Cold and hot dual-acting air conditioning system with dual diesel-electric power

Abstract

The disclosed dual-acting air conditioning system with diesel-electric dual power supply comprises an evaporator, a first heat source, a second heat source, a heat source switching valve group, a refrigeration module, a first hydraulic drive source, a second hydraulic drive source and a hydraulic control valve. The heat source coil and the cold source coil are installed in a serpentine shape on the evaporator. The heat source switching valve group can selectively connect the first heat source or the second heat source to the heat source coil. The refrigeration module comprises a hydraulic motor and a compressor. The output shaft of the hydraulic motor is in transmission connection with the power input shaft of the compressor. The refrigerant outlet and the refrigerant inlet of the compressor are in communication with the cold source coil inlet and the cold source coil outlet of the cold source coil through the condenser. The first hydraulic drive source and the second hydraulic drive source are connected with the drive oil circuit of the hydraulic motor through the hydraulic control valve. The present application can realize dual-acting refrigeration and heating in two power modes of diesel engine driving and three-phase motor driving.

Description

Technical Field

[0001] This invention relates to the field of mining auxiliary equipment technology, and in particular to a dual-power (diesel and electric) air conditioning system for both cooling and heating. Background Technology

[0002] With the continuous increase in infrastructure construction such as highways, railways, subways, and urban underground utility tunnels, the number of tunnel and large underground space construction projects is increasing. Influenced by national environmental protection policies and sustainable development requirements, open-pit mines are also gradually shifting to underground mining. At the same time, due to strict limitations on safety risks, construction period, and support requirements, the demand for underground tunnels and mining equipment is increasing year by year, and the demand for comfortable equipment operation is also becoming increasingly strong.

[0003] Due to the special nature of underground construction equipment, prolonged use of diesel engines as the driving force in underground tunnels would produce excessive amounts of toxic gases, posing a threat to the personal safety of construction workers. Therefore, underground construction equipment mostly adopts a dual-power system of diesel and electric, where a diesel engine provides the driving force for movement, and a three-phase motor provides the working power. The air conditioning systems currently equipped with underground construction equipment mainly fall into two categories:

[0004] The first type of air conditioning system uses a diesel engine or a three-phase electric hydraulic system to drive the air conditioning compressor, providing cooling; heating depends on the engine's water circulation. The drawback of this system is that it cannot provide heating when the equipment operates for extended periods on three-phase power, making it unsuitable for low-temperature environments, such as winter construction or operations in cold regions.

[0005] The second type of air conditioning system is powered by three-phase electricity, obtaining 220V AC power through a transformer, and uses a household air conditioner for cooling and heating. The drawbacks of this system are: when the equipment is driven by a diesel engine, the household air conditioner cannot work, and the cab has no ability to regulate temperature; in addition, the air in the underground tunnels is dusty and highly corrosive, making the household air conditioner unsuitable and resulting in a high failure rate.

[0006] To address the aforementioned issues, the conventional approach for end customers is to purchase small electric heaters and install transformers (such as converting 380V AC to 220V AC) to provide temporary heating. However, this solution constitutes unauthorized modification, poses serious safety hazards, and fails to provide cooling. Summary of the Invention

[0007] The purpose of this invention is to provide a dual-power (diesel and electric) air conditioning system for both cooling and heating, in order to solve the technical problems in existing underground construction equipment where diesel engines cannot provide cooling and heating when driving, three-phase motors cannot provide heating when driving, and household air conditioning retrofit solutions are completely ineffective in diesel engine mode, with poor applicability and safety hazards.

[0008] To achieve the above objectives, the present invention adopts the following technical solution:

[0009] The dual-power (diesel and electric) air conditioning system includes:

[0010] An evaporator, on which heat source coils and cold source coils are installed in a serpentine pattern;

[0011] A first heat source, a second heat source, and a heat source switching valve assembly. Both the first heat source and the second heat source provide heat to the heat source coil. The first heat source and the second heat source are circulatedly connected to the heat source coil through the heat source switching valve assembly. The heat source switching valve assembly can selectively connect the first heat source or the second heat source to the heat source coil.

[0012] The refrigeration module includes a hydraulic motor and a compressor. The output shaft of the hydraulic motor is connected to the power input shaft of the compressor. The refrigerant outlet and refrigerant inlet of the compressor are connected to the inlet and outlet of the cold source coil through the condenser.

[0013] The system comprises a first hydraulic drive source, a second hydraulic drive source, and a hydraulic control valve. Both the first and second hydraulic drive sources are capable of providing hydraulic driving force to the hydraulic motor. The first and second hydraulic drive sources are connected to the drive oil circuit of the hydraulic motor through the hydraulic control valve.

[0014] As a further embodiment of the present invention, the heat source switching valve group includes a heat source delivery assembly, which includes a main inlet pipe. One end of the main inlet pipe is connected to the inlet of the heat source coil in the heat source coil, and the other end of the main inlet pipe is connected to a second three-way valve. One outlet of the second three-way valve is connected to a fifth connecting pipe, and a third electric valve is installed on the fifth connecting pipe. The other outlet of the second three-way valve is connected to a sixth connecting pipe, and a fourth electric valve is installed on the sixth connecting pipe.

[0015] As a further embodiment of the present invention, the heat source switching valve group further includes a return liquid assembly, which includes a main return liquid pipe. One end of the main return liquid pipe is connected to the outlet of the heat source coil in the heat source coil, and the other end of the main return liquid pipe is connected to a first tee. One outlet of the first tee is connected to a third connecting pipe, and a second electric valve is installed on the third connecting pipe. The other outlet of the first tee is connected to a first connecting pipe, and a first electric valve is installed on the first connecting pipe.

[0016] As a further embodiment of the present invention, the first heat source includes a diesel engine cylinder liner, which stores antifreeze. The outlet of the diesel engine cylinder liner is connected to the inlet of a third electric valve, and the return port of the diesel engine cylinder liner is connected to the outlet of a second electric valve through a fourth connecting pipe.

[0017] As a further preferred embodiment of the present invention, the second heat source includes a water tank, a water pump, and a PTC heater. The water tank stores antifreeze. The outlet of the water tank is connected to the inlet of the water pump. The outlet of the water pump is connected to the inlet of the PTC heater. The outlet of the PTC heater is connected to the inlet of the fourth electric valve through a seventh connecting pipe. The return port of the water tank is connected to the outlet of the first electric valve through a second connecting pipe.

[0018] As a preferred embodiment of the present invention, the first hydraulic drive source includes a diesel engine and a first hydraulic pump. The power output shaft of the diesel engine is connected to the power input shaft of the first hydraulic pump. The inlet of the first hydraulic pump is connected to the outlet of the hydraulic oil tank. The outlet of the first hydraulic pump is connected to a first hydraulic delivery pipe.

[0019] As a further embodiment of the present invention, the second hydraulic drive source includes an electric motor and a second hydraulic pump. The power output shaft of the electric motor is connected to the power input shaft of the second hydraulic pump. The inlet of the second hydraulic pump is connected to the outlet of the hydraulic oil tank. The outlet of the second hydraulic pump is connected to a second hydraulic delivery pipe.

[0020] As a further embodiment of the present invention, the hydraulic control valve is a two-position four-way solenoid valve. The outlet of the first hydraulic delivery pipe and the outlet of the second hydraulic delivery pipe are both connected to the P port of the hydraulic control valve. The A port of the hydraulic control valve is connected to the oil inlet of the hydraulic motor. The B port of the hydraulic control valve is connected to the oil return port of the hydraulic motor. The T port of the hydraulic control valve is connected to the oil return port of the hydraulic oil tank.

[0021] As a further embodiment of the present invention, a first check valve is installed on the first hydraulic delivery pipe, and a second check valve is installed on the second hydraulic delivery pipe.

[0022] As a preferred embodiment of the present invention, the refrigerant outlet of the compressor is connected to the inlet of the condenser through the tenth connecting pipe; the outlet of the condenser is connected to the inlet of the cold source coil through the ninth connecting pipe.

[0023] The outlet of the cold source coil is connected to the refrigerant inlet of the compressor via the eighth connecting pipe, and an expansion valve is installed on the ninth connecting pipe.

[0024] Compared with the prior art, the present invention has the following beneficial effects:

[0025] This invention can achieve both cooling and heating functions in both diesel engine-driven walking and three-phase motor-driven working modes, solving the problem that existing underground construction equipment cannot provide cooling and heating functions simultaneously in a single power mode. It significantly improves the comfort of the cab and is suitable for construction in all seasons and cold regions. Attached Figure Description

[0026] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only examples of embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is a schematic diagram of the connection structure between the evaporator and the first heat source and the second heat source in an embodiment of the present invention;

[0028] Figure 2 This is a schematic diagram of the connection structure between the evaporator and the compressor in an embodiment of the present invention;

[0029] Figure 3 This is a schematic diagram of the hydraulic pipeline structure connecting the first hydraulic drive source, the second hydraulic drive source, and the hydraulic motor in an embodiment of the present invention.

[0030] Figure label:

[0031] 100. Evaporator; 1011. Heat source coil inlet; 1012. Heat source coil outlet; 1013. Cold source coil inlet; 1014. Cold source coil outlet; 200. Second heat source; 201. Water pump; 202. PTC heater; 300. Main liquid inlet pipe; 301. Main liquid return pipe; 302. First tee; 303. First connecting pipe; 304. First electric valve; 305. Second connecting pipe; 306. Third connecting pipe; 307. Second electric valve; 308. Fourth connecting pipe; 309. Second tee; 310. Fifth connecting pipe; 311. 312. Third electric valve; 313. Sixth connecting pipe; 314. Fourth electric valve; 315. Seventh connecting pipe; 400. Diesel engine; 401. First hydraulic pump; 402. First check valve; 403. First hydraulic delivery pipe; 500. Electric motor; 501. Second hydraulic pump; 502. Second check valve; 503. Second hydraulic delivery pipe; 600. Hydraulic source switching valve; 700. Hydraulic motor; 701. Compressor; 702. Condenser; 703. Eighth connecting pipe; 704. Ninth connecting pipe; 705. Tenth connecting pipe; 800. First heat source. Detailed Implementation

[0032] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the embodiments of the present invention will be further described in detail below with reference to the accompanying drawings and examples. It should be understood that the specific embodiments described herein are only for explaining the present invention and are not intended to limit the present invention.

[0033] In the description of the embodiments of the present invention, it should be understood that the terms "upper", "lower", "front", "rear", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the embodiments of the present invention.

[0034] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation", "connection" and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, an integral connection, or a detachable connection; they can refer to the internal connection of two components; they can refer to a direct connection or an indirect connection through an intermediate medium. For those skilled in the art, the specific meaning of the above terms in the embodiments of the present invention can be understood according to the specific circumstances.

[0035] See Figures 1 to 3 As shown, the dual-powered (diesel and electric) air conditioning system of this invention includes an evaporator 100, a first heat source 800, a second heat source 200, a heat source switching valve group, a refrigeration module, a first hydraulic drive source, a second hydraulic drive source, and a hydraulic control valve 600.

[0036] The evaporator 100 is equipped with heat source coils and cold source coils in a serpentine pattern.

[0037] Both the first heat source 800 and the second heat source 200 can provide heat to the heat source coil. The first heat source 800 and the second heat source 200 are circulatedly connected to the heat source coil through a heat source switching valve group. The heat source switching valve group can selectively connect the first heat source 800 or the second heat source 200 to the heat source coil.

[0038] The refrigeration module includes a hydraulic motor 700 and a compressor 701. The output shaft of the hydraulic motor 700 is connected to the power input shaft of the compressor 701. The refrigerant outlet and refrigerant inlet of the compressor 701 are connected to the cold source coil inlet 1013 and cold source coil outlet 1014 of the cold source coil through the condenser 702.

[0039] Both the first hydraulic drive source and the second hydraulic drive source can provide hydraulic driving force to the hydraulic motor 700. The first hydraulic drive source and the second hydraulic drive source are connected to the drive oil circuit of the hydraulic motor 700 through the hydraulic control valve 600.

[0040] When cooling is required, hydraulic oil output from either the first or second hydraulic drive source enters the hydraulic motor 700 via the hydraulic control valve 600. The hydraulic motor 700 drives the compressor 701, which compresses the refrigerant. The refrigerant evaporates and absorbs heat in the cold source coil via the condenser 702, causing the evaporator 100 to blow out cold air. When heating is required, the heat source switching valve group transfers heat from the first heat source 800 or the second heat source 200 to the heat source coil. The heat source coil releases heat, causing the evaporator 100 to blow out hot air. By setting the first heat source 800 and the second heat source 200, as well as the first and second hydraulic drive sources, the system can achieve both cooling and heating functions in both power modes.

[0041] The heat source switching valve assembly includes a heat source delivery component and a return component. The heat source delivery component includes a main inlet pipe 300. One end of the main inlet pipe 300 is connected to the heat source coil inlet 1011 in the heat source coil. The other end of the main inlet pipe 300 is connected to a second three-way valve 309. One outlet of the second three-way valve 309 is connected to a fifth connecting pipe 310. A third electric valve 311 is installed on the fifth connecting pipe 310. The other outlet of the second three-way valve 309 is connected to a sixth connecting pipe 312. A fourth electric valve 313 is installed on the sixth connecting pipe 312.

[0042] The liquid return assembly includes a main liquid return pipe 301. One end of the main liquid return pipe 301 is connected to the outlet 1012 of the heat source coil in the heat source coil. The other end of the main liquid return pipe 301 is connected to a first tee 302. One outlet of the first tee 302 is connected to a third connecting pipe 306. A second electric valve 307 is installed on the third connecting pipe 306. The other outlet of the first tee 302 is connected to a first connecting pipe 303. A first electric valve 304 is installed on the first connecting pipe 303.

[0043] The main inlet pipe 300 in the heat source delivery assembly delivers antifreeze from either the first heat source 800 or the second heat source 200 to the heat source coil inlet 1011. After releasing heat, the antifreeze in the heat source coil flows out from the heat source coil outlet 1012 and returns via the main return pipe 301. The second three-way valve 309, in conjunction with the third electric valve 311 and the fourth electric valve 313, selectively delivers antifreeze from either the first heat source 800 or the second heat source 200 into the main inlet pipe 300. The first three-way valve 302, in conjunction with the first electric valve 304 and the second electric valve 307, selectively returns the antifreeze to either the first heat source 800 or the second heat source 200. The four electric valves work together to ensure the integrity of the heating circuit and prevent mutual interference.

[0044] When the system detects that the diesel engine is operating, the third electric valve 311 and the second electric valve 307 open, while the first electric valve 304 and the fourth electric valve 313 close, forming a diesel engine cylinder liner water circulation. When the system detects that the three-phase motor is powered, the fourth electric valve 313 and the first electric valve 304 open, while the second electric valve 307 and the third electric valve 311 close. Simultaneously, the water pump 201 and the PTC heater 202 are activated, forming an electrically heated water circulation. This design allows the circulation pipelines of the two heat sources to be completely independent.

[0045] The first heat source 800 includes a diesel engine cylinder liner, which stores antifreeze. The outlet of the diesel engine cylinder liner is connected to the inlet of the third electric valve 311, and the return port of the diesel engine cylinder liner is connected to the outlet of the second electric valve 307 through the fourth connecting pipe 308.

[0046] When the diesel engine is running, the antifreeze in the cylinder liner absorbs the waste heat of the diesel engine and heats up. The hot antifreeze flows out from the outlet of the diesel engine cylinder liner, enters the main inlet pipe 300 through the third electric valve 311, and then enters the heat source coil to release heat. The cooled antifreeze flows through the main return pipe 301 and the first three-way valve 302 to the second electric valve 307, and then returns to the return port of the diesel engine cylinder liner through the fourth connecting pipe 308, forming a closed loop. This scheme makes full use of the waste heat of the diesel engine and can achieve heating without consuming additional energy.

[0047] The second heat source 200 includes a water tank, a water pump 201, and a PTC heater 202. The water tank stores antifreeze. The outlet of the water tank is connected to the inlet of the water pump 201. The outlet of the water pump 201 is connected to the inlet of the PTC heater 202. The outlet of the PTC heater 202 is connected to the inlet of the fourth electric valve 313 through the seventh connecting pipe 314. The return port of the water tank is connected to the outlet of the first electric valve 304 through the second connecting pipe 305.

[0048] When the three-phase motor is powered and heating is required, the water pump 201 starts, pumping antifreeze from the water tank into the PTC heater 202. The PTC heater 202 is energized and heats up the flowing antifreeze. The heated antifreeze enters the fourth electric valve 313 through the seventh connecting pipe 314, then enters the heat source coil through the main inlet pipe 300 to release heat. The cooled antifreeze flows to the first electric valve 304 through the main return pipe 301 and the first three-way valve 302, and then returns to the water tank through the second connecting pipe 305, forming an independent electric heating cycle. The PTC heater 202 has a positive temperature coefficient characteristic; its resistance increases as the temperature rises, automatically limiting the temperature for safety and reliability.

[0049] The first hydraulic drive source includes a diesel engine 400 and a first hydraulic pump 401. The power output shaft of the diesel engine 400 is connected to the power input shaft of the first hydraulic pump 401. The inlet of the first hydraulic pump 401 is connected to the outlet of the hydraulic oil tank. The outlet of the first hydraulic pump 401 is connected to a first hydraulic delivery pipe 403.

[0050] When the diesel engine 400 is running, its power output shaft drives the first hydraulic pump 401 to rotate. The first hydraulic pump 401 draws hydraulic oil from the hydraulic oil tank, pressurizes it, and outputs high-pressure hydraulic oil through the first hydraulic delivery pipe 403. This high-pressure hydraulic oil enters the hydraulic motor 700 through the subsequent hydraulic control valve 600, driving the compressor 701 to work. Since the first hydraulic pump 401 is mechanically connected to the diesel engine 400, as long as the diesel engine 400 is running, the first hydraulic pump 401 has the ability to supply oil, without the need for additional control.

[0051] The second hydraulic drive source includes an electric motor 500 and a second hydraulic pump 501. The power output shaft of the electric motor 500 is connected to the power input shaft of the second hydraulic pump 501. The inlet of the second hydraulic pump 501 is connected to the outlet of the hydraulic oil tank. The outlet of the second hydraulic pump 501 is connected to a second hydraulic delivery pipe 503.

[0052] When the electric motor 500 is powered on, its power output shaft drives the second hydraulic pump 501 to rotate. The second hydraulic pump 501 draws hydraulic oil from the hydraulic oil tank, pressurizes it, and outputs high-pressure hydraulic oil through the second hydraulic delivery pipe 503. This high-pressure hydraulic oil enters the hydraulic motor 700 through the subsequent hydraulic control valve 600, driving the compressor 701 to work. The electric motor 500 can be powered by three-phase 380V AC power, and its speed can be adjusted by a frequency converter, thereby adjusting the output flow of the hydraulic pump and realizing stepless speed regulation refrigeration of the compressor 701.

[0053] The hydraulic control valve 600 is a two-position four-way solenoid valve. The outlet of the first hydraulic delivery pipe 403 and the outlet of the second hydraulic delivery pipe 503 are both connected to the P port of the hydraulic control valve 600. The A port of the hydraulic control valve 600 is connected to the oil inlet of the hydraulic motor 700. The B port of the hydraulic control valve 600 is connected to the oil return port of the hydraulic motor 700. The T port of the hydraulic control valve 600 is connected to the oil return port of the hydraulic oil tank.

[0054] The high-pressure hydraulic oil output from the first hydraulic delivery pipe 403 and the second hydraulic delivery pipe 503 converges at port P of the hydraulic control valve 600 and enters the two-position four-way solenoid valve. When the solenoid valve is in the neutral position, port P is connected to port T, and the hydraulic oil flows directly back to the hydraulic oil tank. The hydraulic motor 700 does not rotate, and the compressor 701 stops. When the solenoid valve is energized in the left position, port P is connected to port A, and port B is connected to port T. High-pressure oil enters the inlet of the hydraulic motor 700, driving the hydraulic motor 700 to rotate forward. The return oil returns to the oil tank via ports B and T. When the solenoid valve is energized in the right position, port P is connected to port B, and port A is connected to port T, driving the hydraulic motor 700 to rotate in reverse. By changing the energization state of the solenoid valve, the start, stop, and rotation direction of the compressor 701 can be controlled.

[0055] A first check valve 402 is installed on the first hydraulic delivery pipe 403, and a second check valve 502 is installed on the second hydraulic delivery pipe 503.

[0056] The first check valve 402 allows hydraulic oil to flow from the first hydraulic pump 401 to the P port of the hydraulic control valve 600, but prevents reverse flow; the second check valve 502 allows hydraulic oil to flow from the second hydraulic pump 501 to the P port of the hydraulic control valve 600, but prevents reverse flow.

[0057] The refrigerant outlet of compressor 701 is connected to the inlet of condenser 702 through the tenth connecting pipe 705; the outlet of condenser 702 is connected to the inlet 1013 of cold source coil through the ninth connecting pipe 704; the outlet 1014 of cold source coil is connected to the refrigerant inlet of compressor 701 through the eighth connecting pipe 703, and an expansion valve is installed on the ninth connecting pipe 704.

[0058] The high-temperature, high-pressure gaseous refrigerant discharged from compressor 701 enters condenser 702 via tenth connecting pipe 705. In condenser 702, it dissipates heat and condenses into high-pressure liquid refrigerant. The liquid refrigerant flows through ninth connecting pipe 704 and then through expansion valve. Expansion valve throttles and reduces its pressure to low-temperature, low-pressure mist-like refrigerant, which then enters cold source coil inlet 1013. In the cold source coil, it evaporates and absorbs heat, cooling the air surrounding evaporator 100. The evaporated gaseous refrigerant returns from cold source coil outlet 1014 to compressor 701 refrigerant inlet via eighth connecting pipe 703, completing the refrigeration cycle. The expansion valve automatically adjusts its opening based on the superheat at the cold source coil outlet to control refrigerant flow and prevent liquid slugging.

[0059] During installation, only the evaporator 100 and the air conditioning control panel are placed in the cab, while the rest of the components are placed on the chassis. The cab does not contain high-voltage electricity, ensuring high overall safety and not taking up too much interior space.

[0060] In addition, this dual-power (diesel and electric) air conditioning system also includes a dynamic power matching controller, a cab temperature sensor, a compressor power sensor, and a PTC power sensor. The dynamic power matching controller is electrically connected to the hydraulic control valve, PTC heater 202, cab temperature sensor, compressor power sensor, and PTC power sensor, respectively. The dynamic power matching controller has a built-in dynamic matching control equation for cooling and heating power during the diesel-electric switching transition process, and the equation is as follows: ;

[0061] in, The power conversion factor is dimensionless. This refers to the real-time input power of the compressor, expressed in watts (W). This is the heating power compensation coefficient, which is dimensionless. This refers to the real-time input power of the PTC heater, expressed in watts (W). The thermal inertia coefficient of the driver's cab is expressed in J / K. This refers to the real-time temperature of the driver's cab, expressed in Kelvin (K). This is the coefficient of heat loss variation, with units of W / K.

[0062] Taking the cab of a loader in an underground mine as an example, the known parameters are:

[0063] Cab volume Specific heat capacity of air at constant volume air density ;

[0064] Driver's cab heat transfer coefficient heat transfer area ;

[0065] compressor in cooling mode PTC efficiency in heating mode Waste heat coupling coefficient ;

[0066] Step 1: Calculate the fixed parameters

[0067] Thermal inertia coefficient: ;

[0068] Heat loss variation coefficient: ;

[0069] Step 2: Example of cooling mode switching control

[0070] When switching from diesel engine-driven to electric motor-driven cooling, the sensor detects:

[0071] Second derivative of cab temperature: ;

[0072] First derivative of cab temperature: ;

[0073] Cooling mode , ;

[0074] Substitute into the equation: ; The solution is: ;

[0075] Control action: The controller outputs a signal to the proportional speed-regulating two-position four-way solenoid valve to reduce the hydraulic motor input flow at a corresponding rate, so that the compressor input power decreases steadily at a rate of 191.84W / s, avoiding a sudden rise in temperature.

[0076] Step 3: Example of heating mode switching control

[0077] When switching from electric motor drive to diesel engine drive for heating, the sensor detects:

[0078] Second derivative of cab temperature: ;

[0079] First derivative of cab temperature: ;

[0080] Heating mode , ;

[0081] Substitute into the equation: ; ;

[0082] To fully utilize the waste heat from the diesel engine, the controller prioritizes increasing the compressor power (while simultaneously increasing waste heat output), and sets the compressor power increase rate to [value missing]. Substitute the values ​​into the equation to solve for the PTC power change rate: ; ; ; ;

[0083] Control Action: The controller controls the compressor power to rise steadily at a rate of 200W / s, while simultaneously controlling the PTC heater power to decrease linearly at a rate of 876W / s, achieving seamless connection between waste heat and electric heating and avoiding sudden temperature drops.

[0084] Technical Benefits: During diesel-to-electric switching, the temperature fluctuation in the cab is reduced from ±2~3℃ in the traditional system to within ±0.5℃, fully meeting the comfort requirements of underground construction personnel and avoiding operational errors caused by sudden temperature changes; dynamic power matching avoids overcompensation of the PTC heater, reducing overall energy consumption by 12%~18% in heating mode, extending the range of the motor and battery, and reducing equipment operating costs; it suppresses sudden shocks in compressor speed, increasing the mean time between failures (MTBF) of the hydraulic and refrigeration systems by more than 30%, reducing equipment maintenance frequency and downtime; and it supports online self-learning correction. and The coefficient can adapt to changes in ambient temperature, cab sealing conditions, and equipment aging, maintaining optimal control performance over the long term; it eliminates the risk of compressor reversal from both hardware and software perspectives, while also preventing PTC heater overload operation and improving overall system safety.

[0085] The working principle and process of the equation:

[0086] 1. Data Acquisition Layer: Real-time acquisition of cab temperature, compressor input power, PTC input power, current power source type (diesel engine / electric motor), and air conditioning operating mode (cooling / heating) at a sampling frequency of 10Hz.

[0087] 2. Mode Judgment Layer: Based on the air conditioner's operating mode and power source type, automatically matches the equations... and Coefficient; when a power source switching signal is detected, the dynamic power matching control process is initiated.

[0088] 3. Numerical Calculation Layer: A five-point smoothing filter algorithm is used to preprocess the temperature data, and then the result is calculated using the central difference method. and Substitute the values ​​into the core equation to solve for the required rate of power change.

[0089] 4. Control output layer: Outputs PWM flow regulation signal to proportional speed-regulating two-position four-way solenoid valve to control the compressor power to change smoothly according to the calculated value; outputs PWM duty cycle regulation signal to PTC heater to control its power to change synchronously.

[0090] 6. Closed-loop feedback layer: Continuously collect temperature and power data, repeat the above steps for closed-loop control until the switching process is completed and the temperature stabilizes within the set value ±0.3℃ range, then exit the dynamic power matching mode and switch to normal steady-state control.

[0091] Overall working principle:

[0092] When the equipment is in diesel engine driven mode, the diesel engine 400 operates, driving the first hydraulic pump 401 to rotate. The first hydraulic pump 401 draws hydraulic oil from the hydraulic oil tank and pressurizes it, then sends it to the P port of the hydraulic control valve 600 via the first check valve 402 and the first hydraulic delivery pipe 403. If the air conditioning control panel issues a cooling command, the hydraulic control valve 600 switches to the working position, and high-pressure oil enters the hydraulic motor 700, driving the hydraulic motor 700 to rotate. The hydraulic motor 700 drives the compressor 701 to operate. The compressor 701 compresses the refrigerant, which passes through the condenser 702 and the expansion valve before entering the cold source coil to evaporate and absorb heat. The evaporator 100 blows out cold air. If the air conditioning control panel issues a heating command and the control system detects that the diesel engine 400 is working, it opens the third electric valve 311 and the second electric valve 307, and closes the first electric valve 304 and the fourth electric valve 313. The hot antifreeze in the diesel engine cylinder liner enters the heat source coil through the third electric valve 311 and the main inlet pipe 300 to release heat, heating the air around the evaporator 100 and blowing out hot air. The cooled antifreeze returns to the diesel engine cylinder liner through the main return pipe 301, the second electric valve 307, and the fourth connecting pipe 308, completing the heating cycle.

[0093] When the equipment is in three-phase motor driven operation, the motor 500 operates, driving the second hydraulic pump 501 to rotate. The second hydraulic pump 501 draws hydraulic oil from the hydraulic oil tank and pressurizes it, then sends it to the P port of the hydraulic control valve 600 via the second check valve 502 and the second hydraulic delivery pipe 503. The cooling operation is the same as when driven by a diesel engine; the hydraulic control valve 600 controls the hydraulic motor 700 to drive the compressor 701 for cooling. If heating is required, the control system detects the three-phase motor power supply, opens the fourth electric valve 313 and the first electric valve 304, closes the second electric valve 307 and the third electric valve 311, and simultaneously starts the water pump 201 and the PTC heater 202. The antifreeze in the water tank is pumped into the PTC heater 202 by the water pump 201 and heated. The hot antifreeze enters the heat source coil through the fourth electric valve 313 and the main inlet pipe 300 to release heat and blow out hot air. The return liquid returns to the water tank through the main return pipe 301, the first electric valve 304 and the second connecting pipe 305, completing the electric heating cycle.

[0094] When the equipment does not require cooling or heating, the hydraulic control valve 600 remains in the neutral position, the hydraulic oil returns directly to the oil tank, and the hydraulic motor 700 and compressor 701 stop operating; all electric valves in the heat source switching valve group are closed or remain in their current state, and the heat source circulation stops.

[0095] The above description illustrates the basic principles of the present invention. The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. The above embodiments and descriptions in the specification are only for illustrating the principles of the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and scope of the present invention without departing from the scope of the present invention should be included within the protection scope of the present invention.

Claims

1. A dual-power (diesel and electric) air conditioning system for both cooling and heating, characterized in that... include: Evaporator (100), on which heat source coil and cold source coil are installed in a serpentine manner; A first heat source (800), a second heat source (200), and a heat source switching valve group are provided. Both the first heat source (800) and the second heat source (200) provide heat to the heat source coil. The first heat source (800) and the second heat source (200) are circulatedly connected to the heat source coil through the heat source switching valve group. The heat source switching valve group connects the first heat source (800) or the second heat source (200) to the heat source coil. The refrigeration module includes a hydraulic motor (700) and a compressor (701). The output shaft of the hydraulic motor (700) is connected to the power input shaft of the compressor (701). The refrigerant outlet and refrigerant inlet of the compressor (701) are connected to the cold source coil inlet (1013) and cold source coil outlet (1014) of the cold source coil through a condenser (702). The system comprises a first hydraulic drive source, a second hydraulic drive source, and a hydraulic control valve (600). Both the first and second hydraulic drive sources provide hydraulic driving force to the hydraulic motor (700). The first and second hydraulic drive sources are connected to the drive oil circuit of the hydraulic motor (700) through the hydraulic control valve (600).

2. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 1, characterized in that: The heat source switching valve group includes a heat source delivery assembly, which includes a main inlet pipe (300). One end of the main inlet pipe (300) is connected to the heat source coil inlet (1011) in the heat source coil. The other end of the main inlet pipe (300) is connected to a second three-way valve (309). One outlet of the second three-way valve (309) is connected to a fifth connecting pipe (310). A third electric valve (311) is installed on the fifth connecting pipe (310). The other outlet of the second three-way valve (309) is connected to a sixth connecting pipe (312). A fourth electric valve (313) is installed on the sixth connecting pipe (312).

3. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 2, characterized in that: The heat source switching valve group also includes a return liquid assembly, which includes a main return liquid pipe (301). One end of the main return liquid pipe (301) is connected to the heat source coil outlet (1012) in the heat source coil. The other end of the main return liquid pipe (301) is connected to a first tee (302). One outlet of the first tee (302) is connected to a third connecting pipe (306). A second electric valve (307) is installed on the third connecting pipe (306). The other outlet of the first tee (302) is connected to a first connecting pipe (303). A first electric valve (304) is installed on the first connecting pipe (303).

4. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 3, characterized in that: The first heat source (800) includes a diesel engine cylinder liner, which stores antifreeze. The outlet of the diesel engine cylinder liner is connected to the inlet of the third electric valve (311), and the return port of the diesel engine cylinder liner is connected to the outlet of the second electric valve (307) through a fourth connecting pipe (308).

5. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 3, characterized in that: The second heat source (200) includes a water tank, a water pump (201), and a PTC heater (202). The water tank stores antifreeze. The outlet of the water tank is connected to the inlet of the water pump (201). The outlet of the water pump (201) is connected to the inlet of the PTC heater (202). The outlet of the PTC heater (202) is connected to the inlet of the fourth electric valve (313) through a seventh connecting pipe (314). The return port of the water tank is connected to the outlet of the first electric valve (304) through a second connecting pipe (305).

6. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 1, characterized in that: The first hydraulic drive source includes a diesel engine (400) and a first hydraulic pump (401). The power output shaft of the diesel engine (400) is connected to the power input shaft of the first hydraulic pump (401). The inlet of the first hydraulic pump (401) is connected to the outlet of the hydraulic oil tank. The outlet of the first hydraulic pump (401) is connected to a first hydraulic delivery pipe (403).

7. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 6, characterized in that: The second hydraulic drive source includes an electric motor (500) and a second hydraulic pump (501). The power output shaft of the electric motor (500) is connected to the power input shaft of the second hydraulic pump (501). The inlet of the second hydraulic pump (501) is connected to the outlet of the hydraulic oil tank. The outlet of the second hydraulic pump (501) is connected to a second hydraulic delivery pipe (503).

8. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 7, characterized in that: The hydraulic control valve (600) is a two-position four-way solenoid valve. The outlet of the first hydraulic delivery pipe (403) and the outlet of the second hydraulic delivery pipe (503) are both connected to the P port of the hydraulic control valve (600). The A port of the hydraulic control valve (600) is connected to the oil inlet of the hydraulic motor (700). The B port of the hydraulic control valve (600) is connected to the oil return port of the hydraulic motor (700). The T port of the hydraulic control valve (600) is connected to the oil return port of the hydraulic oil tank.

9. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 8, characterized in that: A first check valve (402) is installed on the first hydraulic delivery pipe (403), and a second check valve (502) is installed on the second hydraulic delivery pipe (503).

10. The dual-power (diesel and electric) air conditioning system for both cooling and heating according to claim 1, characterized in that: The refrigerant outlet of the compressor (701) is connected to the inlet of the condenser (702) via the tenth connecting pipe (705); the outlet of the condenser (702) is connected to the inlet (1013) of the cold source coil via the ninth connecting pipe (704). The outlet (1014) of the cold source coil is connected to the refrigerant inlet of the compressor (701) through the eighth connecting pipe (703), and an expansion valve is installed on the ninth connecting pipe (704).

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