Valve assembly for a compressor and compressor

Abstract

This invention provides a valve assembly for a compressor and a compressor. The compressor includes a valve assembly for communicating with a gas supply device to supply gaseous refrigerant to the compressor. The valve assembly includes a mounting member and at least one valve plate. The mounting member has at least one outlet for gaseous refrigerant to flow out. Each valve plate includes a tail portion fixedly connected to the mounting member, a head portion for opening and closing one outlet, and a connecting portion connecting the head and tail portion. The outlet is circular, and the head is polygonal. This invention uses a polygonal valve plate head to close a circular outlet, which can reduce the vacuum negative pressure formed on the mounting member due to the overlap between the valve plate head and the periphery of the outlet while ensuring valve plate sealing and head rigidity, thereby reducing gas supply pressure loss.

Description

Technical Field

[0001] This utility model relates to a vapor compression refrigeration system, and more particularly to a valve assembly for a compressor and a compressor. Background Technology

[0002] In existing air conditioning technology, single-stage gas injection and enthalpy-increasing rotor compressors are generally divided into two types: piston cutting gas injection method and one-way valve gas injection method.

[0003] Piston-cutting gas replenishment has the advantages of simple structure and high reliability. However, due to structural limitations, the gas replenishment port of piston-cutting gas replenishment is generally designed to be relatively small, resulting in high gas replenishment resistance and limited gas replenishment volume. Moreover, piston-cutting gas replenishment has high requirements for the design position of the gas replenishment port. The optimal position of the gas replenishment port varies under different operating conditions. This means that piston-cutting gas replenishment cannot adapt well to changes in operating conditions. In particular, it cannot achieve the optimal gas replenishment volume when facing a wide range of operating conditions, and gas backflow will occur to varying degrees.

[0004] Compared to piston-cutting gas replenishment, one-way valve gas replenishment offers advantages such as larger replenishment volume, less gas backflow, and stronger adaptability to all operating conditions, making it widely used. However, the head of the gas replenishment one-way valve is typically designed in an arc shape because the arc shape has better machining capabilities and more uniform head rigidity. But to improve the sealing performance and reduce deformation of the gas replenishment valve, the diameter of the circular head of the gas replenishment one-way valve needs to be larger than the diameter of the outer arc of the protruding gas replenishment port. When the gas replenishment one-way valve is closed, the gap between the area of ​​the valve head protruding from the gas replenishment port and the gas replenishment valve seat will be filled with refrigerant oil, creating a vacuum. The gas replenishment valve requires a large pressure differential to open, which results in a significant gas replenishment pressure loss and is detrimental to improving gas replenishment capacity.

[0005] To increase the amount of supplemental air, the flow cross-sectional area of ​​the supplemental air inlet is usually increased, the rigidity of the intermediate connection of the supplemental air valve is reduced, or the lift of the supplemental air valve is increased. Increasing the flow cross-sectional area of ​​the supplemental air inlet can reduce flow resistance and increase the amount of supplemental air to some extent. However, a larger flow cross-sectional area requires a larger supplemental air valve to increase the rigidity of the valve head and reduce deformation to ensure sealing. This results in a greater pressure difference between the two ends of the supplemental air valve to overcome the vacuum negative pressure before the valve opens (the valve opens with a delay, and excessively high supplemental air pressure is detrimental to heat exchange in the air conditioning system's economizer), leading to a reduction in effective supplemental air time and hindering the improvement of supplemental air capacity. Reducing the rigidity of the connection between the head and tail of the supplemental air valve can... Reducing the pressure difference required for the gas supply valve to open during compressor gas supply increases the gas supply volume (by improving the effective gas supply duration and the heat exchange efficiency of the air conditioning system's economizer). However, reducing the stiffness of the gas supply valve connection will slow down the closing speed of the gas supply valve. When the pressure in the cylinder compression chamber is greater than the gas supply pressure, the delayed closing of the gas supply valve causes the high-pressure gas in the cylinder compression chamber to flow back outward from the gas supply port, which will also reduce the gas supply capacity to some extent. Under the condition that the stiffness of the gas supply valve connection is constant, increasing the lift of the gas supply baffle will cause the gas supply valve to close late and the compressed gas to flow back.

[0006] Taking all factors into consideration, the design needs to provide a valve assembly and compressor for the compressor that can reliably increase the amount of supplemental gas. Utility Model Content

[0007] One objective of the first aspect of this utility model is to overcome at least one technical defect in the prior art and provide a valve assembly for a compressor.

[0008] A further objective of the first aspect of this invention is to reduce the pressure loss during gas replenishment.

[0009] Another further objective of the first aspect of this utility model is to improve the opening and closing response speed and sealing reliability of the valve plate.

[0010] A second aspect of this invention aims to provide a compressor having a make-up air valve assembly.

[0011] According to a first aspect of the present invention, a valve assembly for a compressor is provided, characterized in that it comprises:

[0012] The mounting component forms at least one outlet for the outflow of gaseous refrigerant; and

[0013] At least one valve disc, each valve disc including a tail portion fixedly connected to the mounting member, a head portion for opening and closing one of the air outlets, and a connecting portion connecting the head portion and the tail portion; wherein...

[0014] The air outlet is circular; and

[0015] The head is polygonal.

[0016] This utility model uses a polygonal valve head to close a circular air outlet, which can reduce the vacuum negative pressure formed on the mounting part due to the overlap between the valve head and the periphery of the air outlet while ensuring the valve sealing and head rigidity, thereby reducing the air replenishment pressure loss.

[0017] Optionally, the number of sides of the head is greater than or equal to 5.

[0018] This invention sets the head of the valve plate as a polygon with 5 or more sides. The sharp edges of the polygon can increase the rigidity of the head and reduce deformation, thereby improving the service life of the valve plate.

[0019] Optionally, the shortest distance between the vertex of the angle projected by the head onto the opening plane of the air outlet and the edge of the air outlet is 0.8mm to 1.6mm; and / or

[0020] The opening diameter of the air outlet is 2.5mm to 4mm.

[0021] This invention sets the apex of the valve head to protrude from the outlet by 0.8mm to 1.6mm. Compared to the existing circular valve head that protrudes more than 3mm from the outlet, this effectively reduces the area of ​​negative pressure formed between the valve head and the outlet periphery while ensuring a seal, thus effectively reducing the pressure loss of the replenishment gas. Setting the outlet opening diameter in the range of 2.5mm to 4mm allows for a suitable replenishment gas speed, reduces refrigerant flow resistance, reduces valve noise, maintains stable operation of the refrigeration system, and can also be used in conjunction with the polygonal valve head of this invention to achieve the optimal configuration of comprehensive sealing performance, structural strength, and replenishment gas volume.

[0022] Optionally, the valve assembly further includes:

[0023] At least one limiting baffle, each of the limiting baffles being disposed on the side of one of the valve plates away from the mounting member, fixed to the mounting member and including a limiting portion with a free end for limiting the lift of one of the heads.

[0024] This invention provides a limiting baffle for the valve plate to restrict the head lift, which can control the movement trajectory of the valve plate and accurately control the air supply flow, avoiding problems such as tilting and collision of the valve plate, and improving the opening and closing response speed and sealing reliability of the valve plate.

[0025] Optionally, the limiting portion is circular; and

[0026] The center of the limiting part is closer to the tail than the center of the air outlet.

[0027] This invention sets the limiting part of the limiting baffle to a circle, which helps to reduce the stickiness of lubricating oil between the head of the polygonal valve plate and the limiting part, ensures the response speed of the valve plate, and avoids valve plate sealing failure. Furthermore, the center of the limiting part is set between the center of the air outlet and the tail, which can reduce the flow resistance of gaseous refrigerant when the valve plate head is in the open state and improve the gas replenishment efficiency.

[0028] Optionally, the surface of the limiting baffle facing away from the air outlet is a plane parallel to the opening of the air outlet; and / or

[0029] The surface of the limiting baffle near the air outlet includes an arcuate surface corresponding to the connecting part and the head, and the arcuate surface is configured to extend away from the mounting member in the direction from the connecting part to the head.

[0030] This invention sets the surface of the limiting baffle away from the mounting part as a plane parallel to the opening of the air outlet, which can reduce the space occupied by the limiting baffle in the compressor, improve the structural compactness of the compressor, and facilitate the processing and positioning of the limiting baffle; setting the surface of the limiting baffle, at least the connecting part and the head of the valve plate, as an arc surface can realize the flexible contact between the valve plate and the limiting baffle during the opening process, reduce valve plate noise, and form a streamlined refrigerant flow path.

[0031] Optionally, the projection of the limiting part on the opening plane of the air outlet completely covers the head; and / or

[0032] The limiting part is configured such that the lift of the head from closing the air outlet to opening the air outlet is 0.8mm to 1.2mm.

[0033] This invention sets the limiting part of the limiting baffle to completely cover the head, which not only effectively prevents the valve from opening excessively, but also forms a rigid barrier to the outlet when the valve is closed, preventing refrigerant from flowing back through the outlet and lubricating oil from accumulating at the outlet. The lift of the valve from the closed state to the open state is limited to the range of 0.8mm to 1.2mm, which can take into account both the refrigerant flow resistance and the valve closing speed, and achieve the optimization of the air supply.

[0034] According to a second aspect of the present invention, a compressor is provided, characterized in that it includes any of the valve assemblies described above.

[0035] The compressor of this invention uses valve plates and limit baffles of special shape and size, which have excellent opening and closing response speed and sealing reliability, effectively reducing the flow pressure loss of gaseous refrigerant and improving the working performance of the compressor.

[0036] Optionally, the valve assembly is used to communicate with a gas supply device to supply gaseous refrigerant to the compressor.

[0037] The compressor of this invention uses a valve assembly to replenish gaseous refrigerant to the compressor, which can optimize the amount of gas replenished and improve the compressor's working capacity and energy efficiency.

[0038] Optionally, the compressor further includes:

[0039] A first cylinder and a second cylinder, wherein the mounting component is disposed between the first cylinder and the second cylinder, serving as a partition separating the first cylinder and the second cylinder; wherein,

[0040] There are two air outlets and two valve plates, with the openings of the two air outlets facing the first cylinder and the second cylinder, respectively.

[0041] This invention uses a valve assembly as a partition between two cylinders to replenish air to both cylinders, reducing the number of parts, achieving structural integration and space optimization, which is conducive to modular assembly and reduces the production cost of the compressor. Moreover, when the air replenishment circuit is open, the two valve plates can open and close alternately with the piston movement, stabilizing the flow rate of the gaseous refrigerant and improving the operational reliability of the compressor.

[0042] The above and other objects, advantages and features of this utility model will become more apparent to those skilled in the art from the following detailed description of specific embodiments of this utility model in conjunction with the accompanying drawings. Attached Figure Description

[0043] The following sections will describe some specific embodiments of the present invention in a detailed manner by way of example and not limitation, with reference to the accompanying drawings. The same reference numerals in the drawings denote the same or similar parts or components. Those skilled in the art should understand that these drawings are not necessarily drawn to scale. In the drawings:

[0044] Figure 1 This is a schematic structural diagram of a refrigeration system according to an embodiment of the present invention;

[0045] Figure 2 yes Figure 1 Schematic top view of the central valve assembly;

[0046] Figure 3 It is along Figure 2 A schematic cross-sectional view taken by the cutting line AA in the diagram;

[0047] Figure 4 yes Figure 3 A schematic top view of the valve plate;

[0048] Figure 5 yes Figure 3A schematic top view of the middle limit baffle;

[0049] Figure 6 yes Figure 5 A schematic side view of the limiting baffle shown;

[0050] Figure 7 This is a schematic structural diagram of a control circuit according to an embodiment of the present invention;

[0051] Figure 8 This is a schematic flowchart of a control method for a refrigeration system according to an embodiment of the present invention.

[0052] Figure label:

[0053] Refrigeration system 100;

[0054] Compressor 110; Housing 111; Motor 112; Stator 112a; Rotor 112b; Crankshaft 113; Main bearing 114; Auxiliary bearing 115; First cylinder 116; Second cylinder 117;

[0055] Condenser 120; First throttling element 130; Evaporator 140; Gas-liquid separator 150; Second throttling element 160; Air supply tank 170; Solenoid valve 180; Economizer 190;

[0056] Valve assembly 200; mounting part 210; air supply channel 211; air outlet 212; valve plate 220; tail 221; head 222; connecting part 223; limit baffle 230; limit part 231; fastener 240;

[0057] Controller 310; processing unit 311; storage unit 312; computer program 313; temperature sensor 320; exhaust pressure sensor 330; intake pressure sensor 340. Detailed Implementation

[0058] Figure 1 This is a schematic structural diagram of a refrigeration system 100 according to an embodiment of the present invention. See also... Figure 1 The refrigeration system 100 generally includes a compressor 110, a condenser 120, a first throttling element 130 and an evaporator 140 connected in sequence to form a refrigeration circuit.

[0059] The compressor 110 is configured to draw in the low-temperature, low-pressure gaseous refrigerant discharged from the evaporator 140 and compress the low-temperature, low-pressure gaseous refrigerant into a high-temperature, high-pressure gaseous refrigerant; the condenser 120 is configured to dissipate heat and condense the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 110 into a low-temperature, high-pressure liquid refrigerant; the first throttling element 130 is configured to depressurize the low-temperature, high-pressure liquid refrigerant discharged from the condenser 120 into a low-temperature, low-pressure liquid refrigerant; and the evaporator 140 is configured to absorb heat and evaporate the low-temperature, low-pressure liquid refrigerant discharged from the first throttling element 130 into a low-temperature, low-pressure gaseous refrigerant.

[0060] The refrigeration system 100 may also include a gas-liquid separator 150. The gas-liquid separator 150 may be connected in series between the evaporator 140 and the compressor 110 to separate and store the liquid refrigerant produced by the evaporator 140.

[0061] The refrigeration system 100 may also include a gas supply device for supplying gaseous refrigerant to the compressor 110.

[0062] In some embodiments, the air replenishment device may include a second throttling element 160, an air replenishment tank 170, and a solenoid valve 180.

[0063] The second throttling element 160 and the gas supply tank 170 can be connected sequentially to the compressor 110 and the condenser 120 to form a gas supply circuit. The high-pressure liquid refrigerant output from the condenser 120 is reduced to a medium-pressure state through the second throttling element 160 and then enters the gas supply tank 170. Due to the sudden drop in pressure, part of it evaporates into a gaseous state to supply the compressor 110.

[0064] The solenoid valve 180 can be connected in series between the condenser 120 and the second throttling element 160 to switch the gas supply circuit on and off, so as to supply gaseous refrigerant to the compressor 110 when the gas supply circuit is open.

[0065] The heat exchange between the condenser 120 and the first throttling element 130, and between the second throttling element 160 and the air supply tank 170 forms an economizer 190 to improve system operating efficiency and save energy.

[0066] The compressor 110 generally includes a housing 111, a motor 112, a crankshaft 113, a main bearing 114, a secondary bearing 115, and at least one cylinder. In this invention, "at least one" refers to one, two, or more than two cylinders.

[0067] The motor 112, crankshaft 113, main bearing 114, auxiliary bearing 115, and cylinder can all be housed in the housing 111. The cylinder is configured to communicate with the gas-liquid separator 150, and the housing 111 is configured to communicate with the condenser 120.

[0068] The motor 112 may include a stator 112a and a rotor 112b rotatably connected to the stator 112a. The stator 112a is fixedly connected to the housing 111, and the crankshaft 113 is fixedly connected to the rotor 112b to rotate under the drive of the motor 112.

[0069] Each cylinder is slidably connected to a vane, which is used to divide the internal space of the cylinder into an intake chamber and an exhaust chamber.

[0070] The crankshaft 113 may include at least one eccentric part, each eccentric part may be fitted with a piston, and the piston may be configured to abut or connect with a sliding vane, so as to change the size of the intake chamber and the exhaust chamber under the drive of the crankshaft 113, thereby realizing the intake and exhaust of the corresponding cylinder.

[0071] The main bearing 114 can be located between the motor 112 and the cylinder, and the auxiliary bearing 115 can be located on the side of the cylinder away from the main bearing 114.

[0072] Figure 2 yes Figure 1 Schematic top view of the central valve assembly 200; Figure 3 It is along Figure 2 A schematic cross-sectional view taken by section line AA. See also Figure 2 and Figure 3 The compressor 110 may also include a gas replenishment valve assembly 200 for communicating with a gas replenishment tank 170 to replenish gaseous refrigerant to the cylinder.

[0073] The air replenishment valve assembly 200 includes a mounting member 210 and at least one valve plate 220. The mounting member 210 may have an air replenishment passage 211 communicating with the air replenishment tank 170 and at least one air outlet 212 for gaseous refrigerant to flow out.

[0074] Figure 4 yes Figure 3 Schematic top view of the middle valve plate 220. See also Figure 3 and Figure 4 Each valve plate 220 may include a tail portion 221 fixedly connected to the mounting member 210, a head portion 222 for opening and closing an outlet 212, and a connecting portion 223 connecting the head portion 222 and the tail portion 221. When the piston is in the intake state, the head portion 222 automatically opens the outlet 212 under the action of air pressure; when the piston is in the exhaust state, the head portion 222 automatically returns to close the outlet 212. The tail portion 221 may be fixedly connected to the mounting member 210 by a fastener 240.

[0075] The air outlet 212 can be circular. For example, it can be a perfect circle, an ellipse, or other arc-shaped structure.

[0076] In some embodiments, the head 222 may be polygonal. For example, quadrilateral, pentagonal, or hexagonal.

[0077] This utility model uses a polygonal valve plate 220 with its head 222 closing a circular air outlet 212. This can ensure the sealing of the valve plate 220 and the rigidity of its head 222, while reducing the vacuum negative pressure formed on the mounting part 210 due to the overlap between the head 222 of the valve plate 220 and the periphery of the air outlet 212, thereby reducing the loss of air replenishment pressure.

[0078] In some further embodiments, the number of sides of the head 222 may be greater than or equal to 5, i.e., at least pentagonal.

[0079] In this invention, the head 222 of the valve plate 220 is set as a polygon with a number of sides greater than or equal to 5. The edges of the polygon can increase the rigidity of the head 222 and reduce deformation, thereby improving the service life of the valve plate 220.

[0080] In some further embodiments, the shortest distance between the vertex of the corner of the head 222 projected onto the opening plane of the air outlet 212 and the edge of the air outlet 212 can be 0.8 mm to 1.6 mm. For example, 0.8 mm, 1 mm, 1.2 mm, 1.4 mm or 1.6 mm.

[0081] This invention sets the apex of the head 222 of the valve plate 220 to protrude from the air outlet 212 within the range of 0.8mm to 1.6mm. Compared with the prior art where the head 222 of the circular valve plate 220 protrudes more than 3mm from the air outlet 212, this invention can effectively reduce the area of ​​negative pressure formed between the head 222 of the valve plate 220 and the periphery of the air outlet 212 while ensuring sealing, thus effectively reducing the loss of air replenishment pressure.

[0082] In some further embodiments, the opening diameter of the air outlet 212 may be 2.5 mm to 4 mm. For example, 2.5 mm, 3 mm, 3.5 mm or 4 mm.

[0083] This invention sets the opening diameter of the air outlet 212 within the range of 2.5mm to 4mm, which can obtain a suitable air replenishment speed, reduce refrigerant flow resistance, reduce valve plate 220 noise, maintain stable operation of the refrigeration system 100, and can also cooperate with the head 222 of the polygonal valve plate 220 of the specific size of this invention to achieve the optimal configuration of comprehensive sealing performance, structural strength and air replenishment volume.

[0084] Figure 5 yes Figure 3 A schematic top view of the middle limit baffle 230; Figure 6 yes Figure 5 A schematic side view of the limiting baffle 230 shown. See also Figure 3 , Figure 5 and Figure 6In some embodiments, the valve assembly 200 may also include at least one limiting baffle 230.

[0085] Each limit baffle 230 may be disposed on the side of a valve plate 220 away from the mounting member 210, fixed to the mounting member 210 and including a limit portion 231 with a free end for limiting the lift of a head 222. The limit baffle 230 may be fixed to the mounting member 210 with the valve plate 220 using a fastener 240.

[0086] This utility model provides a limiting baffle 230 for the valve plate 220 to limit the lift of the head 222, which can control the movement trajectory of the valve plate 220 and accurately control the air supply flow, avoid problems such as tilting and collision of the valve plate 220, and improve the opening and closing response speed and sealing reliability of the valve plate 220.

[0087] Mounting member 210 may be formed with at least one mounting groove, and the bottom wall of each mounting groove may be formed with an air outlet 212. Limiting baffle 230 may be substantially embedded in the mounting groove to improve the structural compactness of valve assembly 200.

[0088] In some further embodiments, the limiting portion 231 may be circular.

[0089] The present invention sets the limiting part 231 of the limiting baffle 230 to be circular, which helps to reduce the stickiness of lubricating oil between the head 222 of the polygonal valve plate 220 and the limiting part 231, ensures the response speed of the valve plate 220, and avoids the valve plate 220 sealing failure.

[0090] In some further embodiments, the center of the limiting portion 231 may be closer to the tail portion 221 than the center of the air outlet 212. That is, the vertical distance between the central axis of the fastener 240 and the center of the air outlet 212 is L1, and the vertical distance between the central axis of the fastener 240 and the center of the limiting portion 231 is L2, where L1 is greater than L2.

[0091] The present invention sets the center of the limiting part 231 between the center of the air outlet 212 and the tail 221, which can reduce the flow resistance of gaseous refrigerant when the head 222 of the valve plate 220 is in the open state and improve the gas replenishment efficiency.

[0092] In some further embodiments, the surface of the limiting baffle 230 facing away from the air outlet 212 may be a plane parallel to the opening of the air outlet 212.

[0093] This invention sets the surface of the limiting baffle 230 away from the mounting part 210 as a plane parallel to the opening of the air outlet 212, which can reduce the space occupied by the limiting baffle 230 in the compressor 110, improve the structural compactness of the compressor 110, and facilitate the processing and positioning of the limiting baffle 230.

[0094] In some further embodiments, the surface of the limiting baffle 230 near the air outlet 212 may include an arcuate surface corresponding to the connection portion 223 and the head 222, the arcuate surface being configured to extend away from the mounting member 210 in the direction from the connection portion 223 to the head 222.

[0095] This invention sets the surface of the limiting baffle 230, at least corresponding to the connecting part 223 and the head 222 of the valve plate 220, as an arc surface, which enables the valve plate 220 to make flexible contact with the limiting baffle 230 during the opening process, reduces the noise of the valve plate 220, and forms a streamlined refrigerant flow path.

[0096] The surface of the limiting baffle 230 opposite to the tail 221 can be a plane parallel to the mounting member 210, so as to facilitate the installation and positioning of the limiting baffle 230.

[0097] In some further embodiments, the projection of the limiting portion 231 onto the opening plane of the air outlet 212 can completely cover the head 222.

[0098] In this invention, the limiting part 231 of the limiting baffle 230 is set to completely cover the head 222 by projection. This not only effectively prevents the valve plate 220 from being over-opened, but also forms a rigid barrier to the air outlet 212 when the valve plate 220 is in the closed state, preventing the refrigerant from flowing back through the air outlet 212 and the lubricating oil from accumulating at the air outlet 212.

[0099] In some further embodiments, the limiting part 231 may be configured such that the lift H of the head 222 from the closed air outlet 212 to the open air outlet 212 is 0.8 mm to 1.2 mm. For example, 0.8 mm, 0.9 mm, 1 mm, 1.1 mm, or 1.2 mm. The lift H is the distance between the center of the air outlet 212 and the limiting surface of the limiting baffle 230 in the direction perpendicular to the air outlet 212.

[0100] This invention limits the lift of the valve plate 220 from the closed state to the open state to a range of 0.8mm to 1.2mm, which can take into account both the refrigerant flow resistance and the closing speed of the valve plate 220, thereby optimizing the amount of gas replenishment.

[0101] In some embodiments, the number of cylinders may be two, namely a first cylinder 116 and a second cylinder 117. The mounting member 210 may be disposed between the first cylinder 116 and the second cylinder 117 as a partition separating the first cylinder 116 and the second cylinder 117.

[0102] The number of air outlets 212, valve plates 220, and limit baffles 230 can all be two. The openings of the two air outlets 212 can face the first cylinder 116 and the second cylinder 117 respectively.

[0103] The air supply channel 211 can partially penetrate the mounting member 210 in the thickness direction, so as to directly form two coaxial air outlets 212 at both ends of the air supply channel 211.

[0104] This invention uses the valve assembly 200 as a partition between two cylinders to replenish air to both cylinders, reducing the number of parts, achieving structural integration and space optimization, which is conducive to modular assembly and reduces the production cost of the compressor 110. Moreover, when the air replenishment circuit is open, the two valve plates 220 can open and close alternately with the piston movement, stabilizing the flow rate of the gaseous refrigerant and improving the operational reliability of the compressor 110.

[0105] Of course, as will be understood by those skilled in the art, the valve assembly 200 of this utility model can also be used as an exhaust valve for the cylinder to exhaust gas into the housing 111 of the compressor 110, and the cylinder can be used as an installation component 210.

[0106] Figure 7 This is a schematic structural diagram of a control circuit according to an embodiment of the present invention. See also... Figure 1 and Figure 7 The refrigeration system 100 may further include a controller 310. The controller 310 may include a processing unit 311 and a storage unit 312. The storage unit 312 stores a computer program 313, which, when executed by the processing unit 311, is used to implement the control method of this embodiment of the present invention.

[0107] In some embodiments, the processing unit 311 may be configured to, upon receiving a start command to start the compressor 110, acquire the temperature of the compressor 110, and, if the temperature of the compressor 110 is less than or equal to a preset temperature threshold, input a preset heating voltage to the compressor 110 to heat the windings of the motor 112 of the compressor 110; if the temperature of the compressor 110 is greater than the preset temperature threshold, input a preset start voltage to the compressor 110 to start the compressor 110 normally. For example, the preset heating voltage may be less than or equal to 12V; the preset temperature threshold may be 25°C; and both the stator 112a and rotor 112b of the motor 112 may be provided with windings.

[0108] Upon receiving the start command of the compressor 110, the refrigeration system 100 of this invention first heats the windings of the motor 112 to raise the temperature of the compressor 110 before starting the compressor 110 normally, even when the temperature of the compressor 110 is low. This not only ensures high heating efficiency but also avoids the problem of excessive load on the motor 112 and accelerated wear of moving parts such as bearings and pistons caused by lubricating oil being discharged from the compressor 110 with the refrigerant at low temperature. Furthermore, it prevents delayed opening or closing or jamming of the gas injection valve 220, or even valve 220 malfunction (such as seal failure or blockage of the gas injection channel 211), reduces fatigue damage to the valve 220, avoids undesirable increases in system energy efficiency, and enables the system to adapt to complex operating conditions.

[0109] In some further embodiments, the refrigeration system 100 may also include a temperature sensor 320 disposed at the bottom of the compressor 110 for sensing the temperature at the location of the compressor 110 housing 111 corresponding to the bottom oil sump. The temperature of the compressor 110 used to determine whether to preheat the compressor 110 may be the temperature at the location of the compressor 110 housing 111 corresponding to the bottom oil sump.

[0110] This invention uses the temperature of the bottom of the outer casing 111 of the compressor 110 to determine whether the compressor 110 needs to be preheated, which can accurately assess the impact of the lubricating oil condition on the operation of the compressor 110 and improve the start-up speed of the compressor 110.

[0111] In some further embodiments, after the compressor 110 is started normally, the processing unit 311 may also be configured to determine whether the compressor 110 is overloaded, and if the compressor 110 is overloaded, control the gas supply device to supply gaseous refrigerant to the compressor 110.

[0112] This invention replenishes gaseous refrigerant to the compressor 110 when it is overloaded. By adjusting the refrigerant flow rate, it can improve the circulation and lubrication effect of the lubricating oil, reduce the temperature of the motor 112, optimize the circulation efficiency, and improve the service life and safety performance of the refrigeration system 100.

[0113] In some further embodiments, the processing unit 311 may also be configured to determine whether the compressor 110 is overloaded based on its operating frequency. Specifically, the processing unit 311 is configured to determine whether the operating frequency of the compressor 110 is greater than or equal to a preset frequency threshold; if so, it determines that the compressor 110 is overloaded. For example, the preset frequency threshold may be 30 Hz (Hertz).

[0114] This invention determines whether gaseous refrigerant needs to be added to the compressor 110 based on the compressor 110's frequency. It can achieve real-time judgment of workload without adding additional sensors, and has low hardware cost and simple control logic.

[0115] In some further embodiments, the refrigeration system 100 may also include an exhaust pressure sensor 330 and an intake pressure sensor 340 for sensing the exhaust pressure and intake pressure of the compressor 110, respectively.

[0116] The processing unit 311 can also be configured to determine whether the compressor 110 is overloaded based on the ratio of the discharge pressure to the suction pressure of the compressor 110. Specifically, the processing unit 311 is configured to determine whether the ratio of the discharge pressure to the suction pressure of the compressor 110 is greater than or equal to a preset pressure ratio threshold; if so, it determines that the compressor 110 is overloaded. For example, the preset pressure ratio threshold can be 3.

[0117] This invention determines whether gaseous refrigerant needs to be added to the compressor 110 based on the ratio of the compressor's discharge pressure to its suction pressure. This allows for a more direct reflection of the compressor 110's workload and avoids control failures caused by abnormal electrical parameters.

[0118] In some further embodiments, the processing unit 311 may also be configured to determine whether the compressor 110 is overloaded based on the operating frequency of the compressor 110 and the ratio of the discharge pressure to the suction pressure of the compressor 110. That is, if either the operating frequency is greater than or equal to a preset frequency threshold or the ratio of the discharge pressure to the suction pressure is greater than or equal to a preset pressure ratio threshold, the compressor 110 is determined to be overloaded, so as to balance response speed and control reliability.

[0119] Figure 8 This is a schematic flowchart illustrating a control method for a refrigeration system 100 according to an embodiment of the present invention. See also... Figure 8 The control method of this utility model for the refrigeration system 100 may include the following steps:

[0120] Step S802: Receive the start command to start compressor 110 and obtain the temperature of compressor 110;

[0121] Step S804: When the temperature of compressor 110 is less than or equal to a preset temperature threshold, a preset heating voltage is input to compressor 110 to heat the motor 112 winding of compressor 110 to heat compressor 110.

[0122] Step S806: When the temperature of compressor 110 is greater than the preset temperature threshold, input the preset starting voltage to compressor 110 to start compressor 110 normally.

[0123] Upon receiving the start command of the compressor 110, the control method of this utility model first heats up the windings of the motor 112 to raise the temperature of the compressor 110 before starting the compressor 110 normally, even when the temperature of the compressor 110 is low. This not only has high heating efficiency and avoids the problem of excessive load on the motor 112 and accelerated wear of moving parts such as bearings and pistons caused by the lubricating oil being discharged from the compressor 110 with the refrigerant due to low temperature, but also prevents the gas replenishment valve 220 from opening and closing delayed or stuck, or even malfunctioning (such as seal failure or blockage of the gas replenishment channel 211), reduces fatigue damage to the valve 220, avoids undesirable increases in system energy efficiency, and enables the system to adapt to complex working conditions.

[0124] The control strategy of this utility model, combined with the one-way air supply valve plate 220, can reduce the wear of the valve plate 220 and avoid abnormal air supply caused by the failure of the sealing performance of the valve plate 220. It also reduces the requirement for the overlap area between the valve plate 220 and the periphery of the outlet 212, and can ensure the reliability of the compressor 110 operation while reducing the size of the valve plate 220 head 222.

[0125] In some embodiments, in step S802, the temperature of the compressor 110 can be the temperature of the housing 111 of the compressor 110 at the location corresponding to the bottom oil sump, so as to accurately assess the impact of the lubricating oil condition on the operation of the compressor 110 and improve the start-up speed of the compressor 110.

[0126] In some embodiments, the method further includes the following after step S806:

[0127] Step S808: Determine if compressor 110 is overloaded;

[0128] Step S810: When the compressor 110 is overloaded, control the gas supply device to supply gaseous refrigerant to the compressor 110.

[0129] This invention replenishes gaseous refrigerant to the compressor 110 when it is overloaded. By adjusting the refrigerant flow rate, it can improve the circulation and lubrication effect of the lubricating oil, reduce the temperature of the motor 112, optimize the circulation efficiency, and improve the service life and safety performance of the refrigeration system 100.

[0130] In some further embodiments, step S808 may include:

[0131] Determine whether the operating frequency of compressor 110 is greater than or equal to the preset frequency threshold. If so, determine that compressor 110 is overloaded.

[0132] This invention determines whether gaseous refrigerant needs to be added to the compressor 110 based on the compressor 110's frequency. It can achieve real-time judgment of workload without adding additional sensors, and has low hardware cost and simple control logic.

[0133] In some further embodiments, step S808 may include:

[0134] Determine whether the ratio of the discharge pressure to the suction pressure of compressor 110 is greater than or equal to a preset pressure ratio threshold. If so, determine that compressor 110 is overloaded.

[0135] This invention determines whether gaseous refrigerant needs to be added to the compressor 110 based on the ratio of the compressor's discharge pressure to its suction pressure. This allows for a more direct reflection of the compressor 110's workload and avoids control failures caused by abnormal electrical parameters.

[0136] In some further embodiments, step S808 may include:

[0137] Determine whether the operating frequency of compressor 110 is greater than or equal to a preset frequency threshold, or whether the ratio of the discharge pressure to the intake pressure of compressor 110 is greater than or equal to a preset pressure ratio threshold. If either condition is met, determine that compressor 110 is overloaded, so as to balance response speed and control reliability.

[0138] Therefore, those skilled in the art should recognize that although many exemplary embodiments of the present invention have been shown and described in detail herein, many other variations or modifications conforming to the principles of the present invention can be directly determined or derived from the disclosure of the present invention without departing from the spirit and scope of the present invention. Therefore, the scope of the present invention should be understood and recognized as covering all such other variations or modifications.

Claims

1. A valve assembly for a compressor, characterized in that, include: The mounting component forms at least one outlet for the outflow of gaseous refrigerant. and At least one valve disc, each valve disc including a tail portion fixedly connected to the mounting member, a head portion for opening and closing one of the air outlets, and a connecting portion connecting the head portion and the tail portion; wherein... The air outlet is circular; and The head is polygonal.

2. The valve assembly according to claim 1, characterized in that, The number of sides of the head is greater than or equal to 5.

3. The valve assembly according to claim 1, characterized in that, The shortest distance between the vertex of the angle projected onto the opening plane of the air outlet and the edge of the air outlet is 0.8mm to 1.6mm; and / or The opening diameter of the air outlet is 2.5mm to 4mm.

4. The valve assembly according to claim 1, characterized in that, Also includes: At least one limiting baffle, each of the limiting baffles being disposed on the side of one of the valve plates away from the mounting member, fixed to the mounting member and including a limiting portion with a free end for limiting the lift of one of the heads.

5. The valve assembly according to claim 4, characterized in that, The limiting part is circular; and The center of the limiting part is closer to the tail than the center of the air outlet.

6. The valve assembly according to claim 4, characterized in that, The surface of the limiting baffle that faces away from the air outlet is a plane parallel to the opening of the air outlet; and / or The surface of the limiting baffle near the air outlet includes an arcuate surface corresponding to the connecting part and the head, and the arcuate surface is configured to extend away from the mounting member in the direction from the connecting part to the head.

7. The valve assembly according to claim 4, characterized in that, The projection of the limiting part on the opening plane of the air outlet completely covers the head; and / or The limiting part is configured such that the lift of the head from closing the air outlet to opening the air outlet is 0.8mm to 1.2mm.

8. A compressor, characterized in that, Includes the valve assembly as described in any one of claims 1-7.

9. The compressor according to claim 8, characterized in that, The valve assembly is used to communicate with the gas supply device to supply gaseous refrigerant to the compressor.

10. The compressor according to claim 9, characterized in that, Also includes: A first cylinder and a second cylinder, wherein the mounting component is disposed between the first cylinder and the second cylinder, serving as a partition separating the first cylinder and the second cylinder; wherein, There are two air outlets and two valve plates, with the openings of the two air outlets facing the first cylinder and the second cylinder, respectively.

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