Control system for air-conditioning a vehicle

Patent metadata

Field	Value
Publication number	US-10773570-B2
Application number	US-201815868381-A
Country	US
Kind code	B2
Filing date	Jan 11, 2018
Priority date	Sep 30, 2015
Publication date	Sep 15, 2020
Grant date	Sep 15, 2020

Abstract

A control system method is disclosed for air-conditioning a vehicle by a heat pump system, wherein one of multiple operating modes is automatically set, depending on the air-conditioning requirement. The passenger space is cooled by an air-conditioning evaporator and/or is heated by a heating heat exchanger. The heating heat exchanger is arranged in a heating branch of a coolant circuit and is provided with heat via a heat pump. If cooling is required, the heating branch is opened and the heating pump is deactivated. If heating is required, the heating branch is closed and heat is fed to the heating heat exchanger via the heat pump. In order to remove heat from the heating branch, same is opened and a low-temperature cooler, the condenser and the heating heat exchanger are operated connected in series.

First claim

What is claimed is:

1. A method of operating a control system for air-conditioning a vehicle, the method comprising the steps of:
automatically setting one of several operating modes in a manner dependent on an air-conditioning demand for a passenger compartment of the vehicle;
cooling the passenger compartment by an air-conditioning evaporator in response to the air-conditioning demand comprising a cooling or dehumidification demand;
heating the passenger compartment by a heating heat exchanger in response to the air-conditioning demand comprising a heating demand, wherein the heating heat exchanger is arranged in a heating branch of a coolant circuit, wherein the heating heat exchanger is supplied with heated coolant via a heat pump, and wherein the heating branch has a chiller and a condenser which are both connected to a refrigeration circuit, and wherein the chiller is arranged in a cooling branch of the coolant circuit and the condenser is arranged in the heating branch;
operating the heating branch and deactivating the chiller of the heat pump, to achieve a cooling mode, in response to a cooling demand without an additional heating demand;
closing the heating branch such that heat is supplied to the heating heat exchanger by: the condenser of the heat pump, the cooling branch and/or absorption of heat by a low-temperature cooler, to achieve a heating mode; and
dissipating heat from the heating branch by opening the heating branch, and operating the low-temperature cooler, the condenser and the heating heat exchanger in a manner connected in series.

2. The method as claimed in claim 1 , wherein
proceeding from the heating mode, a first mixed mode is set by the air-conditioning evaporator being activated,
proceeding from the first mixed mode, a second mixed mode is set by the heating power being reduced by an expansion valve, which is connected upstream of the chiller in the refrigeration circuit, being throttled down,
proceeding from the second mixed mode, a third mixed mode is set by the heating branch being operated in clocked fashion,
proceeding from the third mixed mode, the cooling mode is set by the heating branch being opened and maintained as opened while the third mixed mode is set.

3. The method as claimed in claim 1 , wherein said control system regulates a power of a compressor and has a first regulator and a second regulator that regulate the power of the compressor, by which a compressor rotational speed of the compressor is set, wherein the respectively set compressor rotational speed serves as a first control variable for the first regulator and as a second control variable for the second regulator, wherein only one of the two regulators and the control variable thereof are selected, in a manner dependent on the air-conditioning demand, for the regulation of the compressor.

4. The method as claimed in claim 3 , wherein in the heating mode, the compressor is regulated by the first regulator, wherein a heating branch actual temperature is used as a regulating variable, and a heating branch setpoint temperature is used as a reference variable.

5. The method as claimed in claim 3 , wherein in response to the cooling demand, the compressor is regulated by the second regulator in a manner dependent on an evaporator actual temperature as a regulating variable, and an evaporator setpoint temperature is used as reference variable.

6. The method as claimed in claim 3 , wherein said control system has a third regulator, by which the compressor is regulated based on a coolant actual temperature as a regulating variable, and a minimum coolant temperature as a reference variable, being supplied to the third regulator, and wherein the third regulator regulates the power of the compressor, by which the compressor rotational speed of the compressor is set, the set compressor rotational speed serving as a third control variable.

7. The method as claimed in claim 6 , wherein said control system selects one control variable out of the first control variable and a third control variable by a comparator, wherein the comparator performs a comparison and selects the lower of the first control variable and the third control variable for the regulation of the compressor.

8. The method as claimed in claim 7 , wherein said control system has a superheating regulator, by which a degree of superheating of the refrigerant is set through regulation of an expansion valve which is arranged upstream of the chiller and which has an opening which serves as a manipulated variable of the superheating regulator, wherein the degree of superheating serves as a regulating variable of the superheating regulator and a setpoint degree of superheating serves as a reference variable, which is determined in a manner dependent on the air-conditioning demand.

9. The method as claimed in claim 8 , wherein for a first mixed mode, the setpoint degree of superheating is set to be lower than in the heating mode.

10. The method as claimed in claim 9 , wherein the manipulated variable of the fourth regulator is influenced by an additional throttling-down factor, which reflects a throttling down of the expansion valve, thereby reducing the amount of heat transferred by the heat pump.

11. The method as claimed in claim 9 , wherein a reduction of the absorption of heat is achieved via the setpoint degree of superheating being modified with an additional throttling-down supplement.

12. The method as claimed in claim 11 , wherein in the case of a reduction of the control variable by the throttling-down factor, an I component of the superheating regulator is stopped.

13. The method as claimed in claim 12 , wherein, in response to a limit value for the throttling-down factor being reached, the expansion valve is fully closed, and a third mixed mode is automatically set via the heating branch being operated in a clocked fashion.

14. The method as claimed in claim 8 , wherein upon shut-down of the vehicle or in response to both the chiller and the air-conditioning evaporator being active, a minimum degree of opening is predefined for the expansion valve upstream of the chiller, which minimum degree of opening limits the manipulated variable of the superheating regulator.

15. The method as claimed in claim 13 , wherein said control system opens and closes the heating branch by a shut-off valve, wherein, for the opening of the heating branch, the shut-off valve is opened, for the closure of the heating branch, the shut-off valve is closed, and the third mixed mode is set via the shut-off valve being periodically opened and closed.

16. The method as claimed in claim 1 , wherein said control system sets a low-temperature heating configuration via the heat pump being deactivated and waste heat of a vehicle component which is connected to the cooling branch being used for heating purposes.

17. The method as claimed in claim 16 , wherein the low-temperature heating configuration is activated only in response to a heating branch setpoint temperature being lower than a coolant actual temperature and not lower than a heating branch actual temperature.

18. The method as claimed in claim 1 , wherein said control system sets a heat store configuration via the coolant being conducted past the low-temperature cooler via a low-temperature cooler bypass.

19. The method as claimed in claim 18 , wherein the heat store configuration is automatically set in response to a coolant actual temperature being higher than an outside temperature and the coolant actual temperature being lower than a maximum coolant

Assignees

• Bayerische Motoren Werke Ag

Inventors

• Herbolzheimer Robert
• Horn Oliver
• Oswald Patrick

Classifications

• B60H1/00899 Primary

  Controlling the flow of liquid in a heat pump system (controlling the properties of the refrigerant liquid, e.g. pressure or temperature, B60H1/3204) · CPC title

• B60H2001/3272

  to control the revolving speed of a compressor · CPC title

• B60H1/00007

  Combined heating, ventilating, or cooling devices (control systems or mechanisms B60H1/00642) · CPC title

• B60H1/32284

  comprising two or more secondary circuits, e.g. at evaporator and condenser side · CPC title

• B60H1/3213

  for increasing the efficiency in a vehicle heat pump · CPC title