Special low-carbon ventilation regulation and control method for hotel guest rooms

Abstract

The invention provides a low-carbon ventilation regulation and control method special for a hotel guest room, and the method comprises the following steps: S1, enabling a hotel guest room management system, a fresh air unit, an exhaust unit and a guest room power taking system to be in communication connection with an upper computer, a heat exchanger is arranged between the air inlet section of the fresh air unit and the air exhaust section of the air supply unit so as to recover cold or heat in air exhaust of the air exhaust unit; s2, the hotel guest room management system transmits guest room check-in information to the upper computer, and the guest room electricity taking system transmits electricity taking information to the upper computer; s3, after the upper computer receives the guest room check-in information and the electricity taking information, the upper computer adjusts the fan air supply amount Q of a fresh air handling unit of the guest room in the current area according to the number M of guest room check-in personnel in the check-in information; and S4, the upper computer controls the exhaust air rate of the exhaust unit according to the air supply rate of the fresh air unit, so that the exhaust air rate of the exhaust unit is 65%-90% of the air supply rate of the fresh air unit, and the positive pressure in the guest room is maintained. And the effects of air exhaust and air supply combined adjustment and energy conservation are achieved.

Description

Technical Field

[0001] The present invention relates to the technical field of energy-saving equipment, and particularly to a low-carbon ventilation regulation method dedicated for hotel guest rooms. Background Art

[0002] At present, for the ventilation system of a hotel building after heat recovery transformation, the efficient operation of this system is an important indicator for evaluating energy-saving transformation. However, currently, each system operates independently: the fresh air units and exhaust fan units in existing hotel guest rooms all operate independently, and the energy consumption of independent operation is relatively high. The energy consumption of the exhaust fan units without heat recovery is seriously wasted, and the systems with heat recovery do not coordinate the balance between each system, and each system cannot perform comprehensive regulation according to the situation in the room. Generally, hotel bathrooms are set inside the guest rooms, and it can be considered that the exhaust air temperature in the bathroom is the same as the indoor temperature. When the exhaust fan unit is turned on, the fresh air demand in the guest room increases. If the air supply volume of the fresh air unit is insufficient, the outdoor hot air or cold air will enter the room along the gaps of the doors and windows, thus increasing the load of the air-conditioning system in the guest room and resulting in high fresh air energy consumption. Summary of the Invention

[0003] To solve the above problems, the purpose of the present invention is to provide a low-carbon ventilation regulation method dedicated for hotel guest rooms.

[0004] The present invention is implemented by the following method: A low-carbon ventilation regulation method dedicated for hotel guest rooms, including a hotel guest room management system, a fresh air unit, an exhaust fan unit, and a power-taking system for guest rooms, and is regulated through the following steps: Step S1: Communicate and connect the hotel guest room management system, the fresh air unit, the exhaust fan unit, and the power-taking system for guest rooms with the upper computer, and set a heat exchanger between the air inlet section of the fresh air unit and the air exhaust section of the air supply unit to recover the cold or heat in the exhaust air of the exhaust fan unit; Step S2: The hotel guest room management system transmits the guest room occupancy information to the upper computer, and the power-taking system for guest rooms transmits the power-taking information to the upper computer; Step S3: After the upper computer simultaneously receives the guest room occupancy information and the power-taking information, the upper computer determines the number of occupants M in the guest rooms in this area. The upper computer adjusts the air supply volume Q of the fresh air unit of the guest rooms in the current area according to the number of occupants M in the occupancy information. Set the minimum air supply volume of the fresh air unit as Qmin, which meets the fresh air demand of N persons. When the number of occupants M exceeds the preset value N, calculate the fresh air volume according to the formula Q = Qmin + A×(M−N) and control the air supply volume of the fresh air unit; A is the fresh air demand per person; Step S4: The upper computer controls the air exhaust volume of the exhaust fan unit according to the air supply volume of the fresh air unit, so that the air exhaust volume of the exhaust fan unit is 65%-90% of the air supply volume of the fresh air unit to maintain a positive pressure in the guest room.

[0005] Preferably, in step S3, the air supply volume of the fresh air unit is determined through the following steps: Step S31, establish the flow curve Q=f(VSP) and pressure curve H=g(VSP) of the fan model of the fresh air unit through on-site testing; calculate the air resistance of the air duct and the most unfavorable point of the air duct according to the installation trend of the air supply duct, and find the minimum rotational speed required by the fan of the fresh air unit at the most unfavorable point according to the fan model by looking up the table. Step S32, when there is a fresh air demand for the occupancy of the guest rooms in the current area, the fan of the fresh air unit is started at the set minimum rotational speed. At this time, there is a corresponding minimum air supply volume Qmin, which meets the fresh air volume demand of N persons. When the number of occupied guest rooms M in this area is greater than N persons, the fresh air unit adjusts the air supply volume upwards. When the number of persons decreases, the air supply volume is reduced accordingly. When the number of occupied guest rooms M is not greater than N, Q1 = Qmin; when the number of persons is greater than N, Q1 = Qmin + A(M - N). Q1——The air supply volume of the fresh air unit, m³ / h; Qmin——The minimum air supply volume of the fresh air unit, m³ / h, corresponding to meeting the fresh air volume demand of N persons; M——The number of occupied guest rooms in the area, with a fresh air volume demand of A m³ / h per person.

[0006] Step S33, when the fresh air unit of the guest rooms in the current area is started, the exhaust fan is correspondingly started. The exhaust frequency of the exhaust fan is set according to the size of the bathroom, and is set to 5 - 10 times / h. The exhaust air volume of the exhaust fan is set to Qexhaust. To ensure the positive pressure in the room, the exhaust air volume Qexhaust should be 70% - 80% of the fresh air volume Q2, and Q2 = Qexhaust / (70% - 80%); Step S34, according to the fresh air volume Q1 calculated in step S32 and the fresh air volume Q2 calculated in step S33, select the larger value as the actual air supply volume to set the air supply volume Q of the fresh air unit fan; substitute the air volume Q into the flow curve Q=f(VSP) and pressure curve H=g(VSP) of the fan model, and the operating frequency VSP required by the fresh air unit fan can be obtained to set the rotational speed of the fresh air unit fan.

[0007] Preferably, in step S31, the establishment of the fan model includes the following steps: Step S311, determine the fan test frequency range to be 20 - 50 Hz; Step S312, manually set the frequency of the fresh air unit to 20 Hz, measure and record the on-site fan air volume value (m3 / h) and pressure difference (Pa); Step S313, manually set the fan frequency of the fresh air unit to increase by 5 Hz, and record the on-site fan air volume value (m3 / h) and pressure difference (Pa), and repeat this process until the fan frequency of the fresh air unit increases to 50 Hz; Step S314, fit the seven groups of data to generate a flow curve Q = f(VSP) and a pressure curve H = g(VSP); Step 315, input the coefficients of the flow curve Q = f(VSP) and the pressure curve H = g(VSP) into the intelligent controller.

[0008] Preferably, in step S31, the minimum supply air volume Qmin is determined by the fan model of the pre-established fresh air unit. The calculation formulas for the air volume curve Q = f(VSP) and the pressure curve H = g(VSP) are as follows: Q = f(VSP) = VCoeff1 * VSP + Vcoeff2 H = g(VSP) = PCoeff1 * VSP^2 + Pcoeff2 * VSP + Pcoeff3 In the formula: Q—the air volume of the fresh air unit fan, m3 / h; VSP—the operating frequency of the fresh air unit fan, Hz; VCoeff1, Vcoeff2—the coefficients of the air volume performance curve of the fresh air unit fan, obtained from on-site measurements; PCoeff1, Pcoeff2, Pcoeff3—the coefficients of the pressure performance curve of the fresh air unit fan, obtained from on-site measurements.

[0009] Preferably, in step S1, the heat exchanger has a first heat exchange side, a second heat exchange side, and a third heat exchange side. The fresh air unit includes an evaporation end, a condensation end, and an inlet fan; connect the outlet end of the exhaust fan unit to the second heat exchange side of the heat exchanger, and connect the exhaust air on the second heat exchange side of the heat exchanger to the condensation end of the fresh air unit; connect the inlet end of the fresh air unit to the first heat exchange side of the heat exchanger, and the incoming air of the fresh air unit passes through the first heat exchange side of the heat exchanger, the inlet fan, and the evaporation end and then enters the guest room.

[0010] Preferably, in step S1, according to the seasonal change, the heat exchanger provided between the air inlet section of the fresh air unit and the exhaust air section of the supply air unit can be switched to the summer working mode or the winter working mode; summer interfaces and winter interfaces are provided at both the condensation end and the evaporation end of the fresh air unit; when switched to the winter working mode, the exhaust air on the second heat exchange side of the heat exchanger is connected to the winter interface of the evaporation end of the fresh air unit, and the outlet of the supply air fan is connected to the winter interface of the condensation end; when switched to the summer working mode, the exhaust air on the second heat exchange side of the heat exchanger is connected to the summer interface of the condensation end of the fresh air unit, and the outlet of the supply air fan is connected to the summer interface of the evaporation end.

[0011] Preferably, in step S1, a water storage tank is provided, and the heat exchange coil in the water storage tank is connected to the condensation end of the fresh air unit, or the heat exchange coil is connected to the third heat exchange side of the heat exchanger for preparing domestic hot water; the clean energy inlets of the fresh air unit and the exhaust air unit are connected to a clean energy power generation system.

[0012] Preferably, in step S1, a first air valve is provided at the exhaust air outlet of each guest room, and a second air valve is provided at the air inlet of each guest room. The first air valve and the second air valve are electrically connected to the upper computer. The air inlet of each guest room is connected to the outlet end of the fresh air unit, and the exhaust air outlet of each guest room is connected to the inlet end of the exhaust air unit. In step S3, after the upper computer receives the power-on information of the guest room power supply system, the upper computer controls the opening of the first air valve and the second air valve in the corresponding guest room.

[0013] Preferably, in step S1, all the guest rooms on the same floor of the hotel are classified into the same area, and the total number of occupants in the guest rooms in the same area is sent to the upper computer. The outlets of the exhaust air units on the same floor of the hotel are jointly connected to an exhaust air duct; one or more fresh air units are shared by the guest rooms on the same floor, and the inlet ends of the fresh air units on the same floor are all connected to the first heat exchange side of the same heat exchanger, and the exhaust air duct is connected to the second heat exchange side of the same heat exchanger.

[0014] Preferably, in step S3, after the upper computer receives the occupancy information and power-on information of the guest rooms on the floor of this area, it determines the total number of occupants M in all the guest rooms in this area. The upper computer adjusts the air supply volume Q of the fresh air units connected to the guest rooms in the current floor area according to the number of occupants M in the guest rooms; in step S4, the upper computer regulates the exhaust air volume of the exhaust air units on the floor of this area according to the air supply volume Q of the fresh air units connected to this floor. The beneficial effects of the present invention are as follows: The present invention provides a special low-carbon ventilation regulation method for hotel guest rooms. Compared with the prior art, the present invention has at least the following technical effects: 1. A heat exchanger is arranged between the fresh air unit and the exhaust fan unit to recover the waste heat or waste cold of the exhaust air, which can reduce the energy consumption of the fresh air unit and the central air-conditioning system; when a hotel guest room management system inputs the number of people during the check-in registration of a tenant, the power-taking system can read whether there is power-taking in the room and transmit the number of people checked in and taking power in this area to the host computer. The host computer can then adjust the fan speed of the fresh air unit to control the supply air volume threshold according to the number of people staying in the room and the room information. Furthermore, within this threshold range, on-demand supply is carried out according to the real-time fresh air feedback load of the hotel, thereby realizing precise control of the fresh air volume in hotel guest rooms; at the same time, the exhaust air volume is set to 65%-90% of the supply air volume, and the fresh air volume is slightly larger than the exhaust air volume to ensure a slightly positive pressure in the room, while also reducing the entry of outdoor air and avoiding the leakage of cold or heat, further achieving an energy-saving effect. 2. By establishing the Q=f(VSP) and H=g(VSP) curves through on-site testing, the actual duct resistance characteristics can be accurately matched, avoiding a 20-30% air volume deviation caused by traditional empirical formulas; by determining the lowest speed at the most unfavorable point, it is ensured that the air resistance can still be overcome at the lowest supply air volume Qmin to meet the basic needs of N people and avoid inefficient operation; dual air volume control: in step S34, the larger value of Q1 / Q2 is selected, taking into account the personnel needs and positive pressure maintenance to achieve multi-objective optimization. 3. The 20-50Hz step-by-step test covers the actual working range of the fan, which can improve the model accuracy by more than 15% compared with only testing typical frequencies (such as 30 / 40 / 50Hz); the error of the curve fitted by seven data points is reduced to within ±3% compared with the linear interpolation method, ensuring the consistency between the control command and the on-site working conditions. 4. Three-side heat exchange design: The first side pre-cools / pre-heats the fresh air, the second side recovers the exhaust air energy, and the third side is linked to the domestic hot water system, increasing the exhaust air waste heat utilization rate from the conventional 40% to more than 65%; the heat exchange temperature difference is strengthened through the heat pump cycle of the fresh air unit, and a heat recovery efficiency of more than 60% can still be maintained under extreme climates (such as -10°C / 40°C). 5. Seasonal mode switching: The connection methods of the evaporation / condensation ends are optimized in winter and summer modes respectively, increasing the summer cold recovery rate by 25% and the winter heat recovery rate by 18%, solving the problem of poor seasonal adaptability of traditional single-mode systems. 6. The exhaust air waste heat is preferentially used for fresh air pretreatment, and the remaining heat is used to prepare domestic hot water through a storage water tank to maximize the energy utilization rate; clean energy coupling: Connect to systems such as photovoltaic / ground source heat pumps to further reduce the hotel's electricity cost. 7. The control units are divided by floor, reducing 80% of the signal transmission nodes compared with single-room control, improving the system stability; intensive equipment layout: The fresh air unit and exhaust air ducts are shared on the same floor, reducing the initial investment by more than 30% and at the same time reducing 50% of the maintenance points.8. Floor-level air volume regulation can automatically distribute the unit load according to the occupancy density, avoiding the inefficient operation of multiple units (such as changing from 2 units at 50% load to 1 unit at 100% load), saving 15-20% of the fan energy consumption; air volume coordination and matching: uniformly regulate the floor exhaust air volume to ensure the overall positive pressure gradient in the area and prevent local air leakage problems caused by pressure difference imbalance between different guest rooms. Description of the Drawings

[0015] Figure 1 is the control flow chart of a low-carbon ventilation regulation method for hotel guest rooms according to the present invention.

[0016] Figure 2 is the circuit principle block diagram of a low-carbon ventilation regulation method for hotel guest rooms according to the present invention.

[0017] Figure 3 is the system block diagram of the host computer of the present invention.

[0018] Figure 4 is the system regulation principle block diagram of a low-carbon ventilation regulation method for hotel guest rooms according to the present invention.

[0019] Explanation of the reference numerals in the drawings: 1, evaporation end; 2, intake fan; 3, condensation end; 4, heat exchanger; 5, exhaust fan; 6, first air valve; 7, second air valve; 8, guest room power-taking system; 9, host computer; 10, clean energy access port; 11, water storage tank; 12, heat exchange coil; 13, hotel guest room management system. Detailed Embodiment

[0020] The present invention will be further described below with reference to the drawings and specific embodiments.

[0021] Please refer to Figures 1 to 4 , a low-carbon ventilation regulation method for hotel guest rooms, including a hotel guest room management system 13, a fresh air unit and an exhaust fan group 5, and a guest room power-taking system 8, which is regulated through the following steps: Step S1: Communicate and connect the hotel guest room management system 13, the fresh air unit, the exhaust fan group 5 and the guest room power-taking system 8 with the host computer 9, and set a heat exchanger 4 between the intake section of the fresh air unit and the exhaust section of the supply fan unit to recover the cold or heat in the exhaust air of the exhaust fan group 5; Step S2: The hotel guest room management system 13 transmits the guest room occupancy information to the host computer 9, and the guest room power-taking system 8 transmits the power-taking information to the host computer 9; Step S3. After the host computer 9 receives the guest room occupancy information and power-on information, the host computer 9 determines the number of occupants M in the guest rooms in this area. The host computer 9 adjusts the air supply volume Q of the fresh air unit of the guest rooms in the current area according to the number of occupants M in the occupancy information. The minimum air supply volume of the fresh air unit of the fresh air unit is set as Qmin, which meets the fresh air demand of N persons. When the number of occupants M exceeds the preset value N, the fresh air volume is calculated according to the formula Q = Qmin + A×(M−N) and the air supply volume of the fresh air unit is controlled; A is the fresh air demand of each person. Step S4. The host computer 9 controls the exhaust air volume of the 5 groups of exhaust fans according to the air supply volume of the fresh air unit, so that the exhaust air volume of the 5 groups of exhaust fans is 65%-90% of the air supply volume of the fresh air unit to maintain a positive pressure in the guest room. A heat exchanger 4 is arranged between the fresh air unit and the 5 groups of exhaust fans to recover the waste heat or waste cold of the exhaust air, which can reduce the energy consumption of the fresh air unit and the central air-conditioning system; when the hotel guest room management system 13 registers the occupancy of the guests, the number of people will be input. The power-on system can read whether there is power-on in the room and transmit the number of occupants and power-on people in this area to the host computer 9. The host computer 9 can adjust the air supply volume threshold by controlling the fan speed of the fresh air unit according to the number of occupants in the room and the room information, and then further supply on demand according to the real-time fresh air feedback load of the hotel within this threshold range, so as to realize the accurate control of the fresh air volume in the hotel guest rooms; at the same time, the exhaust air volume is set to 65%-90% of the air supply volume, and the fresh air volume is slightly larger than the exhaust air volume to ensure a slight positive pressure in the room, while also reducing the entry of outdoor air and avoiding the leakage of cold or heat, further achieving an energy-saving effect. Preferably, the fresh air unit can adopt a heat pump type fresh air unit; the heat exchanger 4 is a power tube type heat exchanger 4, etc., and is not limited thereto.

[0022] Please refer to Figures 1 to 4 , preferably, in step S3, the air supply volume of the fresh air unit is determined through the following steps: Step S31. Establish a flow curve Q = f(VSP) and a pressure curve H = g(VSP) of the fan model of the fresh air unit through on-site testing; calculate the air resistance of the air duct and the most unfavorable point of the air duct according to the installation trend of the air supply duct, and find the lowest rotation speed required for the fan of the fresh air unit at the most unfavorable point according to the fan model. There is a corresponding air volume value and pressure value for the air supply outlet at the most unfavorable point of the pipeline. This wind pressure value needs to meet that the air supply outlet wind speed should be maintained at 2-5 m / s (determined by GB50019). According to this requirement, find the corresponding pressure value and air volume in the fan model, which are the lowest pressure point and the minimum air volume value. According to this model, the lowest rotation speed required for the fan can be obtained. Step S32: When there is a fresh air demand for the guests in the current area, the fan of the fresh air unit starts at the set minimum speed. At this time, it corresponds to a minimum air supply volume Qmin, which meets the fresh air demand of N persons. When the number of guests M in the guest rooms in this area is greater than N, the fresh air unit increases the air supply volume. When the number of persons decreases, the air supply volume is correspondingly reduced. When the number of guests M in the guest rooms is not greater than N, Q1 = Qmin; when the number of persons is greater than N, Q1 = Qmin + A(M - N). Q1——The air supply volume of the fresh air unit, m³ / h; Qmin——The minimum air supply volume of the fresh air unit, m³ / h, corresponding to meeting the fresh air demand of N persons; M——The number of guests in the guest rooms in the area, with the fresh air demand of each person being Am³ / h.

[0023] Step S33: When the fresh air unit of the guest rooms in the current area starts, the exhaust fan 5 starts correspondingly. The exhaust frequency of the exhaust fan 5 is set according to the size of the bathroom, and is set to 5 - 10 times / h. The hourly exhaust air volume of the exhaust fan is set to Qexhaust (which is known). To ensure the positive pressure in the room, the exhaust air volume Qexhaust should be 70% - 80% of the fresh air volume Q2, and Q2 = Qexhaust / (70% - 80%); Step S34: According to the fresh air volume Q1 calculated in Step S32 and the fresh air volume Q2 calculated in Step S33, select the larger value as the actual air supply volume to set the air supply volume Q of the fan of the fresh air unit; Substitute the air volume Q into the flow curve Q = f(VSP) and the pressure curve H = g(VSP) of the fan model, and then the required operating frequency VSP of the fan of the fresh air unit can be obtained to set the rotation speed of the fan of the fresh air unit. Preferably, A is 30 m³ / h. Of course, other data can also be used as long as it can meet the fresh air requirements for a single person. By establishing the curves Q = f(VSP) and H = g(VSP) through on-site testing, the actual duct resistance characteristics can be accurately matched, avoiding the 20 - 30% air volume deviation caused by traditional empirical formulas; Determine the minimum speed through the most unfavorable point to ensure that the minimum air supply volume Qmin can still overcome the wind resistance and meet the basic needs of N persons, avoiding inefficient operation; Dual air volume control: Step S34 selects the larger value of Q1 / Q2, taking into account the personnel needs and positive pressure maintenance, and realizing multi-objective optimization.

[0024] Please refer to Figures 1 to 4, preferably, in step S31, the establishment of the fan model includes the following steps: Step S311, determine the fan test frequency range to be 20 - 50 Hz; Step S312, manually set the frequency of the fresh air unit to 20 Hz, measure and record the on-site fan air volume value (m3 / h) and differential pressure (Pa); Step S313, manually set the fan frequency of the fresh air unit to increase by 5 Hz, and record the on-site fan air volume value (m3 / h) and differential pressure (Pa), and repeat this cycle until the fan frequency of the fresh air unit increases to 50 Hz; Step S314, fit the seven groups of data to generate a flow curve Q = f(VSP) and a pressure curve H = g(VSP); Step 315, input the coefficients of the flow curve Q = f(VSP) and the pressure curve H = g(VSP) into the intelligent controller. The step-by-step test from 20 - 50 Hz covers the actual working range of the fan. Compared with only testing typical frequencies (such as 30 / 40 / 50 Hz), the model accuracy can be improved by more than 15%; the error of the fitting curve of the seven groups of data points is reduced to within ±3% compared with the linear interpolation method, ensuring the consistency between the control command and the on-site working conditions. 20 Hz is a measurement point taken to accurately measure the fan model, not the value of the air volume required to reach the minimum pressure. If the rotational speed corresponding to the minimum air volume value is less than 20 Hz, then the minimum rotational speed is 20 Hz (take the larger value of the two for comparison). One is to achieve precise control, and the controlled rotational speeds are all within the measured model range to avoid sudden drops in air volume and air pressure when operating at lower frequencies, resulting in non-meeting of requirements. The other is to protect the motor and avoid damaging the motor due to too low rotational speed.

[0025] Please refer to Figures 1 to 4 , preferably, in step S31, the minimum supply air volume Qmin is determined by the pre-established fan model of the fresh air unit. The calculation formulas for the air volume curve Q = f(VSP) and the pressure curve H = g(VSP) are: Q = f(VSP) = VCoeff1 * VSP + Vcoeff2 H = g(VSP) = PCoeff1 * VSP^2 + Pcoeff2 * VSP + Pcoeff3 In the formula: Q—the air volume of the fresh air unit fan, m3 / h; VSP—the operating frequency of the fresh air unit fan, Hz; VCoeff1 and Vcoeff2 are the coefficients of the air volume performance curve of the fresh air unit fan, obtained from on-site measurements; PCoeff1, Pcoeff2, and Pcoeff3 are the coefficients of the pressure performance curve of the fresh air unit fan, obtained from on-site measurements. Parametric modeling: The digitalization of the fan performance is achieved through the VCoeff1 / 2 and PCoeff1 / 2 / 3 coefficients, facilitating the real-time calculation of the optimal frequency by the upper computer 9, and improving the calculation efficiency by 50% compared to the traditional look-up table method; Quadratic pressure curve: H = g(VSP) uses a quadratic equation to better fit the actual characteristics of the centrifugal fan, reducing the error by 8 - 12% compared to the linear model. According to the system resistance equation H = KQ 2 , that is, g(VSP) = K[f(VSP)] 2 , solve this equation to obtain the operating frequency VSP of the fan, VSPmin ≤ VSP ≤ VSPmax. The adjustment range of the fan air volume is determined by the minimum air volume obtained above, and the maximum air volume is determined by the maximum operating frequency allowed by the fan. Substitute into the above formula to obtain the fan air volume adjustment range (Qmin~Qmax) and the pressure adjustment range (Hmin~Hmax); Please refer to Figures 1 to 4 , Preferably, in step S1, the heat exchanger 4 has a first heat exchange side, a second heat exchange side, and a third heat exchange side. The fresh air unit includes an evaporation end 1, a condensation end 3, and an intake fan 2; Connect the outlet end of the exhaust fan group 5 to the second heat exchange side of the heat exchanger 4, and connect the exhaust air on the second heat exchange side of the heat exchanger 4 to the condensation end 3 of the fresh air unit; Connect the inlet end of the fresh air unit to the first heat exchange side of the heat exchanger 4, and the incoming air of the fresh air unit passes through the first heat exchange side of the heat exchanger 4, the intake fan 2, and the evaporation end 1 and then enters the guest room. Preferably, in step S1, a water storage tank 11 is provided, and the heat exchange coil 12 in the water storage tank 11 is connected to the condensation end 3 of the fresh air unit, or the heat exchange coil 12 is connected to the third heat exchange side of the heat exchanger 4 for preparing domestic hot water; Connect the clean energy access ports 10 of the fresh air unit and the exhaust fan group 5 to the clean energy power generation system. Three-side heat exchange design: The first side pre-cools / pre-heats the fresh air, the second side recovers the exhaust air energy, and the third side is linked to the domestic hot water system, increasing the exhaust air waste heat utilization rate from the conventional 40% to over 65%; Strengthen the heat exchange temperature difference through the heat pump cycle of the fresh air unit, and still maintain a heat recovery efficiency of over 60% under extreme climates (such as -10°C / 40°C). Give priority to using the exhaust air waste heat for fresh air pretreatment, and use the remaining heat to prepare domestic hot water through the water storage tank 11 to maximize the energy utilization rate; Clean energy coupling: Connect to systems such as photovoltaic / ground source heat pump to further reduce the hotel's electricity cost. Preferably, the clean energy power generation system is a photovoltaic power generation system or a wind power generation system, both of which are mature existing technologies and will not be elaborated in detail and no specific protection requirements are made. The exhaust fan group 5 is composed of exhaust fans, and the outlet end of the exhaust fan is connected to the second heat exchange side of the heat exchanger 4.

[0026] Please refer to Figures 1 to 4 , preferably, in step S1, according to the seasonal change, the heat exchanger 4 provided between the air inlet section of the fresh air unit and the exhaust air section of the supply air unit can be switched to the summer working mode or the winter working mode; summer interfaces and winter interfaces are provided at both the condensation end 3 and the evaporation end 1 of the fresh air unit; when switched to the winter working mode, the exhaust air on the second heat exchange side of the heat exchanger 4 is connected to the winter interface of the evaporation end 1 of the fresh air unit, and the outlet of the inlet fan 2 is connected to the winter interface of the condensation end 3; when switched to the summer working mode, the exhaust air on the second heat exchange side of the heat exchanger 4 is connected to the summer interface of the condensation end 3 of the fresh air unit, and the outlet of the inlet fan 2 is connected to the summer interface of the evaporation end 1. Seasonal mode switching: The connection methods of the evaporation / condensation end 3 are optimized for winter and summer modes respectively, so that the summer cooling recovery rate is increased by 25% and the winter heat recovery rate is increased by 18%, solving the problem of poor seasonal adaptability of the traditional single mode. Interface separation design: Avoid the efficiency loss of 10-15% caused by the mixing of cold and hot media, and ensure that the annual comprehensive energy efficiency ratio (COP) > 3.5.

[0027] Please refer to Figures 1 to 4 , preferably, in step S1, a first air valve 6 is provided at the exhaust air outlet of each guest room, a second air valve 7 is provided at the air inlet of each guest room, the first air valve 6 and the second air valve 7 are electrically connected to the upper computer 9, the air inlet of each guest room is connected to the outlet end of the fresh air unit, and the exhaust air outlet of each guest room is connected to the inlet end of the exhaust fan 5 group. In step S3, after the upper computer 9 receives the power-taking information of the guest room power-taking system 8, the upper computer 9 controls the opening of the first air valve 6 and the second air valve 7 in the corresponding guest room. Through the electric control air valve, "the room moves with the people" is realized. The supply and exhaust air of the unoccupied guest rooms are closed, reducing the ineffective ventilation energy consumption by 30-50%. Linkage response mechanism: The valve is opened when power is taken, ensuring that the ventilation is started instantly when the personnel check in, and avoiding the 1-2 hour delay existing in the traditional time schedule control. The upper computer 9 includes a digital quantity input port BI, which monitors the switch feedback of the heat exchange system of the storage water tank 11, the photovoltaic power generation system, the integrated energy unit, and the fresh air unit; the digital quantity output port BO controls the switches of the above-mentioned equipment. The analog quantity input port AI monitors the operation parameter feedback of the exhaust fan and the fresh air fan, and the analog quantity output port AO controls the operation parameters of the above-mentioned equipment. The upper computer 9 and each device are connected to the intelligent regulator, and the upper computer 9 uniformly regulates and manages each device in the system.

[0028] Please refer to Figures 1 to 4, preferably, in step S1, all the guest rooms on the same floor of the hotel are grouped into the same area, and the total number of occupants in the guest rooms in the same area is sent to the host computer 9. The outlets of 5 sets of exhaust fans 5 on the same floor of the hotel are jointly connected to an exhaust duct; the guest rooms on the same floor share one or more fresh air units, and the inlet ends of the fresh air units on the same floor are all connected to the first heat exchange side of the same heat exchanger 4, and the exhaust duct is connected to the second heat exchange side of the same heat exchanger 4. Dividing the control unit by floor reduces 80% of the signal transmission nodes compared with single-room control, improving the system stability; intensive equipment layout: sharing fresh air units and exhaust ducts on the same floor reduces the initial investment by more than 30% and reduces the maintenance points by 50% at the same time.

[0029] Please refer to Figures 1 to 4 , preferably, in step S3, after the host computer 9 receives the occupancy information and power-taking information of the guest rooms on the floor of the area, it determines the total number of occupants M in all the guest rooms in the area. The host computer 9 adjusts the air supply volume Q of the fans of the fresh air units connected to the guest rooms in the current floor area according to the total number of occupants M in the guest rooms; in step S4, the host computer 9 regulates the exhaust air volume of 5 sets of exhaust fans 5 on the floor of the area according to the air supply volume Q of the fresh air units connected to the floor. Floor-level air volume regulation can automatically distribute the unit load according to the occupancy density, avoiding the inefficient operation of multiple units (such as changing from 2 units with 50% load to 1 unit with 100% load), saving 15-20% of the fan energy consumption; air volume coordination and matching: uniformly regulating the floor exhaust air volume to ensure the overall positive pressure gradient in the area and prevent local air leakage problems caused by the pressure difference imbalance between different guest rooms.

[0030] The working principle of the present invention is as follows: When a guest checks into a hotel room, the hotel room management system 13 will input the number of people. The room power supply system 8 can read whether there is power consumption in the room and transmit the number of people staying and consuming power in this area to the host computer 9. The host computer 9 can then adjust the fan speed of the fresh air unit to control the threshold of the air supply volume according to the number of people staying in the room and the room information. Furthermore, within this threshold range, it can supply air on demand according to the real-time fresh air feedback load of the hotel, thereby achieving precise control of the fresh air volume in hotel rooms. When there is power consumption in the rooms in this area and people are staying, the host computer 9 will turn on the fresh air unit, 5 groups of exhaust fans, the high-efficiency heat exchanger 4, the first air valve 6, and the second air valve 7. When no one is staying, the above-mentioned equipment will be turned off. The host computer 9 adjusts the air supply volume of the exhaust fan according to the air supply volume of the fresh air unit, making the fresh air volume slightly larger than the exhaust air volume to ensure a slightly positive pressure in the room and also reduce the entry of outdoor air. When the number of people in the rooms in this area decreases, the fan speeds of the fresh air unit and the 5 groups of exhaust fans will be correspondingly reduced. If the number of people increases, the fan speeds of the fresh air unit and the 5 groups of exhaust fans will be correspondingly increased. After a certain period of time (1 minute), the heat pump device of the fresh air unit will be turned on to cool the fresh air entering the room. When the room temperature is lower than the outdoor temperature, the exhaust air temperature is lower than the fresh air temperature, and the dynamic heat pipe can recover the energy of the exhaust air and pre-treat the fresh air. (During summer operation, the host computer 9 controls the fan speed of the condensing end 3 and the heat exchange system of the water storage tank 11 according to the fresh air load of the system and the temperature of the condensing end 3, maintaining a certain temperature difference range between the heat exchanger 4 and the condensing end 3, and recovering and eliminating the condensation heat generated by the fresh air load to prepare medium-temperature (about 35°C) domestic hot water. When the exhaust air temperature after heat recovery is lower than the outdoor fresh air, the exhaust air can also be sent to the condensing side of the fresh air unit to cool the condensing pipe using the remaining cold of the exhaust air. In winter, this side is the evaporation side, and the exhaust air temperature is higher than the outdoor temperature. The exhaust air can also be sent to this side to make full use of the waste heat of the exhaust air.)

[0031] It should be noted that: First, in the description of this application, it should be noted that unless otherwise specified and limited, the terms "installation", "connection", and "coupling" should be understood in a broad sense. It can be a mechanical connection or an electrical connection, or it can be the communication inside two components. It can be directly connected. "Upper", "lower", "left", "right", etc. are only used to represent the relative position relationship. When the absolute position of the object being described changes, the relative position relationship may change.

[0032] Second: In the drawings of the disclosed embodiments of the present invention, only the structures related to the disclosed embodiments are involved. Other structures can refer to the general design. Without conflict, the same embodiment and different embodiments of the present invention can be combined with each other.

[0033] Finally, the above description is only the preferred embodiment of the present invention. The protection scope of the present invention is not limited to the above embodiments. All technical solutions falling within the scope of the idea of the present invention belong to the protection scope of the present invention.

[0034] It should be noted that, for those of ordinary skill in the art, several improvements and refinements made without departing from the principles of the present invention shall also be regarded as falling within the scope of protection of the present invention.

Claims

1. A low-carbon ventilation control method for hotel guest rooms, comprising a hotel guest room management system, a fresh air unit and an exhaust air unit, and a guest room power supply system, characterized in that: Control by following the steps below: Step S1, connecting the hotel room management system, the fresh air unit, the exhaust fan unit and the guest room power supply system to the host computer, and setting a heat exchanger between the air inlet section of the fresh air unit and the exhaust section of the air supply unit to recover the cold or heat in the exhaust air of the exhaust fan unit; Step S2: The hotel room management system transmits the room check-in information to the host computer, and the room power supply system transmits the power supply information to the host computer; Step S3, after the host computer receives the guest room check-in information and the power supply information, the host computer determines the number of occupants M in the guest rooms in the area, and adjusts the fan air supply volume Q of the guest room fresh air unit in the current area according to the number of occupants M in the check-in information, and sets the minimum fan air supply volume of the fresh air unit to Qmin to meet the fresh air demand of N people. When the number of occupants M exceeds the preset value N, the fresh air volume is calculated according to the formula Q=Qmin+A×(M−N) and the air supply volume of the fresh air unit is controlled; A is the fresh air demand of each person; Step S4, the upper computer controls the exhaust volume of the exhaust fan group according to the air supply volume of the fresh air unit, so that the exhaust volume of the exhaust fan group is 65% to 90% of the air supply volume of the fresh air unit to maintain the positive pressure in the guest room.

2. A low-carbon ventilation control method for hotel rooms according to claim 1, characterized in that: In step S3, the air supply volume of the fresh air unit is determined by the following steps: step S31, establishing the flow curve Q=f(VSP) and pressure curve H=g(VSP) of the fan model of the fresh air unit through field testing; calculating the wind resistance of the air duct and the most unfavorable point of the air duct according to the installation trend of the air supply duct, and finding the minimum speed required for the fan of the fresh air unit at the most unfavorable point by looking up the table according to the fan model; Step S32: When there is a demand for fresh air when guests check in to the guest rooms in the current area, the fan of the fresh air unit is turned on at the set minimum speed. At this time, a minimum air supply volume Qmin is corresponding to meet the fresh air demand of N guests. When the number of guests M in the guest rooms in this area is greater than N, the fresh air fan increases the air supply volume. When the number of guests decreases, the air supply volume is reduced accordingly. When the number of guests M is not greater than N, Q1=Qmin; when the number of guests is greater than N, Q1=Qmin+A(MN). Q1——air supply volume of fresh air fan, m³ / h; Qmin——the minimum air supply volume of the fresh air fan, m³ / h, corresponding to the fresh air volume demand of N people; M——Number of people staying in guest rooms in the area, fresh air volume requirement per person Am³ / h. Step S33, the fresh air unit of the guest room in the current area is turned on, and the exhaust fan is turned on accordingly. The exhaust frequency of the exhaust fan is set according to the size of the bathroom, which is set to 5-10 times / h. The exhaust volume of the exhaust fan is set to Qrow. To ensure the positive pressure exhaust volume of the room, Qrow should be 70%-80% of the fresh air volume Q2, Q2=Qrow / (70%-80%); Step S34, according to the fresh air volume Q1 calculated in step S32 and the fresh air volume Q2 calculated in step S33, select the larger value as the actual air supply volume to set the air supply volume Q of the fresh air unit fan; substitute the air volume Q into the flow curve Q=f(VSP) and pressure curve H=g(VSP) of the fan model to calculate the operating frequency VSP required by the fresh air unit fan to set the speed of the fresh air unit fan.

3. A low-carbon ventilation control method for hotel rooms according to claim 2, characterized in that: In step S31, the establishment of the fan model includes the following steps: step S311, establishing the fan test frequency range as 20-50Hz; step S312, manually setting the frequency of the fresh air unit to 20Hz, measuring and recording the on-site fan air volume value and pressure difference; step S313, manually setting the fan frequency of the fresh air unit to increase by 5Hz, and recording the on-site fan air volume value and pressure difference, and repeating this cycle until the fan frequency of the fresh air unit increases to 50Hz; step S314, fitting the seven groups of data to generate a flow curve Q=f(VSP) and a pressure curve H=g(VSP); step 315, inputting the coefficients of the flow curve Q=f(VSP) and the pressure curve H=g(VSP) into the intelligent controller.

4. A low-carbon ventilation control method for hotel guest rooms according to claim 3, characterized in that: In step S31, the minimum air supply volume Qmin is determined by the fan model of the fresh air unit established in advance, and the air volume curve Q=f(VSP) and the pressure curve H=g(VSP) are calculated by the following formula: Q=f(VSP) = VCoeff1* VSP + Vcoeff2 H=g(VSP) = PCoeff1* VSP^2+ Pcoeff2* VSP+ Pcoeff3 Where: Q—air volume of fresh air unit fan, m3 / h; VSP—the operating frequency of the fan of the fresh air unit, Hz; VCoeff1, Vcoeff2—coefficients of the air volume performance curve of the fresh air unit fan, obtained based on on-site measurements; PCoeff1, Pcoeff2, Pcoeff3—coefficients of the fan pressure performance curve of the fresh air unit, obtained based on field measurements.

5. A low-carbon ventilation control method for hotel rooms according to claim 1, characterized in that: In step S1, the heat exchanger has a first heat exchange side, a second heat exchange side and a third heat exchange side, and the fresh air unit includes an evaporating end, a condensing end and an air inlet fan; the outlet end of the exhaust fan unit is connected to the second heat exchange side of the heat exchanger, and the exhaust air of the second heat exchange side of the heat exchanger is connected to the condensing end of the fresh air unit; the inlet end of the fresh air unit is connected to the first heat exchange side of the heat exchanger, and the air intake of the fresh air unit passes through the first heat exchange side of the heat exchanger, the air intake fan and the evaporating end and then enters the guest room.

6. A low-carbon ventilation control method for hotel rooms according to claim 5, characterized in that: In step S1, the heat exchanger arranged between the air inlet section of the fresh air unit and the air exhaust section of the air supply unit can also be switched to a summer working mode or a winter working mode according to seasonal changes; summer interfaces and winter interfaces are set at both the condensing end and the evaporating end of the fresh air unit; when switching to the winter working mode, the exhaust air on the second heat exchange side of the heat exchanger is connected to the winter interface of the evaporating end of the fresh air unit, and the outlet of the air inlet fan is connected to the winter interface of the condensing end; when switching to the summer working mode, the exhaust air on the second heat exchange side of the heat exchanger is connected to the summer interface of the condensing end of the fresh air unit, and the outlet of the air inlet fan is connected to the summer interface of the evaporating end.

7. A low-carbon ventilation control method for hotel rooms according to claim 6, characterized in that: In step S1, a water storage tank is set up, and the heat exchange coil in the water storage tank is connected to the condensing end of the fresh air unit, or the heat exchange coil is connected to the third heat exchange side of the heat exchanger to prepare domestic hot water; the clean energy inlet of the fresh air unit and the exhaust fan unit is connected to the clean energy power generation system.

8. A low-carbon ventilation control method for hotel rooms according to claim 1, characterized in that: In step S1, a first air valve is set at the exhaust outlet of each guest room, and a second air valve is set at the air inlet of each guest room. The first air valve, the second air valve and the upper computer are electrically connected, the air inlet of each guest room is connected to the outlet end of the fresh air unit, and the exhaust outlet of each guest room is connected to the inlet end of the exhaust fan unit. In step S3, after the upper computer receives the power supply information of the guest room power supply system, the upper computer controls the first air valve and the second air valve in the corresponding guest room to open.

9. A low-carbon ventilation control method for hotel rooms according to claim 1, characterized in that: In step S1, all guest rooms on the same floor of the hotel are classified into the same area, the total number of occupants in the guest rooms in the same area is sent to the host computer, and the outlets of the exhaust fan units on the same floor of the hotel are connected to an exhaust duct; the guest rooms on the same floor share one or more fresh air units, and the inlet ends of the fresh air units on the same floor are connected to the first heat exchange side of the same heat exchanger, and the exhaust ducts are connected to the second heat exchange side of the same heat exchanger.

10. A low-carbon ventilation control method for hotel guest rooms according to claim 9, characterized in that: In step S3, after the upper computer receives the guest room occupancy information and power supply information of the floor of the area, it determines the number of occupants M of all the guest rooms in the area, and adjusts the fan air supply volume Q of the fresh air group connected to the guest rooms in the current floor area according to the number of occupants M; in step S4, the upper computer adjusts the exhaust volume of the exhaust fan group on the floor of the area according to the air supply volume Q of the fresh air group connected to the floor.

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