A double-temperature-zone temperature-controlled air-cooled scroll water chiller

Abstract

This invention relates to a dual-temperature-zone controlled air-cooled scroll chiller unit, comprising a common base, a unit housing fixedly mounted on top of the common base, and a partition plate fixedly mounted inside the unit housing, dividing the interior of the unit housing into an upper heat dissipation chamber and a lower main unit chamber. Two independently operating fully enclosed scroll compressors are fixedly mounted inside the lower main unit chamber. Each fully enclosed scroll compressor includes a casing, an inlet valve on the side of the casing, an outlet valve on the top of the casing, and a motor fixedly mounted at the lower end of the casing. The output end of the motor is driven by a sealed drive component, and the top of the sealed drive component is driven by a moving scroll plate. This invention achieves stepless automatic adjustment of the compressor's gas delivery capacity, thereby adaptively matching the cooling capacity requirements of different loads in the dual-temperature zones, effectively reducing operating energy consumption under partial load, and simultaneously reducing mechanical shock and electrical losses caused by compressor start-up and shutdown.

Description

Technical Field

[0001] This invention relates to the technical field of air-cooled scroll chillers, specifically to an air-cooled scroll chiller with dual-temperature zone control. Background Technology

[0002] Dual-zone temperature-controlled air-cooled scroll chillers are widely used in industrial production scenarios such as electronics manufacturing, pharmaceuticals, chemicals, and injection molding. They can simultaneously output chilled water at two different temperatures to meet the differentiated cooling needs of different equipment and processes in the production process. They are key supporting equipment for ensuring the stability of production processes and improving product yield. With the dynamic changes in industrial production conditions, the heat load of the two temperature zones often fluctuates, placing high demands on the unit's load adaptability and operational efficiency.

[0003] Existing dual-temperature zone air-cooled scroll chiller units mostly use a constant-volume structure for their scroll compressors. They typically rely on compressor start-stop to match changes in heat load. Under high load conditions, the compressor runs continuously at full load, while under low load conditions, the compressor stops directly and restarts after the water temperature rises.

[0004] Because this adjustment method cannot adjust the compressor's gas delivery volume in real time according to the operating conditions, the unit's operating efficiency is low under partial load conditions. Furthermore, frequent start-stop of the compressor will generate significant mechanical shock and electrical losses. Long-term operation will easily aggravate component wear and shorten the overall service life of the equipment. Summary of the Invention

[0005] The purpose of this invention is to provide a dual-temperature-zone controlled air-cooled scroll chiller unit, which aims to improve the problem that scroll compressors in the prior art cannot adjust the compressor gas delivery volume in real time according to the operating conditions.

[0006] The objective of this invention is achieved through the following technical solution: a dual-temperature zone temperature-controlled air-cooled scroll chiller unit, comprising a common base for the unit, a unit outer shell fixedly mounted on the top of the common base, a unit middle partition fixedly mounted inside the unit outer shell, the unit middle partition dividing the interior of the unit outer shell into an upper heat dissipation cavity and a lower main unit cavity, and two independently operating fully enclosed scroll compressors fixedly mounted inside the lower main unit cavity.

[0007] The fully enclosed scroll compressor includes a casing, an inlet valve on the side of the casing, an outlet valve on the top of the casing, a motor fixedly installed at the lower end of the casing, a sealed drive component connected to the output end of the motor, a moving scroll plate connected to the top of the sealed drive component, a stationary scroll plate arranged above the moving scroll plate, and the lower end of the outlet valve facing the high-pressure zone at the center of the moving scroll plate and the stationary scroll plate.

[0008] The stationary vortex disk includes a fixed sealing ring, which is fixedly installed inside the upper part of the housing. A floating vortex disk is slidably installed inside the fixed sealing ring. The lower end of the tension spring is connected to the top of the floating vortex disk. Several sets of differential pressure relief valves are distributed circumferentially inside the floating vortex disk. As a further description of the above technical solution: the differential pressure relief valve assembly includes a valve cylinder, a conical plate is fixedly provided inside the valve cylinder, a sliding ring is slidably provided inside the valve cylinder corresponding to the lower part of the conical plate, a conical plug is fixedly provided at the center of the sliding ring, the conical plug cooperates with the central conical hole of the conical plate to achieve sealing, and a top high-pressure oil chamber is provided at the upper end of the housing corresponding to the upper part of the stationary vortex disk.

[0009] As a further description of the above technical solution: magnetic strips are provided on the contact surfaces of the sliding ring and the conical plate. The two magnetic strips form a preliminary locking structure through magnetic attraction. The bottom of the conical plug is rotatably connected to a turbine spray port, and the lower end of the turbine spray port faces the compression chamber between the moving scroll plate and the floating scroll plate.

[0010] As a further description of the above technical solution: the upper end of the differential pressure relief valve group is connected to the top high-pressure oil chamber, and the lower end of the differential pressure relief valve group is connected to the compression chamber between the moving scroll and the stationary scroll. The inner side of the housing is provided with a diversion mechanism corresponding to the outer side of the moving scroll. The diversion mechanism is used to receive the lubricating oil flowing out of the differential pressure relief valve group and guide the lubricating oil to the compression chamber and the bottom oil storage chamber.

[0011] As a further description of the above technical solution: the sealing drive component includes a main rotating shaft, the lower end of which is connected to the output end of the motor, and an eccentric shaft is fixedly connected to the upper end of the main rotating shaft. The outer side of the eccentric shaft is rotatably connected to the bottom center of the moving scroll plate through a ball bearing. A sealing box is fitted on the outer side of the main rotating shaft. The sealing box is filled with high-pressure gas to press the outer side of the main rotating shaft to prevent oil leakage. A fixed plate is also fixedly installed inside the housing, and the sealing box is located at the bottom of the fixed plate. Several eccentric steel balls are arranged in a ring between the top surface of the fixed plate and the bottom surface of the moving scroll plate.

[0012] As a further description of the above technical solution: the drainage mechanism includes a chassis, which is fixedly installed inside the housing and sleeved on the outside of the main rotating shaft. A rotating cylinder is rotatably installed above the chassis. Spiral fins are fixedly installed on the outer wall of the rotating cylinder, and a centering inner ring is fixedly installed on the inner wall of the rotating cylinder. A drive cylinder is fixedly installed on the outside of the main rotating shaft. Repulsive magnetic plates are embedded in both the outer wall of the drive cylinder and the inner wall of the centering inner ring. The two layers of repulsive magnetic plates are magnetically attracted to each other, and the rotating cylinder is driven to rotate synchronously and centerably by the rotational motion of the rotating vortex disk.

[0013] As a further description of the above technical solution: the lower end of the casing is provided with an oil lubrication mechanism, which includes an oil tank. The internal cavity of the oil tank forms a bottom oil storage chamber. A return groove is opened on the top surface of the oil tank. The return groove is used to receive the lubricating oil that flows back and guides it into the oil tank. A lifting pipe is provided between the top of the oil tank and the top high-pressure oil chamber. A one-way return valve group is provided between the bottom oil storage chamber and the top high-pressure oil chamber and is connected through the one-way return valve group. The one-way return valve group is configured to allow the lubricating oil in the bottom oil storage chamber to flow into the top high-pressure oil chamber in one direction only. The one-way return valve group includes a through ring fixedly installed on the top of the lifting pipe. A second conical plate is fixedly installed inside the through ring. A second conical plug is provided above the second conical plate. The second conical plate and the second conical plug cooperate to form a one-way sealing structure.

[0014] As a further description of the above technical solution: two sets of V-shaped finned tube air-cooled condensers are fixedly installed inside the upper heat dissipation cavity. The bottom of each set of V-shaped finned tube air-cooled condensers is connected to a condenser manifold and a high-pressure detection valve group. An axial flow fan exhaust duct is installed above each set of V-shaped finned tube air-cooled condensers at the top of the upper heat dissipation cavity. Two independent shell-and-tube evaporators, as well as a drying filter and throttling valve group, are also fixedly installed inside the lower main unit cavity. Chilled water inlet and outlet flange interfaces are connected to the side of each shell-and-tube evaporator. An electrical control box is fixedly installed on the upper side of one side of the unit casing. The unit's outer casing includes an outer panel. The side of the upper heat dissipation cavity is equipped with a vent plate corresponding to the air inlet side of the V-shaped finned tube air-cooled condenser. The vent plate is used to allow ambient air to enter the upper heat dissipation cavity to participate in heat exchange.

[0015] Compared with the prior art, the advantages of the present invention are as follows: 1. By driving the conical plug of the differential pressure relief valve group to slide back and forth along the inner wall of the valve cylinder through the suction pressure, the oil storage volume and oil pressure of the top high pressure oil chamber change dynamically with the heat load, driving the floating scroll to make a slight axial floating along the fixed sealing ring. Combined with the reset force of the tension spring and the automatic oil replenishment and pressure stabilization function of the one-way return oil valve group, the stepless automatic adjustment of the compressor's gas delivery volume is realized, thereby adaptively matching the cooling demand of different loads in the dual temperature zones, effectively reducing the operating energy consumption under partial load, and reducing the mechanical shock and electrical loss caused by compressor start-up and shutdown.

[0016] 2. The lubricating oil discharged through the differential pressure relief valve group is initially sprayed and distributed through the turbine spray nozzle. In conjunction with the main rotating shaft, the magnetic transmission of the inner and outer repulsive magnetic plates drives the rotating cylinder to rotate in a centered manner, driving the spiral fins to rotate synchronously and guide the flow. This allows the lubricating oil to slowly fall along the spiral channel and fully mix with the rising suction air to form a uniform oil mist. This lubricating medium evenly covers all moving parts such as the volute meshing surface, eccentric bearing, and eccentric steel ball, achieving forced lubrication throughout the entire path. This compensates for the defect of reduced oil return rate under low load conditions, avoids dry running of the compressor due to lack of oil, effectively reduces frictional wear of moving parts, and significantly extends the service life of the entire machine. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the main body of an embodiment of a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0018] Figure 2 This is a plan view of an embodiment of a dual-temperature-zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0019] Figure 3 This is a schematic diagram of the main body of a fully enclosed scroll compressor of a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0020] Figure 4 This is a schematic diagram of the structure of a fully enclosed scroll compressor for a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0021] Figure 5 This is a schematic diagram of the static scroll plate of a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0022] Figure 6 This is a schematic diagram of the sealing drive component of a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0023] Figure 7 This is a schematic diagram of the floating scroll of a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0024] Figure 8 This is a schematic diagram of the turbine spray nozzle of an air-cooled scroll chiller unit with dual-temperature zone temperature control proposed in this invention.

[0025] Figure 9 This is a schematic diagram of the flow diversion mechanism of a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0026] Figure 10 This is a schematic diagram of the oil lubrication mechanism of an air-cooled scroll chiller unit with dual-temperature zone control proposed in this invention.

[0027] Figure 11 This is a schematic diagram of the through-loop structure of a dual-temperature zone temperature-controlled air-cooled scroll chiller unit proposed in this invention.

[0028] Labeling Explanation: 1. Axial flow fan exhaust duct; 2. V-shaped finned tube air-cooled condenser; 3. Condenser manifold and high-pressure detection valve assembly; 4. Unit partition plate; 5. Chilled water inlet and outlet flange interfaces; 6. Shell and tube evaporator; 7. Fully enclosed scroll compressor; 71. Casing; 72. Inlet valve; 73. Outlet valve; 74. Motor; 75. Sealing drive component; 751. Main shaft; 752. Eccentric shaft; 753. Ball bearing I; 754. Sealing box; 755. Fixed plate; 756. Eccentric steel ball; 76. Moving scroll plate; 77. Stationary scroll plate; 771. Fixed sealing ring; 772. Floating scroll plate; 773. Valve 774. Cylinder; 775. Conical orifice plate one; 776. Sliding ring; 777. Conical plug one; 778. Magnetic strip; 779. Turbine spray nozzle; 78. Tension spring; 79. Drainage mechanism; 701. Chassis; 702. Rotating cylinder; 703. Spiral fins; 704. Centering inner ring; 705. Drive cylinder; 706. Repulsive magnetic plate; 707. Lubrication mechanism; 71. Oil tank; 72. Return channel; 793. Lifting pipe; 794. Through ring; 795. Conical orifice plate two; 796. Conical plug two; 8. Drying filter and throttling valve assembly; 9. Electrical control box; 10. Unit common base; 11. Ventilation plate; 12. Outer plate. Detailed Implementation

[0029] The present invention will now be described in detail with reference to the accompanying drawings and embodiments: Figures 1 to 11 The diagram shows an embodiment of a dual-temperature-zone controlled air-cooled scroll chiller provided by the present invention. The chiller includes a common base 10, which provides a stable installation support foundation for the entire unit, bearing the weight of all components and providing shock absorption and hoisting / transportation functions to ensure the stability of the unit during operation. A unit casing is fixedly mounted on the top of the common base 10, protecting all internal components, isolating them from external dust, moisture, and impurities, and reducing noise diffusion during operation, thus maintaining a stable internal operating environment. A partition 4 is fixedly mounted inside the unit casing, dividing the interior into an upper heat dissipation chamber and a lower main unit chamber. This physical separation of the hot and cold chambers prevents heat transfer from the upper heat dissipation chamber to the lower main unit chamber, preventing overheating of the main unit chamber components and ensuring that the operation of the two chambers does not interfere with each other.

[0030] The upper heat dissipation cavity is equipped with two sets of V-shaped finned tube air-cooled condensers 2. These condensers serve as the heat release end of the refrigeration cycle. Through the combination of fins and coils, they increase the heat exchange area with the air, enabling the condensation and heat release of the high-temperature gaseous refrigerant, thus converting the refrigerant from a gaseous state to a liquid state. Each set of V-shaped finned tube air-cooled condensers 2 is connected to a condenser manifold and a high-pressure detection valve group 3 at its bottom. These manifolds and valve group 3 collect and transport the condensed liquid refrigerant, while simultaneously monitoring the condensing pressure of the refrigeration system in real time. This provides pressure monitoring assurance for safe system operation and facilitates subsequent maintenance and pressure regulation.

[0031] Above each group of V-shaped finned tube air-cooled condensers 2, an axial flow fan exhaust duct 1 is installed at the top of the upper heat dissipation cavity. The axial flow fan exhaust duct 1 has an internal axial flow fan that provides forced convection power to the condenser, driving ambient air to flow quickly across the condenser fin surface, carrying away the heat released by the refrigerant, improving the heat exchange efficiency of the condenser, and accelerating the condensation process of the refrigerant. Inside the lower main unit cavity, two independently operating fully enclosed scroll compressors 7 are fixedly installed. The fully enclosed scroll compressors 7 serve as the core power source of the refrigeration system, compressing the low-pressure gaseous refrigerant and converting it into a high-temperature, high-pressure gaseous refrigerant, providing power for the entire refrigeration cycle. The two compressors operate independently and can respectively adapt to the different cooling capacity requirements of the dual temperature zones. The lower main unit cavity is also equipped with two independent shell-and-tube evaporators 6. The shell-and-tube evaporators 6 serve as the heat absorption end of the refrigeration cycle, realizing the heat exchange between the refrigerant and the chilled water. The liquid refrigerant absorbs the heat of the chilled water and vaporizes into a low-pressure gaseous state, completing the cooling process of the chilled water. The two evaporators operate independently, corresponding to the two chilled water circulation paths in the dual temperature zones.

[0032] The lower main unit cavity is also equipped with a drying filter and throttling valve assembly 8. This assembly 8 dries the condensed liquid refrigerant, filtering out impurities and moisture. Simultaneously, it reduces the pressure and temperature of the refrigerant through throttling, controlling the refrigerant flow into the evaporator and ensuring its heat exchange efficiency. Each shell-and-tube evaporator 6 has a chilled water inlet / outlet flange 5 connected to its side. These flanges connect the evaporator 6 to the external cooling load piping, facilitating chilled water output and return. The cooled chilled water is delivered to the load end, while the returned water, heated by heat absorption, is introduced into the evaporator for further cooling. An electrical control box 9 is fixed to the upper side of one side of the unit's casing. This box contains various controllers and electrical components, enabling the operation control of the two compressors, axial fan, and other components. It also integrates safety protection functions to ensure stable and safe operation of the unit.

[0033] The unit's outer casing includes an outer panel 12, which constitutes the main structure of the unit's outer casing, providing overall protection and sealing, ensuring the structural strength of the unit's outer casing, and isolating the external environment from the internal components. A vent plate 11 is provided on the side of the upper heat dissipation cavity corresponding to the air inlet side of the V-shaped finned tube air-cooled condenser 2. The vent plate 11 allows ambient air to enter the upper heat dissipation cavity to participate in heat exchange, ensuring smooth airflow, while simultaneously filtering large particulate impurities in the air to prevent impurities from adhering to the condenser fins and affecting heat exchange efficiency.

[0034] The fully enclosed scroll compressor 7 includes a casing 71. The casing 71 serves as the outer shell of the compressor, providing a mounting platform and sealed space for all internal components, preventing the entry of external impurities, and preventing leakage of internal refrigerant and lubricating oil, thus maintaining stable operating pressure and environment inside the compressor. An inlet valve 72 is located on the side of the casing 71. The inlet valve 72 controls the input of low-pressure gaseous refrigerant, ensuring a stable flow of refrigerant into the compression zone inside the compressor. It can also be closed during maintenance to isolate the compressor from the refrigeration piping. An outlet valve 73 is located on the top of the casing 71. The outlet valve 73 controls the output of the compressed high-temperature, high-pressure gaseous refrigerant, delivering it to the condenser for subsequent condensation. It can also be closed during maintenance to ensure safety. A motor 74 is fixedly installed at the lower interior of the casing 71. The motor 74 provides rotational torque for the compressor's operation and is the power input component, driving the internal transmission mechanism and compression components.

[0035] A sealed drive component 75 is connected to the output end of the motor 74. The sealed drive component 75 ensures stable torque transmission from the motor 74 while maintaining the internal sealing performance of the compressor, preventing refrigerant and lubricating oil leakage, and maintaining the internal pressure environment of the compressor. A moving scroll plate 76 is connected to the top of the sealed drive component 75. The moving scroll plate 76 and the stationary scroll plate 77 cooperate to form a compression chamber. The refrigerant is compressed through planetary trajectory translation, gradually compressing the low-pressure gaseous refrigerant into a high-temperature, high-pressure gaseous state. A stationary scroll plate 77 is positioned above the moving scroll plate 76. The stationary scroll plate 77 meshes with the moving scroll plate 76 to form multiple independent compression chambers, providing a sealed space for refrigerant compression and ensuring smooth operation of the compression process. The lower end of the discharge valve 73 is directly opposite the central high-pressure area of ​​the moving scroll plate 76 and the stationary scroll plate 77, ensuring that the compressed high-pressure refrigerant can be quickly and smoothly discharged from the compressor.

[0036] The stationary scroll plate 77 includes a fixed sealing ring 771, which is fixedly installed inside the upper part of the housing 71. The fixed sealing ring 771 provides sliding guidance and limitation for the floating scroll plate 772, ensuring that the floating scroll plate 772 can only float slightly axially, preventing radial offset and rotation. The floating scroll plate 772 is slidably mounted inside the fixed sealing ring 771. The floating scroll plate 772 adjusts the gap between the moving and stationary scroll plates through axial floating, thereby controlling the effective gas delivery of the compressor to adapt to different heat load requirements. The lower end of a tension spring 779 is connected to the top of the floating scroll plate 772. The tension spring 779 provides an upward reset force for the floating scroll plate 772. Under low load conditions, it pulls the floating scroll plate 772 up, reducing the gas delivery. Simultaneously, when the load increases, it works with oil pressure to smoothly reset the floating scroll plate 772. The floating scroll 772 has several sets of differential pressure relief valves distributed circumferentially inside. The differential pressure relief valves automatically open and close according to the change of suction pressure, control the oil discharge process of the top high-pressure oil chamber, and at the same time realize the spraying and distribution of lubricating oil, thus completing the capacity regulation and lubrication functions of the compressor.

[0037] The differential pressure relief valve assembly includes a valve cylinder 773. The valve cylinder 773 serves as the mounting carrier for the differential pressure relief valve assembly, providing sliding guidance and sealing space for the internal valve core components, ensuring stable valve operation. A conical orifice plate 774 is fixedly installed inside the valve cylinder 773. The conical orifice plate 774 cooperates with a conical plug 776 to achieve valve sealing and opening, controlling the flow of lubricating oil through the central conical orifice, and simultaneously providing initial guidance for the lubricating oil. A sliding ring 775 is slidably installed inside the valve cylinder 773 below the conical orifice plate 774. The sliding ring 775 drives the conical plug 776 to slide along the inner wall of the valve cylinder 773, realizing valve opening and closing and opening degree adjustment, while also supporting the installation of the magnetic strip 777, achieving a magnetic locking function. A conical plug 776 is fixedly installed at the center of the sliding ring 775. The conical plug 776 cooperates with the central conical orifice of the conical orifice plate 774 to achieve valve sealing and control the on / off state and flow rate of lubricating oil. The contact surfaces of the sliding ring 775 and the conical plate 774 are both equipped with magnetic strips 777. The two magnetic strips 777 form a preliminary locking structure through magnetic attraction, which helps the conical plug 776 to press the conical plate 774, ensuring the sealing performance of the valve under high load conditions and preventing lubricating oil leakage.

[0038] A turbine spray nozzle 778 is rotatably connected to the bottom of the conical plug 776. The turbine spray nozzle 778 delivers lubricating oil to the compression chamber of the moving and stationary scroll plates 77 in the form of a spray, ensuring that the lubricating oil is evenly distributed on the meshing surface of the scroll teeth, improving the lubrication effect, and preventing the lubricating oil from dripping. The lower end of the turbine spray nozzle 778 faces the compression chamber between the moving scroll plate 76 and the floating scroll plate 772, ensuring that the lubricating oil can accurately act on the lubrication parts of the compression area. The conical plug 776 and the central conical hole of the conical plate 774 cooperate to achieve a seal. A top high-pressure oil chamber is provided at the upper end of the housing 71, corresponding to the top of the stationary scroll plate 77. The top high-pressure oil chamber stores high-pressure lubricating oil, which applies a downward clamping force to the floating scroll plate 772 through oil pressure, ensuring the tight meshing of the moving and stationary scroll plates 77 under full load conditions, and at the same time providing an oil source for drain lubrication.

[0039] The upper end of the differential pressure relief valve assembly is connected to the top high-pressure oil chamber, ensuring that lubricating oil can enter the valve assembly from the top high-pressure oil chamber; the lower end of the differential pressure relief valve assembly is connected to the compression chamber between the moving scroll plate 76 and the stationary scroll plate 77, ensuring that the discharged lubricating oil can accurately enter the compression area for lubrication. Inside the housing 71, corresponding to the outer ring of the moving scroll plate 76, there is a flow guiding mechanism 78. The flow guiding mechanism 78 is used to receive the lubricating oil flowing out of the differential pressure relief valve assembly and guide the lubricating oil to the compression chamber and the bottom oil storage chamber, while realizing the mixing of lubricating oil and suction air, improving the uniformity of lubrication.

[0040] The sealing drive component 75 includes a main shaft 751, which transmits the rotational torque output by the motor 74 and drives the eccentric shaft 752 to perform eccentric rotational motion. It is the core transmission component inside the compressor. The lower end of the main shaft 751 is connected to the output end of the motor 74, and the upper end of the main shaft 751 is fixedly connected to the eccentric shaft 752. The eccentric shaft 752 converts the rotational motion of the main shaft 751 into the planetary translational motion of the moving scroll 76, providing power for the operation of the moving scroll 76 and ensuring the smooth operation of the compression process. The outer side of the eccentric shaft 752 is rotatably connected to the bottom center of the moving scroll 76 through a ball bearing 753. The ball bearing 753 reduces the frictional resistance between the eccentric shaft 752 and the moving scroll 76, ensuring the smooth operation of the moving scroll 76 and extending the service life of the components. A sealing box 754 is fitted around the outer side of the main rotating shaft 751. High-pressure gas is filled inside the sealing box 754 to press the outer side of the main rotating shaft 751 tightly, preventing oil leakage and achieving a seal between the main rotating shaft 751 and the housing 71, preventing refrigerant and lubricating oil leakage. A fixed plate 755 is also fixedly installed inside the housing 71, with the sealing box 754 located at the bottom of the fixed plate 755. The fixed plate 755 provides mounting support for the sealing box 754 and axial support for the moving scroll 76, ensuring the stability of the moving scroll 76's operating posture. Several eccentric steel balls 756 are arranged in a ring between the top surface of the fixed plate 755 and the bottom surface of the moving scroll 76. The eccentric steel balls 756 provide axial support and motion guidance for the moving scroll 76, maintaining its planetary translational posture, preventing radial offset and rotation, and reducing frictional losses.

[0041] The flow guiding mechanism 78 includes a chassis 781, which is fixedly installed inside the housing 71 and sleeved on the outside of the main rotating shaft 751. The chassis 781 provides mounting support and rotation limit for the rotating cylinder 782, ensuring its stable operation. The rotating cylinder 782 is rotatably mounted above the chassis 781. The rotating cylinder 782 drives the spiral fins 783 to rotate synchronously, realizing the guidance and distribution of lubricating oil, while ensuring the overall operational coordination of the flow guiding mechanism 78. The spiral fins 783 are fixedly mounted on the outer wall of the rotating cylinder 782. The spiral fins 783 extend the falling path of the lubricating oil, allowing the lubricating oil to fully mix with the rising low-pressure suction air to form a uniform oil mist, improving the uniformity of lubrication, and simultaneously guiding the lubricating oil to various lubrication points. A centering inner ring 784 is fixedly mounted on the inner wall of the rotating cylinder 782. The centering inner ring 784 achieves a magnetic transmission connection between the rotating cylinder 782 and the drive cylinder 785, ensuring the centered rotation of the rotating cylinder 782 and preventing it from deviating. A drive cylinder 785 is fixedly installed on the outer side of the main rotating shaft 751. The drive cylinder 785 rotates synchronously with the main rotating shaft 751. Through the magnetic attraction of the repulsive magnetic plate 786, it drives the centering inner ring 784 and the rotating cylinder 782 to rotate, providing power for the operation of the diversion mechanism 78. The outer wall of the drive cylinder 785 and the inner wall of the centering inner ring 784 are both embedded with repulsive magnetic plates 786. The two layers of repulsive magnetic plates 786 magnetically cooperate, driving the rotating cylinder 782 to rotate synchronously and centerably through contactless transmission, reducing mechanical friction and improving the smoothness of transmission. The rotation of the moving scroll plate 76 drives the rotating cylinder 782 to rotate synchronously and centerably.

[0042] An oil lubrication mechanism 79 is located at the lower end of the casing 71. This mechanism stores, returns, and transports lubricating oil, providing a stable oil source for the compressor's lubrication system. The oil lubrication mechanism 79 includes an oil tank 791. The internal cavity of the oil tank 791 forms a bottom oil storage chamber for storing lubricating oil, providing a source for the compressor's lubrication and hydraulic drive. A return channel 792 is formed on the top surface of the oil tank 791. This channel receives the lubricating oil that flows back down and guides it into the oil tank 791, achieving lubricating oil recovery and recycling, and maintaining a stable oil level in the bottom oil storage chamber. A lifting pipe 793 connects the top of the oil tank 791 to the top high-pressure oil chamber. The lifting pipe 793 transports lubricating oil between the bottom oil storage chamber and the top high-pressure oil chamber, replenishing the top high-pressure oil chamber with lubricating oil and ensuring the hydraulic drive function. A one-way return valve assembly is provided between the bottom oil storage chamber and the top high-pressure oil chamber and is connected through the one-way return valve assembly. The one-way return valve assembly is designed to allow lubricating oil in the bottom oil storage chamber to flow into the top high-pressure oil chamber in one direction only, to prevent the lubricating oil in the top high-pressure oil chamber from flowing back and to ensure the pressure stability of the top oil chamber.

[0043] The one-way return valve assembly includes a through ring 794 fixedly mounted on the top of the lifting pipe 793. The through ring 794 provides a mounting carrier for the second conical plate 795, ensuring the structural stability of the one-way return valve assembly. The second conical plate 795 is fixedly mounted inside the through ring 794. The second conical plate 795 cooperates with the second conical plug 796 to form a one-way sealing structure, controlling the one-way flow of lubricating oil. The second conical plug 796 is located above the second conical plate 795. The second conical plate 795 and the second conical plug 796 cooperate to form a one-way sealing structure, ensuring that lubricating oil can only flow from the bottom oil reservoir to the top high-pressure oil chamber, maintaining stable pressure in the top oil chamber.

[0044] Working principle: After the motor 74 is powered on and starts, it outputs rotational torque. The torque is transmitted to the main shaft 751 of the sealed drive component 75. The main shaft 751 drives the upper eccentric shaft 752 to perform eccentric rotation. The eccentric shaft 752 drives the moving scroll 76 to move along a planetary trajectory above the fixed disk 755 through the ball bearing 753. The eccentric steel balls 756 arranged around the top surface of the fixed disk 755 provide axial support and motion guidance for the moving scroll 76, maintain the operating posture of the moving scroll 76, and prevent radial offset and rotation. Low-pressure gaseous refrigerant enters the internal space of housing 71 through the intake valve 72 on the side of housing 71, and flows upward to the meshing area of ​​moving scroll 76 and stationary scroll 77. As the moving scroll 76 continues to rotate, the volume of multiple compression chambers distributed from the outer periphery to the center gradually decreases, and the low-pressure refrigerant is continuously compressed into a high-temperature and high-pressure gaseous state. Finally, the high-pressure refrigerant in all compression chambers gathers in the high-pressure area at the center of the moving and stationary scrolls, and is discharged from the compressor through the outlet valve 73 at the top of housing 71, completing a single refrigerant compression process.

[0045] When the heat load in the corresponding temperature zone is at a high level, the suction pressure entering the compressor is maintained at the rated high level. The high-pressure suction airflow acts on the lower end of the differential pressure relief valve assembly, applying an upward thrust to the sliding ring 775 and the conical plug 776. The upward thrust is superimposed on the magnetic attraction force of the two sets of magnetic strips 777, pushing the conical plug 776 upward to stick to the central conical hole of the conical plate 774, so that the entire differential pressure relief valve assembly is in a completely closed state, and the top high-pressure oil chamber above the stationary scroll plate 77 forms a closed space. Meanwhile, the lubricating oil in the bottom oil reservoir flows upward along the riser pipe 793 under the action of suction pressure. The upward oil pressure acts on the bottom of the conical plug 796, pushing it upward and disengaging it from the central conical hole of the conical plate 795. The one-way return valve group is activated, and the lubricating oil in the bottom oil reservoir continues to flow into the top high-pressure oil chamber. When the oil pressure in the top high-pressure oil chamber reaches equilibrium with the bottom pressure, the conical plug 796 falls back under the combined action of its own weight and the top oil pressure, re-sealing the central conical hole of the conical plate 795, and the one-way return valve group closes. The high-pressure lubricating oil in the top high-pressure oil chamber applies downward static pressure to the floating scroll 772, overcoming the upward tension of the tension spring 779, and pushing the floating scroll 772 downward along the inner wall of the fixed sealing ring 771 to the lowest limit. The scroll teeth of the floating scroll 772 are fully engaged with the scroll teeth of the moving scroll 76, all compression chambers remain completely sealed, and the compressor operates at full load with rated gas delivery.

[0046] When the heat load in the corresponding temperature zone decreases, the evaporation pressure on the evaporator side decreases synchronously, and the suction pressure of the compressor gradually decreases accordingly. The upward thrust acting on the lower end of the differential pressure relief valve assembly decreases synchronously. When the resultant force of the upward thrust and the magnetic attraction force is less than the downward force of the oil pressure in the top high-pressure oil chamber, the sliding ring 775 slides downwards along the inner wall of the valve cylinder 773, causing the conical plug 776 to disengage from the central conical hole of the conical plate 774, and the differential pressure relief valve assembly opens. The lubricating oil in the top high-pressure oil chamber flows downwards through the central conical hole of the conical plate 774 and is sprayed through the turbine spray nozzle 778 at the bottom of the conical plug 776 into the compression chamber between the moving scroll plate 76 and the floating scroll plate 772. As the lubricating oil in the top high-pressure oil chamber continues to flow out, the amount of oil stored in the chamber decreases, the oil pressure gradually drops, and the downward clamping force continues to weaken. The upward pulling force of the tension spring 779 gradually becomes dominant, pulling the floating scroll 772 to slide upward along the inner wall of the fixed sealing ring 771. A gap appears on the top surface of the scroll teeth of the moving and stationary scrolls, and some of the refrigerant in the compression chamber bypasses and flows back to the outer suction area through the tooth gap. The effective gas delivery volume of the compressor decreases synchronously with the decrease in oil pressure to match the current low-load cooling demand. The lower the heat load, the smaller the suction pressure value, the larger the opening of the differential pressure relief valve group, the higher the lifting height of the floating scroll 772, and the greater the reduction in gas delivery volume, achieving stepless capacity regulation throughout the process.

[0047] Part of the lubricating oil sprayed from the turbine nozzle 778 falls directly onto the meshing surface of the volute teeth of the moving volute disk 76 and the floating volute disk 772. As the volute disks move relative to each other, the oil spreads evenly along the tooth surface, forming a continuous oil film on the tooth tips and sides. This film fills the gap between the tooth tips, reduces gas bypass, and lubricates the meshing surface of the volute teeth. The remaining lubricating oil is thrown outwards by the centrifugal force generated by the rotation of the moving volute disk 76, landing on the surface of the spiral fins 783 of the flow guide mechanism 78. During the rotation of the main shaft 751, the drive cylinder 785 rotates synchronously with the main shaft 751. The two layers of repulsive magnetic plates 786 on the outer wall of the drive cylinder 785 and the inner wall of the centering inner ring 784 are driven by magnetic force to drive the centering inner ring 784 and the rotating cylinder 782 to rotate synchronously. The rotating cylinder 782 drives the spiral fins 783 on the outer wall to rotate synchronously. The falling lubricating oil flows slowly downward along the spiral channel of the spiral fins 783. During the flow, it comes into full contact with and mixes with the low-pressure suction air coming from the bottom up, forming a uniform oil mist that enters the compression chamber synchronously with the suction air, achieving uniform lubrication of the entire tooth surface. Some of the lubricating oil drips down along the guide structure on the spiral fins 783 to lubricate the moving parts such as the eccentric steel ball 756, the ball bearing 753, and the eccentric shaft 752 sleeve below.

[0048] After completing the full-path lubrication, the lubricating oil drips continuously downwards under gravity, eventually collecting at the oil lubrication mechanism 79 at the bottom of the housing 71. It then flows into the bottom oil storage chamber inside the oil tank 791 via the return channel 792 on the top surface of the oil tank 791. The slowing and guiding effect of the spiral fins 783 prevents the lubricating oil from directly impacting the bottom oil surface, reducing oil splashing and bubble generation, and maintaining a stable bottom oil surface. The splashed lubricating oil carried by the rotating scroll plate 76 slides down the inner wall of the housing 71 to the bottom and also flows into the bottom oil storage chamber via the return channel 792, completing a single internal lubrication cycle. Under low-load conditions, the differential pressure relief valve group continuously discharges oil, and the forced lubrication process continues synchronously, supplementing the lubrication gap caused by the decreased system return oil rate under low load.

[0049] As the heat load in the corresponding temperature zone gradually increases, the evaporation pressure on the evaporator side rises, and the compressor's suction pressure rises synchronously. The upward thrust acting on the lower end of the differential pressure relief valve assembly increases simultaneously, pushing the sliding ring 775 upwards along the valve cylinder 773. The conical plug 776 gradually approaches the central conical hole of the conical plate 774, the valve opening gradually decreases, and the top oil discharge decreases synchronously. When the suction pressure rises back to the rated threshold, the conical plug 776 completely presses against the conical plate 774, the differential pressure relief valve assembly closes, and the top high-pressure oil chamber stops discharging oil. At the same time, the pressure in the bottom oil storage chamber increases synchronously with the suction pressure, pushing the conical plug 796 to rise again. The one-way oil return valve group is opened, and the lubricating oil stored at the bottom is pressed back into the top high-pressure oil chamber by the air pressure. The oil storage in the chamber increases and the oil pressure gradually rises, overcoming the tension of the tension spring 779 and pushing the floating scroll 772 to slide downward. The gap between the scroll teeth gradually narrows, and the compressor's gas delivery volume steadily rises to the full load state, completing a complete capacity adjustment and lubrication cycle.

[0050] The high-temperature, high-pressure gaseous refrigerant discharged from the compressor outlet valve 73 enters the V-shaped finned tube air-cooled condenser 2 in the upper heat dissipation chamber through external pipelines. The fan in the axial flow fan exhaust duct 1 operates synchronously, driving ambient air to enter the upper heat dissipation chamber through the vent plate 11. The air sweeps laterally across the fins and coils of the V-shaped finned tube air-cooled condenser 2, carrying away the heat carried by the refrigerant and condensing the high-temperature gaseous refrigerant into a normal-temperature, high-pressure liquid refrigerant. The condenser manifold and high-pressure detection valve group 3 collect the condensed liquid refrigerant and monitor the condensation pressure in real time. After being dried, filtered, and depressurized and cooled by the throttling valve group 8, the liquid refrigerant enters the corresponding shell-and-tube evaporator 6, where it exchanges heat with the chilled water. After absorbing the heat from the chilled water, it vaporizes into a low-pressure gaseous refrigerant, which is then drawn back into the compressor to complete the refrigeration cycle. The cooled chilled water is delivered to the external cooling load through the chilled water inlet / outlet flange 5, and the return water, after absorbing heat and heating up, flows back to the shell-and-tube evaporator 6 for further cooling through the other flange. The two independent compressor refrigeration circuits correspond to two independent chilled water circulations, each operating independently according to the load of its corresponding temperature zone, without interfering with each other, thus achieving independent temperature control in two temperature zones.

Claims

1. A dual-temperature-zone temperature-controlled air-cooled scroll chiller unit, comprising a common base (10), characterized in that: The unit's common base (10) is fixedly provided with a unit shell, and a unit middle partition (4) is fixedly provided inside the unit shell. The unit middle partition (4) divides the inside of the unit shell into an upper heat dissipation cavity and a lower main unit cavity. Two independently operating fully enclosed scroll compressors (7) are fixedly provided inside the lower main unit cavity. The fully enclosed scroll compressor (7) includes a housing (71), an inlet valve (72) is provided on the side of the housing (71), an outlet valve (73) is provided on the top of the housing (71), a motor (74) is fixedly provided at the lower end of the interior of the housing (71), a sealing drive component (75) is driven to the output end of the motor (74), a moving scroll plate (76) is driven to the top of the sealing drive component (75), a stationary scroll plate (77) is provided above the moving scroll plate (76), and the lower end of the outlet valve (73) is directly opposite the high pressure zone at the center of the moving scroll plate (76) and the stationary scroll plate (77). The stationary vortex disk (77) includes a fixed sealing ring (771), which is fixedly installed inside the upper part of the housing (71). A floating vortex disk (772) is slidably installed inside the fixed sealing ring (771). The lower end of the tension spring (779) is connected to the top of the floating vortex disk (772). Several sets of differential pressure relief valves are distributed circumferentially inside the floating vortex disk (772).

2. The air-cooled scroll chiller unit with dual-temperature zone control according to claim 1, characterized in that: The differential pressure relief valve assembly includes a valve cylinder (773), a conical plate (774) is fixedly provided inside the valve cylinder (773), a sliding ring (775) is slidably provided inside the valve cylinder (773) corresponding to the lower part of the conical plate (774), a conical plug (776) is fixedly provided at the center of the sliding ring (775), and the conical plug (776) cooperates with the central conical hole of the conical plate (774) to achieve sealing. The upper part of the housing (71) is provided with a top high-pressure oil chamber corresponding to the upper part of the stationary vortex disk (77).

3. The air-cooled scroll chiller unit with dual-temperature zone control according to claim 2, characterized in that: The contact surfaces of the sliding ring (775) and the cone plate (774) are provided with magnetic strips (777). The two magnetic strips (777) form a preliminary locking structure through magnetic attraction. The bottom of the cone plug (776) is rotatably connected to a turbine spray port (778). The lower end of the turbine spray port (778) faces the compression chamber between the moving scroll plate (76) and the floating scroll plate (772).

4. The air-cooled scroll chiller unit with dual-temperature zone control according to claim 2, characterized in that: The upper end of the differential pressure relief valve assembly is connected to the top high-pressure oil chamber, and the lower end of the differential pressure relief valve assembly is connected to the compression chamber between the moving scroll plate (76) and the stationary scroll plate (77). The inner side of the housing (71) is provided with a diversion mechanism (78) corresponding to the outer side of the moving scroll plate (76). The diversion mechanism (78) is used to receive the lubricating oil flowing out of the differential pressure relief valve assembly and guide the lubricating oil to the compression chamber and the bottom oil storage chamber.

5. The air-cooled scroll chiller unit with dual-temperature zone control according to claim 1, characterized in that: The sealing drive component (75) includes a main shaft (751), the lower end of which is connected to the output end of the motor (74), and an eccentric shaft (752) is fixedly connected to the upper end of the main shaft (751). The outer side of the eccentric shaft (752) is rotatably connected to the bottom center of the moving scroll plate (76) through a ball bearing (753). A sealing box (754) is fitted on the outer side of the main shaft (751). High-pressure gas is filled into the sealing box (754) to press the outer side of the main shaft (751) to prevent oil leakage. A fixed plate (755) is also fixedly installed inside the housing (71), and the sealing box (754) is located at the bottom of the fixed plate (755). Several eccentric steel balls (756) are arranged in a ring between the top surface of the fixed plate (755) and the bottom surface of the moving scroll plate (76).

6. The air-cooled scroll chiller unit with dual-temperature zone control according to claim 4, characterized in that: The drainage mechanism (78) includes a chassis (781), which is fixedly installed inside the housing (71) and sleeved on the outside of the main rotating shaft (751). A rotating cylinder (782) is rotatably installed above the chassis (781). Spiral fins (783) are fixedly installed on the outer wall of the rotating cylinder (782). A centering inner ring (784) is fixedly installed on the inner wall of the rotating cylinder (782). A drive cylinder (785) is fixedly installed on the outside of the main rotating shaft (751). A repulsive magnetic plate (786) is embedded in both the outer wall of the drive cylinder (785) and the inner wall of the centering inner ring (784). The inner and outer repulsive magnetic plates (786) are magnetically attracted to each other, and the rotating cylinder (782) is driven to rotate synchronously and centerably by the rotation of the rotating disk (76).

7. The air-cooled scroll chiller unit with dual-temperature zone control according to claim 1, characterized in that: The lower end of the housing (71) is provided with an oil lubrication mechanism (79), which includes an oil tank (791). The internal cavity of the oil tank (791) forms a bottom oil storage chamber. A return groove (792) is provided on the top surface of the oil tank (791). The return groove (792) is used to receive the lubricating oil that flows back and guides it into the oil tank (791). A lifting pipe (793) is provided between the top of the oil tank (791) and the top high-pressure oil chamber. A single-channel valve is provided between the bottom oil storage chamber and the top high-pressure oil chamber. The return oil valve group is connected to the one-way return oil valve group. The one-way return oil valve group is configured to allow lubricating oil in the bottom oil storage chamber to flow into the top high-pressure oil chamber in one direction only. The one-way return oil valve group includes a through ring (794) fixedly installed at the top of the lifting pipe (793). A second conical plate (795) is fixedly installed inside the through ring (794). A second conical plug (796) is installed above the second conical plate (795). The second conical plate (795) and the second conical plug (796) cooperate to form a one-way sealing structure.

8. The air-cooled scroll chiller unit with dual-temperature zone control according to claim 1, characterized in that: The upper heat dissipation cavity is fixedly equipped with two sets of V-shaped finned tube air-cooled condensers (2). The bottom of each set of V-shaped finned tube air-cooled condensers (2) is connected to a condenser manifold and a high-pressure detection valve group (3). The top of the upper heat dissipation cavity is equipped with an axial flow fan exhaust duct (1) above each set of V-shaped finned tube air-cooled condensers (2). The lower main unit cavity is also fixedly equipped with two independent shell-and-tube evaporators (6) and a drying filter and throttling valve group (8). The side of each shell-and-tube evaporator (6) is connected to a chilled water inlet and outlet flange interface (5). An electrical control box (9) is fixedly installed on the upper side of one side of the unit casing. The unit casing includes an outer panel (12), and the side of the upper heat dissipation cavity is provided with a vent plate (11) corresponding to the air inlet side of the V-shaped finned tube air-cooled condenser (2). The vent plate (11) is used to allow ambient air to enter the upper heat dissipation cavity to participate in heat exchange.

Images