discharged from the air conditioning case 150 Can be adjusted appropriately,

2, when the front side passageway of the indoor heat exchanger 110 is completely closed through the temperature control door 151 as shown in FIG. 2, the cold air passing through the evaporator 160 passes through the indoor heat exchanger 110, The indoor heat exchanger 110 is bypassed through the temperature control door 151 as shown in FIG. 3 during the heat pump mode (in the first heating mode) All the air passes through the indoor heat exchanger 110 serving as a condenser and is converted into warm air, and the warm air is supplied to the interior of the vehicle, so that the maximum heating is performed.

The outdoor heat exchanger 130 is installed outside the air conditioning case 150 and is connected to the refrigerant circulation line R to perform heat exchange between the refrigerant circulating in the refrigerant circulation line R and outdoor air .

The outdoor heat exchanger 130 is installed on the front side of the vehicle engine room to exchange heat with the outdoor air.

The outdoor heat exchanger 130 functions as the same condenser as the indoor heat exchanger 110 in the air conditioning mode. At this time, the high-temperature refrigerant flowing in the outdoor heat exchanger 130 is heat-exchanged with the outdoor air, do. In the heat pump mode (first heating mode), the refrigerant acts as an evaporator opposite to the indoor heat exchanger 110. At this time, the low-temperature refrigerant flowing in the outdoor heat exchanger 130 exchanges heat with the outdoor air, .

The first expansion means 140 is installed on the refrigerant circulation line R on the inlet side of the evaporator 160 and expands the refrigerant supplied to the evaporator 160.

That is, the first expansion means 140 causes the refrigerant discharged from the outdoor heat exchanger 130 to expand into a low-temperature and low-pressure liquid state in the air conditioning mode, and then supplied to the evaporator 160 .

The first expansion means 140 may be an expansion valve, but may be an orifice.

The second expansion means 120 may be installed on the refrigerant circulation line R between the indoor heat exchanger 110 and the outdoor heat exchanger 130 so as to perform the outdoor heat exchange Thereby selectively expanding the refrigerant supplied to the compressor 130.

The second expansion means 120 is installed on the expansion line R3 connected in parallel on the refrigerant circulation line R between the indoor heat exchanger 110 and the outdoor heat exchanger 130. [

Here, the second expansion means 120 may include an orifice 121, but may be an expansion valve.

The refrigerant that has passed through the indoor heat exchanger 110 according to the air conditioning mode or the heat pump mode is supplied to the branch line between the expansion line R3 and the refrigerant circulation line R through the expansion line R3, A third direction switching valve 193 for switching the refrigerant flow direction to pass through the expansion means 120 or bypass the second expansion means 120 is provided.

Accordingly, in the air conditioning mode, the refrigerant discharged from the compressor 100 and passed through the indoor heat exchanger 110 by the third direction switching valve 193 bypasses the second expansion means 120 And is supplied to the outdoor heat exchanger 130. In the heat pump mode (in the first heating mode), the refrigerant is discharged from the compressor 100 by the third direction switching valve 193, The refrigerant passes through the expansion line (R3) and the second expansion means (120) and is expanded and supplied to the outdoor heat exchanger (130).

The first bypass line R1 is installed to connect the inlet side refrigerant circulation line R of the first expansion means 140 and the outlet side refrigerant circulation line R of the evaporator 160 , And the refrigerant circulating through the refrigerant circulation line (R) selectively bypasses the first expansion means (140) and the evaporator (160).

As shown in the figure, the first bypass line R1 is disposed in parallel with the first expansion means 140 and the evaporator 160, that is, the inlet side of the first bypass line R1 is connected to the outdoor Is connected to the refrigerant circulation line R connecting the heat exchanger 130 and the first expansion means 140 and the outlet side is connected to the refrigerant circulation line R connecting the evaporator 160 and the compressor 100 .

The refrigerant that has passed through the outdoor heat exchanger 130 flows to the first expansion device 140 and the evaporator 160 in the air conditioner mode. However, in the heat pump mode (first heating mode) The refrigerant that has passed through the outdoor heat exchanger 130 flows directly to the compressor 100 side through the first bypass line R 1 and bypasses the first expansion means 140 and the evaporator 160.

Here, the function of switching the flow direction of the refrigerant according to the air conditioner mode and the heat pump mode is performed through the first direction switching valve 191.

The first direction switching valve 191 is installed at a branch point between the first bypass line Rl and the refrigerant circulation line R and is connected to the outdoor heat exchanger 130 according to an air conditioning mode or a heat pump mode. The refrigerant flow direction is switched so that the refrigerant passing through the first bypass line (R1) or the first expansion means (140) flows.

At this time, the first directional control valve 191 controls the refrigerant discharged from the compressor 100 in the air conditioning mode and passed through the indoor heat exchanger 110 and the outdoor heat exchanger 130 to flow through the first expansion means 140, The refrigerant discharged from the compressor 100 flows through the indoor heat exchanger 110 and the second expansion means 120 and the outdoor heat exchanger 120. In the heat pump mode, So that the refrigerant passing through the first bypass line (130) flows in the first bypass line (R1).

Meanwhile, the first directional control valve 191 is provided at a branch point on the inlet side of the first bypass line R1, and it is preferable to use a three-way valve.

It is preferable that not only the first direction switching valve 191 but also the second direction switching valve 192 and the third direction switching valve 193 use a three-way valve.

The second bypass line R2 is installed in parallel with the refrigerant circulation line R so that the refrigerant selectively passing through the second expansion means 120 bypasses the outdoor heat exchanger 130, That is, the second bypass line (R2) is provided to connect the inlet-outlet refrigerant circulation line (R) of the outdoor heat exchanger (130), so that the refrigerant circulating in the refrigerant circulation line (R) (130).

The refrigerant is circulated through the outdoor heat exchanger 130 or the second bypass line R2 at a branch point between the second bypass line R2 and the refrigerant circulation line R, A second direction switching valve 192 for switching the flow direction is provided.

At this time, when the outdoor temperature is an image, the refrigerant is controlled to flow to the outdoor heat exchanger 130 through the control of the second direction switching valve 192. When the outdoor temperature is zero, The refrigerant is controlled to flow to the second bypass line (R2) by bypassing the outdoor heat exchanger (130) through the control of the control unit (192).

In other words, in order to minimize the influence of the outdoor air at low temperature in the low-temperature source condition in which the outdoor temperature is below zero, the refrigerant passing through the second expansion means (120) (130) and flows to the second bypass line (R2) side.

An electric heater 115 is further installed on the downstream side of the indoor heat exchanger 110 in the air conditioning case 150 to improve the heating performance.

As the electric heater 115, a PTC heater is preferably used.

On the first bypass line R1, a heat supply means 180 for supplying heat to the refrigerant flowing along the first bypass line R1 is installed.

The heat supply unit 180 is connected to the first bypass line Rl so that waste heat of the vehicle electrical product 200 can be supplied to the refrigerant flowing through the first bypass line R1, And a cooling water heat exchanger 181b which is provided at one side of the refrigerant heat exchanger 181a and is capable of heat exchange and in which the cooling water circulating in the vehicle electrical appliance 200 flows, .

Therefore, the heating performance can be improved by recovering the heat source from the waste heat of the vehicle electrical equipment 200 in the heat pump mode.

On the other hand, the vehicle electrical equipment 200 is typically a motor, an inverter, or the like.

The inlet side first bypass line (R1) of the heat supply means (180) is connected to the evaporator (160) to supply a part of the refrigerant flowing toward the heat supply means (180) along the first bypass line (R1) Off valve 195 is provided on the branch line R4 for controlling the flow of the refrigerant on / off, and a branch line R4 for connecting the inlet side refrigerant circulation line R of the evaporator 160 .

The on-off valve 195 is opened in the dehumidifying mode when it is necessary to dehumidify the passenger compartment, so that a part of the refrigerant flowing toward the first bypass line (R1) by the first direction switching valve (191) The exhaust heat of the vehicle electrical component 200 is recovered while passing through the evaporator 160 through the branch line R4.

Accordingly, the air flowing inside the air conditioning case 150 is dehumidified while passing through the evaporator 160, that is, during the heat pump mode operation such as the first and second heating modes, the branch line R4 The evaporator 160 can supply a part of the refrigerant to perform the dehumidification in the passenger compartment.

Meanwhile, in the second heating mode in which the outdoor temperature is zero, the air inlet mode of the air conditioning case 150 is operated in the air inlet inflow mode so as to recover the heat source of the indoor air to improve the heating performance, It is preferable to allow the air to flow into the case 150.

An accumulator 170 is installed on the refrigerant circulation line R on the inlet side of the compressor 100.

The accumulator 170 separates the liquid refrigerant and the gaseous refrigerant from the refrigerant supplied to the compressor 100 so that only the gaseous refrigerant can be supplied to the compressor 100.

The control unit 300 controls the heat pump system according to the present invention. The control unit 300 receives various sensor values of the vehicle, calculates a target discharge temperature, and controls the heat pump system.

The various sensors include an outside air sensor, an inside air sensor, a radiation amount sensor, a vehicle speed sensor, an evaporator sensor, an air discharge temperature sensor, and a cooling water temperature sensor, and the sensed value from each sensor is transmitted to the controller 300.

Although it is described in the claims that the controller 300 receives various sensor values, it is preferable that the controller 300 receives not only actual sensor values but also various vehicle information and occupant selection values (set temperature, mode selection, etc.).

If the number of revolutions of the compressor 100 calculated according to the deviation between the target discharge temperature and the indoor air discharge temperature in the heat pump mode is smaller than the upper limit value of the maximum number of revolutions of the compressor 100, Variable control (automatic control) of the compressor 100 with the number of revolutions of the compressor 100,

When the rotation speed of the compressor 100 is equal to or greater than an upper limit value of the maximum rotation speed of the compressor 100 and the target discharge temperature is higher than the indoor air discharge temperature, Thereby controlling the operation of the heater 115.

The upper limit value of the maximum number of revolutions of the compressor 100 is determined based on the outside temperature, the refrigerant pressure, the vehicle speed, the blower 152 air volume, the cooling fan rotation number of the outdoor heat exchanger 130, Is the smallest upper limit value of the maximum number of revolutions of the compressor (100).

That is, the upper limit value of the maximum number of revolutions of the compressor 100 is not set as the upper limit value of the maximum number of revolutions of the compressor 100 for each factor but is set to the minimum value among the upper limit value of the maximum number of revolutions of the compressor 100 The operation noise of the compressor 100 can be reduced even when the maximum heating is required in the heat pump mode, thereby reducing the complaints of the occupant. In this case, the electric heating heater 115 is operated for the heating shortage.

If the upper limit of the maximum rotation speed of the compressor 100 is set to the minimum upper limit of the maximum rotation speed of the compressor 100 for each factor, the rotation speed of the compressor 100 is limited, The durability of the compressor 100 can be improved, and the stability of the heat pump system can be improved.

On the other hand, the refrigerant pressure is the discharge refrigerant pressure of the compressor (100).

The upper limit value of the maximum number of revolutions of the compressor 100 is calculated by the following equation.

An upper limit value of the maximum number of revolutions of the compressor 100 = Min (an upper limit value of the maximum number of revolutions of the compressor according to the ambient temperature, an upper limit value of the maximum number of revolutions of the compressor according to the refrigerant pressure, an upper limit value of the maximum number of revolutions of the compressor according to the vehicle speed, The upper limit value of the maximum number of revolutions, the upper limit value of the maximum number of revolutions of the compressor according to the number of revolutions of the cooling fan of the outdoor heat exchanger, and the upper limit value of the maximum number of revolutions of the compressor,

In the calculation of the upper limit value of the maximum number of revolutions of the compressor 100, the signal of the outdoor temperature, the refrigerant pressure, the vehicle speed, the blower 152 air volume, the cooling fan rotation number of the outdoor heat exchanger 130, The corresponding expression is excluded from the expression.

It is preferable that the control unit 300 maintains the number of revolutions of the compressor 100 at the upper limit of the maximum number of revolutions of the compressor 100 calculated when the compressor 100 is operated. That is, by differentiating the upper limit value of the maximum number of revolutions of the compressor 100 in accordance with the vehicle state (refrigerant pressure, vehicle speed, blower 152 air volume, cooling fan rotation number of the outdoor heat exchanger 130, It is possible to reduce complaints about the noise of the passenger due to the operation of the compressor 100 in the heat pump mode.

The controller 300 controls the compressor 100 only when the rotational speed of the compressor 100 is equal to or greater than the upper limit of the maximum rotational speed of the compressor 100 in the heat pump mode and the target discharge temperature is higher than the indoor air discharge temperature, The operation of the electric heater 115 is controlled in a state in which the rotational speed of the compressor 100 is maintained at the upper limit value of the maximum number of revolutions of the compressor 100. At this time, (Automatic control) of the electric heater 115 by calculating the calorific value of the electric heater 115 according to the deviation between the discharge temperature and the indoor air discharge temperature.

That is, by controlling the duty ratio of the voltage supplied to the electric heater 115, the amount of heat generated by the electric heater 115 can be variably controlled. At this time, when the condition for turning off the electric heater 115 is reached such that the target discharge temperature is reached through the control of the electric heater 115, only the electric heater 115 is turned off, After the compressor 115 is turned off, the number of rotations of the compressor 100 is variably controlled.

Meanwhile, in the air conditioning mode, the compressor 100 is controlled to be variable (automatically controlled) by calculating the number of rotations of the compressor 100 according to a deviation between the target temperature of the evaporator 160 and the temperature of the evaporator 160.

As described above, in the heat pump mode, the present invention controls the electric heater 115 to operate only when the rotational speed of the compressor 100 reaches the upper limit of the maximum rotational speed of the compressor 100, It is possible to solve the problem that the convergence of the indoor air discharge temperature of the vehicle, which occurs when the compressor 100 and the electric heater 115 are variably controlled at the same time, becomes unstable or unstable.

Hereinafter, the control method of the vehicular heat pump system will be described with reference to FIGS. 5 and 6. FIG.

First, a first step (S1) of receiving various sensor values of a vehicle and calculating a target discharge temperature is performed.

The various sensors include an outside air sensor, an inside air sensor, a radiation amount sensor, a vehicle speed sensor, an evaporator sensor, an air discharge temperature sensor, and a cooling water temperature sensor, and the sensed value from each sensor is transmitted to the controller 300.

At this time, it is preferable that the control unit 300 calculates the target discharge temperature after receiving not only actual sensor values such as the various sensors but also various vehicle information and occupant selection values (set temperature, mode selection, etc.) .

After the first step S1, a second step S2 is performed to determine whether the air conditioner mode or the heat pump mode is selected according to the target discharge temperature or the occupant selection.

As a result of the determination in the second step S2, if the mode is the heat pump mode, a third step S3 is performed to calculate a deviation between the target discharge temperature and the indoor air discharge temperature.

At this time, a temperature sensor (not shown) is installed at a discharge port formed inside the vehicle room to supply the air discharged from the air conditioning case 150 to the inside of the vehicle room to detect the air discharge temperature.

Subsequently, after the third step (S3), the fourth step (S4) of calculating the number of revolutions of the compressor (100) according to the deviation of the third step (S3)

A fifth step S5 of determining whether the number of revolutions of the compressor 100 is less than an upper limit value of the maximum number of revolutions of the compressor 100 after the fourth step S4 is performed.

The upper limit of the maximum number of revolutions of the compressor 100 is set to a minimum value among the upper limit of the maximum number of revolutions of the compressor 100 for various factors of the vehicle.

That is, the maximum value of the maximum number of revolutions of the compressor 100 is set to the minimum value among various factors detected from various sensors installed in the vehicle.

The factors include the vehicle noise factor and the protective factor of the heat pump system.

The noise generation factors of the vehicle include a vehicle speed, a blower 152 air volume, a cooling fan rotation number of the outdoor heat exchanger 130, and a travel drive source on / off.

That is, when the vehicle speed, the blower 152 air volume, the cooling fan rotation speed, or the traveling driving source is on, the operating noise of the compressor 100 is relatively small due to the noise of the factors, However,

When the vehicle speed, the blower 152 air volume, the cooling fan rotation speed are low, or the travel driving source is in the off state, the operation noise of the compressor 100 is relatively louder than the noise of the factors, have.

Therefore, by setting the upper limit value of the maximum number of revolutions of the compressor 100 to the minimum value of the maximum number of revolutions of the compressor 100 according to the noise generation factor of the vehicle, it is possible to reduce the operating noise of the compressor 100, will be.

On the other hand, as a protective factor of the heat pump system, there are outside temperature, refrigerant pressure (discharge refrigerant pressure of the compressor).

As described above, the upper limit value of the maximum number of revolutions of the compressor 100 depends on the outside air temperature, the refrigerant pressure, the vehicle speed, the blower 152 air volume, the cooling fan rotation number of the outdoor heat exchanger 130, And is the minimum value among the upper limit values of the maximum number of revolutions of the compressor 100 for each factor.

That is, by setting the upper limit value of the maximum number of revolutions of the compressor 100 not to the upper limit value of the maximum number of revolutions of the compressor 100 for each factor but to the minimum value of the maximum number of revolutions of the compressor 100 for each factor, Even in the case where the maximum heating is required in the heat pump mode, the number of revolutions of the compressor 100 is limited to reduce the operating noise of the compressor 100 and improve durability, thereby reducing the complaints of the occupant. The heating shortage at this time is operated by the electric heater 115 in a step to be described later.

On the other hand, the upper limit value of the maximum number of revolutions of the compressor 100 is calculated by the following equation.

An upper limit value of the maximum number of revolutions of the compressor 100 = Min (an upper limit value of the maximum number of revolutions of the compressor according to the ambient temperature, an upper limit value of the maximum number of revolutions of the compressor according to the refrigerant pressure, an upper limit value of the maximum number of revolutions of the compressor according to the vehicle speed, The upper limit value of the maximum number of revolutions, the upper limit value of the maximum number of revolutions of the compressor according to the number of revolutions of the cooling fan of the outdoor heat exchanger, and the upper limit value of the maximum number of revolutions of the compressor,

In the calculation of the upper limit value of the maximum number of revolutions of the compressor 100, the signal of the outdoor temperature, the refrigerant pressure, the vehicle speed, the blower 152 air volume, the cooling fan rotation number of the outdoor heat exchanger 130, The corresponding expression is excluded from the expression.

If it is determined that the number of revolutions of the compressor 100 is less than the upper limit value of the maximum number of revolutions of the compressor 100 as a result of the fifth step S5, (Automatic control) of the compressor 100 with the number of revolutions of the compressor 100 (step S6).

That is, under the condition that it is not necessary to operate the compressor 100 at the maximum rotation speed of the compressor 100 at the time of the heat pump mode, rotation of the compressor 100 according to the deviation between the target discharge temperature and the air discharge temperature Only the compressor 100 is subjected to variable control (automatic control) to be heated, and the electric heater 115 is not operated.

If it is determined in step S5 that the number of revolutions of the compressor 100 is not less than the upper limit of the maximum number of revolutions of the compressor 100, that is, if the number of revolutions of the compressor 100 is equal to the upper limit of the maximum number of revolutions of the compressor 100 If it is determined that the target discharge temperature is higher than the indoor air discharge temperature, a seventh step S7 is performed.

In the seventh step S7, it is determined whether the target discharge temperature is higher than the indoor air discharge temperature. At this time, it may be determined whether the target discharge temperature is higher than the air discharge temperature plus a predetermined value.

If the target discharge temperature is higher than the indoor air discharge temperature as a result of the seventh step S7, the operation of the electric heater 115 is controlled in a state where the operation of the compressor 100 is maintained S8).

That is, in the heat pump mode, only when the number of revolutions of the compressor 100 reaches the upper limit of the maximum number of revolutions of the compressor 100, the electric heater 115 is operated to be automatically controlled.

At this time, it is preferable that the rotation speed of the compressor 100 is maintained at the upper limit of the maximum rotation speed of the compressor 100 when the compressor 100 is operated.

6, the operation control of the electric heater 115 of the eighth step S8 will be described in detail. When the operation of the electric heater 115 is controlled, the number of rotations of the compressor 100 (S8-1) of maintaining the compressor 100 at the upper limit of the maximum number of revolutions.

That is, the operation of the compressor (100) is continuously operated at the upper limit of the maximum number of revolutions of the compressor (100) calculated above.

After the step 8-1 (S8-1), the heating value of the electric heater 115 is calculated according to the deviation between the target discharge temperature and the indoor air discharge temperature, and the electric heater 115 is changed Step 8-2 (S8-2) of control (automatic control) is performed.

That is, by controlling the duty ratio of the voltage supplied to the electric heater 115, the amount of heat generated by the electric heater 115 can be variably controlled.

Subsequently, after the above-mentioned step 8-2 (S8-2), the program proceeds to step 8-3 in which it is determined whether or not the electric heater 115 is to be turned off.

That is, it is determined whether or not the condition for turning off the electric heater 115 is reached, such as reaching the target discharge temperature through the variable control (automatic control) of the electric heater 115.

If it is determined that the electric heater 115 is to be turned off as a result of the determination in the step 8-3 (S8-3), the operation goes to the step 8-4 (S8-4) in which only the electric heater 115 is turned off do.

After the electric heater 115 is turned off in step S8-4, the rotational speed of the compressor 100 is variably controlled.

After the step 8-4 (S8-4), the process returns to the starting position of FIG.

On the other hand, if it is determined in the seventh step S7 that the target discharge temperature is not higher than the indoor air discharge temperature, the electric heater 115 is kept in the off state.

If it is determined in the second step S2 that the air conditioner mode is selected, the process proceeds to the ninth step S9 of calculating the target temperature of the evaporator 160,

After the ninth step S9, a tenth step S10 is performed to calculate the deviation between the target temperature of the evaporator 160 and the temperature of the evaporator 160. [

The temperature of the evaporator 160 is sensed by installing a temperature sensor on the evaporator 160 side.

After the tenth step S10, an eleventh step S11 is performed to variably control (automatically control) the compressor 100 by calculating the number of rotations of the compressor 100 according to the deviation of the tenth step S10 Go ahead.

Hereinafter, the operation of the vehicle heat pump system according to the present invention will be described, and only the air conditioning mode and the first and second heating modes of the heat pump mode will be described for convenience.

end. Air conditioning mode (cooling mode) (Fig. 2)

In the air conditioning mode (cooling mode), as shown in FIG. 2, the first bypass line R1 is closed through the first direction switching valve 191, and the first bypass line R1 is closed through the second direction switching valve 192 The second bypass line R2 is also closed, and the third direction switching valve 193 closes the expansion line R3.

The cooling water circulating through the electrical component 200 is not supplied to the water-cooled heat exchanger 181 of the heat supply unit 180.

On the other hand, at the time of maximum cooling, the temperature control door 151 in the air conditioning case 150 is operated to close the passage through the indoor heat exchanger 110, so that the air blown into the air conditioning case 150 by the blower Is cooled while passing through the evaporator (160), and is then supplied to the interior of the vehicle by bypassing the indoor heat exchanger (110), thereby cooling the interior of the vehicle.

Next, the refrigerant circulation process will be described.

The high-temperature, high-pressure gaseous refrigerant discharged from the compressor 100 after being compressed is supplied to the indoor heat exchanger 110 installed in the air conditioning case 150.

The refrigerant supplied to the indoor heat exchanger 110 is supplied to the outdoor heat exchanger 130 without heat exchange with air because the temperature control door 151 closes the passage on the indoor heat exchanger 110 as shown in FIG. .

The refrigerant flowing into the outdoor heat exchanger 130 is condensed while exchanging heat with the outdoor air, thereby changing the gaseous refrigerant into the liquid refrigerant.

Meanwhile, both the indoor heat exchanger 110 and the outdoor heat exchanger 130 perform the condenser dynamics, but the refrigerant is mainly condensed in the outdoor heat exchanger 130 that performs heat exchange with the outdoor air.

Subsequently, the refrigerant passing through the outdoor heat exchanger 130 is decompressed and expanded in the process of passing through the first expansion means 140 to be a low-temperature low-pressure liquid-phase refrigerant, and then flows into the evaporator 160.

The refrigerant flowing into the evaporator 160 is heat-exchanged with the air blown into the air conditioning case 150 through the blower to evaporate, and at the same time, the air is cooled by an endothermic effect due to the latent heat of evaporation of the refrigerant. And supplied to the vehicle interior to be cooled.

Then, the refrigerant discharged from the evaporator 160 flows into the compressor 100 and recycles the cycle as described above.

I. In the first heating mode (Fig. 3) of the heat pump mode,

The first heating mode of the heat pump mode operates under the condition that the outdoor temperature is an image and uses the outdoor air and the waste heat of the vehicle electrical equipment 200 as a heat source. The first bypass line R1 is opened and the refrigerant is not supplied to the first expansion means 140 and the evaporator 160 side.

The second bypass line R2 is closed through the second direction switching valve 192 and the expansion line R3 is opened through the third direction switching valve 193.

On the other hand, the cooling water heated by the vehicle electrical component 200 is supplied to the cooling water heat exchanger 181b of the water-cooled heat exchanger 181 serving as the heat supply means 180.

In the first heating mode, the temperature control door 151 in the air conditioning case 150 is operated to close the passage bypassing the indoor heat exchanger 110, and is blown into the air conditioning case 150 by the blower Air passes through the evaporator 160 (operation stop), passes through the indoor heat exchanger 110, and is converted into hot air to be supplied to the interior of the vehicle, thereby heating the interior of the vehicle.

Next, the refrigerant circulation process will be described.

The high-temperature, high-pressure gaseous refrigerant discharged from the compressor 100 after being compressed is introduced into the indoor heat exchanger 110 installed inside the air conditioning case 150.

The high-temperature, high-pressure gaseous refrigerant introduced into the indoor heat exchanger 110 is condensed while exchanging heat with the air blown into the air conditioning case 150 through the blower. At this time, air passing through the indoor heat exchanger 110 After changing to hot air, it is supplied to the interior of the vehicle, and the interior of the vehicle is heated.

Subsequently, the refrigerant discharged from the indoor heat exchanger 110 flows into the expansion line R3 through the third direction switching valve 193, and the refrigerant flowing into the expansion line R3 flows through the second Pressure low-temperature liquid refrigerant in the process of passing through the expansion means 120, and then supplied to the outdoor heat exchanger 130 serving as an evaporator.

The refrigerant supplied to the outdoor heat exchanger 130 is evaporated while exchanging heat with the outdoor air and then passed through the first bypass line R1 by the first direction switching valve 191. At this time, The refrigerant passing through the pass line R1 is heat-exchanged with the cooling water passing through the cooling water heat exchanging part 181b in the process of passing through the refrigerant heat exchanging part 181a of the water-cooling type heat exchanger 181, And then recycles the cycle as described above while flowing into the compressor 100.

All. In the second heating mode (Fig. 4) of the heat pump mode,

The second heating mode of the heat pump mode operates under the condition that the outdoor temperature is below zero and uses the indoor air (inflow inflow mode) and the waste heat of the vehicle electrical equipment 200 as a heat source. The first bypass line R1 is opened through the direction switching valve 191 and the second bypass line R2 is opened through the second direction switching valve 192. [

Further, the branch line R4 is closed through the on-off valve 195, the expansion line R3 is opened through the third direction switching valve 193, Into the inflow inflow mode.

On the other hand, the cooling water heated by the vehicle electrical component 200 is supplied to the cooling water heat exchanger 181b of the water-cooled heat exchanger 181 serving as the heat supply means 180.

In the second heating mode, the temperature control door 151 in the air conditioning case 150 is operated to close the passage bypassing the indoor heat exchanger 110, so that air is blown into the air conditioning case 150 by the blower Air passes through the evaporator 160 (operation stop), passes through the indoor heat exchanger 110, and is converted into hot air to be supplied to the interior of the vehicle, thereby heating the interior of the vehicle.

Next, the refrigerant circulation process will be described.

The high-temperature, high-pressure gaseous refrigerant discharged from the compressor 100 after being compressed is introduced into the indoor heat exchanger 110 installed inside the air conditioning case 150.

The high-temperature, high-pressure gaseous refrigerant introduced into the indoor heat exchanger 110 is condensed while exchanging heat with the air blown into the air conditioning case 150 through the blower. At this time, air passing through the indoor heat exchanger 110 After changing to hot air, it is supplied to the interior of the vehicle, and the interior of the vehicle is heated.

Subsequently, the refrigerant discharged from the indoor heat exchanger 110 flows into the expansion line R3 through the third direction switching valve 193, and the refrigerant flowing into the expansion line R3 flows through the second The refrigerant flows to the second bypass line (R2) and bypasses the outdoor heat exchanger (130). The liquid refrigerant flows through the second bypass line (R2).

Then, the refrigerant having passed through the second bypass line R2 passes through the first bypass line R1 by the first direction switching valve 191. At this time, the first bypass line R1 Is heat-exchanged with the cooling water passing through the cooling water heat exchanging part 181b in the course of passing through the refrigerant heat exchanging part 181a of the water-cooling type heat exchanger 181 to recover the waste heat of the vehicle electrical equipment 200 , And recycles the cycle as described above while flowing into the compressor (100).

100: compressor 110: indoor heat exchanger
115: Electric heater
120: second expansion means 121: orifice
130: outdoor heat exchanger 140: first expansion means
150: air conditioning case 151: temperature control door
152: Blower
160: Evaporator 170: Accumulator
180: Heat supply unit 181: Water-cooled heat exchanger
181a: refrigerant heat exchanger 181b: cooling water heat exchanger
191: first direction switching valve 192: second direction switching valve
193: Third direction switching valve 195: Flow control valve
200: electrical equipment 300:
R: refrigerant circulation line R1: first bypass line
R2: second bypass line R3: inflation line
R4: Branch line

Claims (14)

A control method for a vehicle heat pump system,
A first step (S1) of receiving various sensor values of the vehicle and calculating a target discharge temperature,
A second step S2 of determining whether the air conditioner mode or the heat pump mode is selected according to the target discharge temperature or the occupant selection after the first step S1;
A third step (S3) of calculating a deviation between the target discharge temperature and the indoor air discharge temperature in the heat pump mode as a result of the determination in the second step (S2)
A fourth step (S4) of calculating the number of rotations of the compressor (100) according to the deviation of the third step (S3) after the third step (S3)
A fifth step S5 of determining whether the number of revolutions of the compressor 100 is less than an upper limit value of the maximum number of revolutions of the compressor 100 after the fourth step S4,
If the number of rotations of the compressor 100 is smaller than the upper limit of the maximum number of rotations of the compressor 100 as a result of the fifth step S5, A sixth step (S6) of variably controlling the compressor (100)
A seventh step of determining whether the target discharge temperature is higher than the indoor air discharge temperature if the number of revolutions of the compressor 100 is not less than the upper limit value of the maximum number of revolutions of the compressor 100 as a result of the fifth step S5 S7)
If the target discharge temperature is higher than the indoor air discharge temperature as a result of the seventh step S7, the operation of the electric heater 115 is controlled in a state where the operation of the compressor 100 is maintained (S8). ≪ / RTI > The method according to claim 1,
Wherein the upper limit of the maximum number of revolutions of the compressor (100) is a minimum value of the maximum number of revolutions of the compressor (100) for each noise generation factor of the vehicle. The method according to claim 1,
Wherein the upper limit value of the maximum number of revolutions of the compressor (100) is a minimum value of an upper limit value of the maximum number of revolutions of the compressor (100) for each protection factor of the heat pump system. 3. The method of claim 2,
Wherein the noise generation factor of the vehicle is a vehicle speed, a blower air volume, a cooling fan rotation number of the outdoor heat exchanger (130), and a traveling drive source on / off. The method of claim 3,
Wherein the protection factor of the heat pump system is an outdoor temperature and a refrigerant pressure. The method according to claim 1,
The upper limit value of the maximum number of revolutions of the compressor 100 is the maximum rotation number of the compressor 100 for each factor according to the outside air temperature, the refrigerant pressure, the vehicle speed, the blower air volume, the cooling fan rotation number of the outdoor heat exchanger, Wherein the maximum value of the upper limit of the number of the heat pumps is a minimum value. The method according to claim 1,
The control method for a vehicle heat pump system according to claim 1, wherein the eighth step (S8) maintains the rotational speed of the compressor (100) at an upper limit of a maximum rotational speed of the compressor (100) . The method according to claim 1,
In the operation control of the electric heater 115 in the eighth step S8,
An eighth step (S8-1) of maintaining the number of revolutions of the compressor (100) at an upper limit value of the maximum number of revolutions of the compressor (100)
After the step 8-1 (S8-1), the amount of heat generated by the electric heater 115 according to the deviation between the target discharge temperature and the indoor air discharge temperature is calculated and the electric heater 115 is subjected to variable control (S8-2) for determining whether or not the heat pump system is in operation. 9. The method of claim 8,
An eighth step (S8-3) of judging whether or not the electric heater 115 is to be turned off after the step 8-2 (S8-2)
If it is determined in step 8-3 that the electric heater 115 is to be turned off as a result of the determination in step 8-3, step 8-4 of turning off only the electric heater And controlling the temperature of the heat pump. The method according to claim 1,
A ninth step S9 of calculating a target temperature of the evaporator 160 if the air conditioning mode is determined as a result of the second step S2,
A tenth step (S10) of calculating a deviation between the target temperature of the evaporator (160) and the temperature of the evaporator (160) after the ninth step (S9)
The method may further include an eleventh step (S11) of calculating the number of rotations of the compressor (100) according to the deviation of the tenth step (S10) after the 10th step (S10) to variably control the compressor Wherein the heat pump system comprises: A compressor 100 connected to the refrigerant circulation line R to compress and discharge the refrigerant, an evaporator 160 and an indoor heat exchanger 110 disposed inside the air conditioning case 150, And an outdoor heat exchanger (130) disposed outside the outdoor heat exchanger (150), wherein an electric heater (115) is provided inside the air conditioning case,
And a control unit (300) for receiving various sensor values of the vehicle and calculating a target discharge temperature to control the heat pump system,
If the number of revolutions of the compressor 100 calculated according to the deviation between the target discharge temperature and the indoor air discharge temperature in the heat pump mode is smaller than the upper limit value of the maximum number of revolutions of the compressor 100, Variable control of the compressor 100 with the number of revolutions of the compressor 100,
When the rotation speed of the compressor 100 is equal to or greater than an upper limit value of the maximum rotation speed of the compressor 100 and the target discharge temperature is higher than the indoor air discharge temperature, And controls operation of the heater (115). 12. The method of claim 11,
The upper limit value of the maximum number of revolutions of the compressor 100 is the maximum rotation number of the compressor 100 for each factor according to the outside air temperature, the refrigerant pressure, the vehicle speed, the blower air volume, the cooling fan rotation number of the outdoor heat exchanger, And the minimum value of the upper limit of the number of the heat pumps. 12. The method of claim 11,
Wherein the controller (300) maintains the rotational speed of the compressor (100) at an upper limit of a maximum rotational speed of the compressor (100) when the compressor (100) is operated. 12. The method of claim 11,
The control unit 300 may control the operation of the electric heating type heater 115 such that the target discharge temperature is lower than the maximum dischargeable temperature of the compressor 100, And the electric heating heater (115) is variably controlled by calculating the heat generation amount of the electric heater (115) according to the temperature deviation.

Images