A refrigerant pressure stabilizing and storing auxiliary device for multi-model general refrigeration systems

Abstract

The application relates to the field of refrigerant storage tank equipment, in particular to a multi-model universal refrigeration system refrigerant pressure-stabilizing storage auxiliary device, which comprises a tank body, liquid storage cavities and liquid outlet cavities are arranged on the two sides of the tank body, a floating plate and a piston plate two are slidably connected in the liquid outlet cavities, a piston plate one is slidably connected in the lower part of the liquid storage cavity, a top spring one is fixedly connected to the bottom of the piston plate one, the top spring one is fixedly connected to the bottom of the liquid storage cavity, a communication seat is fixedly connected to the middle part between the liquid storage cavity and the liquid outlet cavity, the traditional single-space liquid storage tank is changed into a double-cavity type design, the liquid storage cavity is used to receive the gas-liquid two-phase refrigerant input from the condenser, the communication seat is used for variable communication, the liquid refrigerant is guided into the liquid outlet cavity, the pressure in the liquid outlet cavity is kept stable, and the output quantity is prevented from continuously changing due to the internal pressure fluctuation of the liquid storage tank when the refrigerant is output through the liquid outlet pipe.

Description

Technical Field

[0001] This invention relates to the field of refrigerant storage tank equipment, and more particularly to a refrigerant pressure stabilizing and storage auxiliary device for a multi-model universal refrigeration system. Background Technology

[0002] Refrigeration systems typically include components such as compressors, condensers, receivers, expansion valves, and evaporators. The refrigerant is compressed by the compressor and condensed by the condenser before entering the receiver for temporary storage. It is then supplied to the subsequent expansion valve and evaporator. In the prior art, receivers typically store and exchange heat for the refrigerant by setting up a containment cavity and a heat exchange structure. For example, CN116839106A discloses a receiver and an air conditioning system having it, which uses a containment cavity and heat exchange tubes to exchange heat for the stored refrigerant to meet the operating requirements of the refrigeration system.

[0003] However, in actual operation, the refrigeration system is affected by factors such as the model, operating load, and ambient temperature, causing fluctuations in the refrigerant input and output, which in turn causes fluctuations in the liquid level and pressure inside the receiver. When the internal pressure of the receiver changes significantly, it can easily lead to instability in the subsequent liquid supply pressure, changing the refrigerant supply state at the expansion valve and thus affecting the throttling stability of the expansion valve. Simultaneously, the refrigerant may exist in a two-phase state when entering the receiver; the gaseous refrigerant occupies the liquid storage space and may cause discontinuous liquid refrigerant supply. Furthermore, under high refrigerant circulation speeds, the condensation state of the refrigerant after passing through the condenser is easily affected by instantaneous load changes, and some refrigerant may not be fully condensed. Existing receivers have limited capacity to further cool this gaseous refrigerant. Moreover, the heat exchange process of traditional receivers usually lacks direct linkage with the actual refrigerant circulation state of the refrigeration system, making it difficult to maintain a relatively stable refrigerant storage and supply state under different operating conditions. Therefore, we propose a refrigerant pressure stabilizing and liquid storage auxiliary device for multi-model universal refrigeration systems to solve the above-mentioned problems. Summary of the Invention

[0004] The purpose of this invention is to address the shortcomings of the prior art by proposing a refrigerant pressure stabilization and liquid storage auxiliary device for a multi-model universal refrigeration system.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is as follows: a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system, comprising a tank body, wherein a liquid storage chamber and a liquid outlet chamber are respectively provided on both sides inside the tank body; a float plate and a second piston plate are slidably connected inside the liquid outlet chamber; a first piston plate is slidably connected to the lower part of the liquid storage chamber; a first top spring is fixedly connected to the bottom of the first piston plate; a connecting seat is fixedly connected in the middle between the liquid storage chamber and the liquid outlet chamber; a connecting flow channel is transversely penetrating the middle of the connecting seat; the connecting flow channel is used to connect the liquid storage chamber and the liquid outlet chamber; a reserved sliding cavity perpendicular to the connecting flow channel is provided in the middle of the connecting seat; a valve core is slidably connected inside the reserved sliding cavity; the valve core consists of an upper column section, an inverted cone section, a lower column section, and a bottom plate from top to bottom; the valve core is used to adjust the connection state of the connecting flow channel; and the bottom of the reserved sliding cavity is connected to... The system has a connecting hole, with a bottom connecting pipe fixedly connected to the bottom of the connecting hole. The bottom of the bottom connecting pipe is fixedly connected to the bottom of the liquid storage chamber. A top spring is fixedly connected to the top of the reserved sliding cavity. A straight through hole penetrating the top wall of the connecting seat is connected to the top of the reserved sliding cavity. A guide pipe is fixedly connected to the upper part of the liquid storage chamber. A uniformly distributed inverted conical tube is fixedly connected to the bottom of the guide pipe. The ends of the guide pipes all penetrate the side wall of the liquid storage chamber and are fixedly connected to the top of the liquid outlet chamber. A connecting plate is fixedly connected to the inner side of the guide pipe. A connecting pipe is fixedly connected to the middle of the connecting plate. A guide vane is provided inside the connecting pipe. The bottom of the shaft of the guide vane is set as a corrugated section. An elastic spring is provided inside the corrugated section. A base frame is fixedly connected to the bottom of the corrugated section. A uniformly distributed flexible tube is fixedly connected to the outer periphery of the base frame. A ball is fixedly connected to the end of each flexible tube. A connecting spring is installed inside each flexible tube.

[0006] Preferably, an inlet pipe is fixedly connected to one side of the top of the tank, and an outlet pipe is fixedly connected to the other side of the top of the tank.

[0007] Preferably, the top inlet of the liquid inlet pipe is used to connect to the condenser, and the bottom outlet of the liquid inlet pipe is connected to the top of the connecting pipe.

[0008] Preferably, the top outlet of the liquid outlet pipe is used to connect to the expansion valve, and the bottom inlet of the liquid outlet pipe is located at the bottom of the liquid outlet chamber for extracting liquid refrigerant from the bottom of the liquid outlet chamber.

[0009] Preferably, the interior of the tank is filled with an insulation layer between the storage chamber and the outlet chamber, and a reserved opening is provided on one side of the insulation layer, which is located at the top of the outlet chamber.

[0010] Preferably, the upper outer periphery of the liquid outlet chamber is fixedly connected with uniformly distributed heat dissipation fins, all of which are arranged inside the reserved opening, and one side of the reserved opening penetrates the side wall of the tank.

[0011] Preferably, the upper front and rear sides of the insulation layer are provided with through openings, and the openings are connected to the interior of the reserved openings. The internal diameter of the openings gradually increases from the middle to both ends.

[0012] Preferably, the top of the float plate is fixedly connected to a plurality of connecting columns, the top of each connecting column is fixedly connected to the bottom of the piston plate II, and a one-way valve II is installed on the front and rear sides of the middle of the piston plate II. The middle of both the float plate and the piston plate II is penetrated by a liquid outlet pipe, and both the float plate and the piston plate II are slidably connected to the liquid outlet pipe.

[0013] Preferably, a one-way valve is fixedly connected at the upper part between the liquid outlet chamber and the liquid storage chamber, and multiple through conical holes are opened on the outer side of the middle part of the float plate.

[0014] Preferably, a limiting ring is fixedly connected to the lower part of the outer periphery of the middle shaft of the guide vane, and a fixing frame is rotatably connected to the inner side of the limiting ring, and the fixing frame is fixedly connected to the lower part of the connecting pipe.

[0015] Compared with the prior art, the present invention has the following beneficial effects: 1. By replacing the traditional single-space liquid storage tank with a dual-chamber design, the liquid storage chamber first receives the gas-liquid two-phase refrigerant input from the condenser, and then a connecting seat is used for variable connection to introduce liquid refrigerant into the outlet chamber. This keeps the internal pressure of the outlet chamber stable and avoids continuous changes in the output due to pressure fluctuations inside the liquid storage tank when the refrigerant is output through the outlet pipe, which would affect the operation of the subsequent expansion valve. When the refrigeration system is working at full capacity, the refrigerant circulation speed increases, and when there is more refrigerant input into the liquid storage chamber, the downward pressure of piston plate one will increase synchronously under the action of gravity, which will increase the amount of gas entering the reserved sliding cavity, thereby increasing the overall upward movement of the valve core. The inverted conical design of the lower section and the reduced diameter design of the lower column section enable a synchronous increase in the flow rate in the connecting channel. When the pressure inside the liquid storage chamber increases, the valve core moves upward, increasing the flow rate in the connecting channel. Conversely, when the pressure inside the liquid storage chamber decreases, under the action of the first top spring, the first piston plate rises and the second top spring presses down, causing the valve core to descend synchronously, thereby synchronously reducing the flow rate in the connecting channel. This achieves variable flow rate regulation of the liquid refrigerant. By realizing adaptive adjustment of the flow rate between the liquid storage chamber and the outlet chamber, pressure changes can be effectively limited within the liquid storage chamber, thus ensuring stable pressure inside the outlet chamber and facilitating stable output of the liquid refrigerant.

[0016] 2. During the start-up or frequency adjustment of the refrigeration system, when the refrigerant circulation rate fluctuates, the liquid level inside the outlet chamber will change rapidly due to continuous liquid extraction and replenishment. During this process, since the movement of piston plate two is directly driven by the change in the refrigerant liquid level in the outlet chamber, when the refrigerant demand of the refrigeration system increases and the outlet speed increases, the movement amplitude of piston plate two increases accordingly, and the auxiliary cooling process is enhanced. When the refrigerant demand decreases, the movement amplitude of piston plate two decreases, and the auxiliary cooling effect decreases synchronously, so that the auxiliary cooling process can adapt to the actual operating state of the refrigeration system, thereby forming a periodic auxiliary cooling process.

[0017] 3. Some of the heat generated after the gas is compressed can be transferred to the heat dissipation fins through the upper cavity wall of the liquid outlet chamber. The heat dissipation fins exchange heat with the external environment through the reserved port, thereby reducing the heat accumulation in the gas phase region of the upper liquid outlet chamber. When the piston plate moves downward to expand the gas, the gas temperature decreases accordingly. Combined with the heat insulation effect of the insulation layer on the circumferential area of ​​the liquid storage chamber and the liquid outlet chamber, it can reduce the disordered transfer of external heat to the refrigerant area, keeping the refrigerant state inside the liquid outlet chamber relatively stable. At the same time, the reserved port penetrates the side wall of the tank and the opening is connected to the reserved port. External air can enter the reserved port through the opening and come into contact with the heat dissipation fins. Through the structure of the opening gradually expanding from the middle to both ends, the air has a large flow cross section when entering and exiting the reserved port, which is conducive to improving the air exchange capacity around the heat dissipation fins. Thus, while maintaining the heat insulation effect of the outer perimeter of the liquid storage chamber, the heat generated by the gas compression in the upper part of the liquid outlet chamber can be preferentially released to the outside, so that the temperature change formed by the reciprocating motion of the piston plate can act more on the gas phase refrigerant in the upper part of the liquid storage chamber.

[0018] 4. When the refrigerant enters the liquid storage chamber through the condenser and inlet pipe, it first enters the connecting pipe through the inlet pipe and then comes into contact with the guide vanes in the connecting pipe. The flow of refrigerant causes the guide vanes to rotate, which in turn causes the base frame to rotate via a spring. When the base frame rotates, the ball joints around its periphery collide with the inverted cone tube, shaking off any condensed or adhered liquid refrigerant from the periphery of the inverted cone tube. This facilitates refrigerant circulation. During this process, the higher the operating intensity of the refrigeration system, the faster the refrigerant circulation, and the better the effect on the guide vanes. The greater the impact force generated by the blades, the faster the base frame and the inverted cone tube rotate, and the higher the vibration frequency of the inverted cone tube. Combined with the auxiliary cooling structure that synchronously accelerates the working frequency inside the liquid outlet chamber, this effectively increases the liquefaction rate of the refrigerant under high-intensity working conditions. It also promotes the condensation of the gaseous refrigerant in the upper part of the liquid storage chamber under high-intensity working conditions, increases the effective storage ratio of liquid refrigerant, and avoids the situation where the condensation effect of the pre-condenser is not ideal when the refrigerant is flowing at high speed. This assists in the liquefaction of the refrigerant and facilitates subsequent circulating refrigeration.

[0019] 5. Through the cooperation of the spring and the corrugated section, the relative height of the base frame can be adjusted in a timely manner. When the refrigerant is circulating at low frequency, the spring is in a normally contracted state, making the base frame relatively high. At this time, the guide vanes rotate at a low speed due to the low refrigerant input rate. When the base frame rotates, there are more contact points between the ball and the inverted cone tube, thus maintaining the vibration effect on the inverted cone tube under low-frequency rotation. When the refrigerant is circulating at high frequency, the refrigerant input is higher, and the impact force on the base frame when the refrigerant falls is stronger. This causes the spring and the corrugated section to be in an extended state, thus lowering the overall position of the base frame. This reduces the contact points between the base frame and the ball when rotating, thereby reducing the contact area with the inverted cone tube when it vibrates at high frequency, thus preventing damage to the inverted cone tube due to high-frequency impact. Attached Figure Description

[0020] Figure 1 This is a frontal three-dimensional structural diagram of a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to the present invention; Figure 2 This is a schematic diagram of the internal structure of a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to the present invention; Figure 3 This is a partial structural diagram of the opening of a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to the present invention; Figure 4 This is a partial structural diagram of the heat dissipation fins of a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to the present invention; Figure 5 This is a partial structural diagram of the liquid storage chamber and liquid outlet chamber of the refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to the present invention; Figure 6 This is a partial structural diagram of the inverted cone tube of a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to the present invention; Figure 7 This is a partial structural diagram of the connecting spring of a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to the present invention; Figure 8 This is a partial structural diagram of the spring at the refrigerant pressure stabilizing and liquid storage auxiliary device of a multi-model universal refrigeration system according to the present invention; Figure 9 for Figure 5 Enlarged view of point A in the middle.

[0021] 101. Tank body; 102. Opening; 103. Inlet pipe; 104. Outlet pipe; 105. Heat dissipation fins; 106. Reserved opening; 107. Outlet chamber; 108. Conductor pipe; 109. Storage chamber; 110. Connecting plate; 111. Insulation layer; 112. Connecting pipe; 113. Inverted conical section; 114. Bottom through pipe; 115. Connecting seat; 116. Piston plate two; 117. Conical hole; 118. Float plate; 119. Top spring one; 120. Piston plate one; 121. Inverted 122. Tapered tube; 123. One-way valve 1; 124. One-way valve 2; 125. Ball valve; 126. Base frame; 127. Connecting spring; 128. Guide vane; 129. Elastic spring; 130. Fixing frame; 131. Limiting ring; 132. Flexible hose; 133. Upper column section; 134. Straight through hole; 135. Top spring 2; 136. Connecting column; 137. Connecting flow channel; 138. Reserved sliding cavity; 139. Connecting hole; 140. Base plate; 141. Lower column section; 142. Corrugated section. Detailed Implementation

[0022] The following description is intended to disclose the invention and enable those skilled in the art to implement it. The preferred embodiments described below are merely examples, and other obvious variations will occur to those skilled in the art.

[0023] like Figures 1-9 The device shown is a refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system. It includes a tank 101, an inlet pipe 103 fixedly connected to one side of the top of the tank 101, and an outlet pipe 104 fixedly connected to the other side of the top of the tank 101. The inlet port of the inlet pipe 103 is used to connect to the condenser, and the outlet port of the inlet pipe 103 is connected to the top of the connecting pipe 112. The outlet port of the outlet pipe 104 is used to connect to the expansion valve, and the inlet port of the outlet pipe 104 is located at the bottom of the outlet chamber 107 for extracting liquid refrigerant from the bottom of the outlet chamber 107. A liquid storage chamber 109 and an outlet chamber 107 are respectively provided on both sides of the inside of the tank 101. A piston plate 120 is slidably connected to the lower part of the liquid storage chamber 109. A top spring 119 is fixedly connected to the bottom of the piston plate 120 and is fixedly connected to the bottom of the liquid storage chamber 109. Furthermore, in specific implementation, after the refrigerant is condensed by the condenser, it enters the liquid storage chamber 109 inside the tank 101 through the liquid inlet pipe 103. The liquid storage chamber 109 can achieve the initial storage of refrigerant. At the same time, through the cooperation of the piston plate 120 and the top spring 119, the liquid storage chamber 109 can change its volume when storing refrigerant.

[0024] A connecting seat 115 is fixedly connected between the liquid storage chamber 109 and the liquid outlet chamber 107 at the middle. A connecting channel 136 is transversely penetrating the middle of the connecting seat 115. The connecting channel 136 is used to connect the liquid storage chamber 109 and the liquid outlet chamber 107. A reserved sliding cavity 137 perpendicular to the connecting channel 136 is provided in the middle of the connecting seat 115. A valve core is slidably connected inside the reserved sliding cavity 137. The valve core consists of an upper cylindrical section 132 and an inverted conical section 113 from top to bottom. The lower column section 140 and the base plate 139 are composed of a valve core for adjusting the communication state of the connecting flow channel 136. The bottom of the reserved sliding cavity 137 is connected to a connecting hole 138. The bottom of the connecting hole 138 is fixedly connected to a bottom connecting pipe 114. The bottom of the bottom connecting pipe 114 is fixedly connected to the bottom of the liquid storage cavity 109. The top of the reserved sliding cavity 137 is fixedly connected to a top spring 134. The top of the reserved sliding cavity 137 is connected to a straight through hole 133 that penetrates the top wall of the connecting seat 115. Furthermore, in specific implementation, when the refrigerant enters the liquid storage chamber 109, it exerts a downward force on the piston plate 120 under the action of gravity, causing the top spring 119 to be compressed. After the top spring 119 is compressed, the gas at the bottom of the piston plate 120 enters the bottom of the reserved sliding cavity 137 through the bottom pipe 114 and the connecting hole 138. After the gas enters the reserved sliding cavity 137, it lifts the bottom plate 139, thereby driving the upper valve core to overcome the downward pressure of the top spring 134 and move upward as a whole, causing the relative position of the valve core and the connecting channel 136 to change, thus enabling the connecting channel 136 to be in a connected state. The refrigerant can enter the liquid outlet chamber 107 through the connecting channel 136. After entering the liquid outlet chamber 107, the refrigerant will deposit at the bottom of the liquid outlet chamber 107. Through the operation of the downstream system, the refrigerant deposited at the bottom of the liquid outlet chamber 107 can be extracted using the liquid outlet pipe 104 and sent to the subsequent expansion valve, thus completing the refrigerant circulation. By changing the traditional single-space liquid storage tank to a dual-chamber design, the liquid storage chamber 109 first receives the gas-liquid two-phase refrigerant input from the condenser, and then the connecting seat 115 provides variable connection to introduce liquid refrigerant into the liquid outlet chamber 107, thus increasing the pressure inside the liquid outlet chamber 107. To maintain stable pressure and prevent continuous changes in refrigerant output due to pressure fluctuations inside the liquid tank when the liquid outlet pipe 104 outputs refrigerant, thus affecting the operation of the subsequent expansion valve, during the operation of the connecting flow channel 136, when the refrigeration system is working strongly, the refrigerant circulation speed increases, and when more refrigerant is input into the liquid storage chamber 109, the downward pressure of the piston plate 120 under the action of gravity will increase synchronously, causing the gas entering the reserved sliding cavity 137 to increase accordingly, thereby synchronously increasing the overall upward movement of the valve core. Through the inverted cone design of the inverted cone section 113 and the reduced diameter design of the lower column section 140, the synchronous increase of the connecting flow diameter of the connecting flow channel 136 can be achieved. This allows the valve core to move upward when the internal pressure of the liquid storage chamber 109 increases, thereby increasing the flow rate of the connecting channel 136. Conversely, when the internal pressure of the liquid storage chamber 109 decreases, the piston plate 120 rises under the action of the top spring 119, and the top spring 134 presses down, causing the valve core to descend synchronously, thereby synchronously reducing the flow rate of the connecting channel 136. This achieves variable flow rate regulation of the liquid refrigerant. By realizing adaptive regulation of the flow rate between the liquid storage chamber 109 and the outlet chamber 107, pressure changes can be effectively limited within the liquid storage chamber 109, thus ensuring the stability of the pressure inside the outlet chamber 107 and facilitating the stable output of the liquid refrigerant.

[0025] The liquid outlet chamber 107 is slidably connected to a float plate 118 and a piston plate 116. Multiple connecting columns 135 are fixedly connected to the top of the float plate 118. The top of each connecting column 135 is fixedly connected to the bottom of the piston plate 116. One-way valves 123 are installed on the front and rear sides of the middle of the piston plate 116. The middle of both the float plate 118 and the piston plate 116 is penetrated by the liquid outlet pipe 104. Both the float plate 118 and the piston plate 116 are slidably connected to the liquid outlet pipe 104. One-way valve 122 is fixedly connected to the upper part of the liquid outlet chamber 107 and the liquid storage chamber 109. Multiple through conical holes 117 are opened on the outer side of the middle of the float plate 118. Furthermore, in practical implementation, during the start-up or frequency adjustment of the refrigeration system, when the refrigerant circulation rate fluctuates, the liquid level inside the outlet chamber 107 will change rapidly and continuously due to continuous liquid extraction and replenishment. During this process, since the movement of the piston plate 116 is directly driven by the change in the refrigerant liquid level within the outlet chamber 107, when the refrigerant demand of the refrigeration system increases and the outlet speed increases, the movement amplitude of the piston plate 116 increases accordingly, and the auxiliary cooling process is enhanced. When the refrigerant demand decreases, the movement amplitude of the piston plate 116 decreases, and the auxiliary cooling effect decreases simultaneously, so that the auxiliary cooling... The process can adapt to the actual operating state of the refrigeration system. Specifically, when the liquid level inside the liquid outlet chamber 107 rises, the float 118 moves upward under the buoyancy of the liquid refrigerant, and drives the piston plate 116 upward through the connecting column 135. This reduces the gas phase space inside the upper part of the liquid outlet chamber 107 and the connected conduit 108, compressing the gaseous refrigerant in this area, and increasing the gas pressure and temperature. The heat generated during compression is transferred to the heat dissipation fins 105 through the upper cavity wall of the liquid outlet chamber 107, and exchanges heat with the outside air through the reserved port 106, thereby converting the gaseous refrigerant into heat. During the refrigerant compression process, some heat is released to the external environment, resulting in a lower initial heat state for the gaseous refrigerant during subsequent expansion. As the liquid level in the outlet chamber 107 decreases, the float 118 moves downward, causing the piston plate 116 to move downward as well. This gradually increases the gas phase space in the upper part of the outlet chamber 107 and inside the conduit 108. The gaseous refrigerant, having been compressed and released some heat in the previous stage, expands with the increased volume, causing a decrease in gas pressure and a further decrease in temperature. This creates a relatively low-temperature gas phase region in the conduit 108 and the upper part of the outlet chamber 107. Because the conduit 108... 8 is connected to the upper part of the liquid storage chamber 109, so that the gaseous refrigerant in the upper part of the liquid storage chamber 109 can exchange heat with the low temperature region. The heat of the gaseous refrigerant in the liquid storage chamber 109 is transferred to the low temperature gaseous region through the cavity wall of the conducting pipe 108, so that the temperature of the gaseous refrigerant in the upper part of the liquid storage chamber 109 is reduced. When its temperature drops to near the condensation temperature under the corresponding pressure, part of the gaseous refrigerant releases heat and condenses to form liquid refrigerant. The condensed liquid refrigerant gathers downward along the outer wall of the inverted cone pipe 121 and enters the interior of the liquid storage chamber 109, thereby reducing the proportion of gaseous refrigerant in the upper part of the liquid storage chamber 109 and increasing the storage capacity of liquid refrigerant.

[0026] The upper part of the liquid storage chamber 109 is fixedly connected to a guide pipe 108, and the bottom of the guide pipe 108 is fixedly connected to a uniformly distributed inverted conical pipe 121. The ends of the guide pipe 108 all penetrate the side wall of the liquid storage chamber 109 and are fixedly connected to the top of the liquid outlet chamber 107. A connecting plate 110 is fixedly connected to the inner side of the guide pipe 108, and a connecting pipe 112 is fixedly connected to the middle of the connecting plate 110. A guide vane 127 is provided inside the connecting pipe 112, and a limiter is fixedly connected to the lower part of the outer circumference of the middle shaft of the guide vane 127. The inner side of the limiting ring 130 is rotatably connected to the fixing frame 129, which is fixedly connected to the lower part of the connecting pipe 112. The bottom of the middle shaft of the guide vane 127 is set as a corrugated section 141, and a spring spring 128 is set inside the corrugated section 141. The bottom of the corrugated section 141 is fixedly connected to the base frame 125, and the outer periphery of the base frame 125 is fixedly connected to evenly distributed hoses 131. Each end of the hose 131 is fixedly connected to a ball 124, and each hose 131 is installed with a connecting spring 126. Furthermore, in specific implementation, when the refrigerant enters the liquid storage chamber 109 through the condenser and the liquid inlet pipe 103, it first enters the connecting pipe 112 through the liquid inlet pipe 103, and then comes into contact with the guide vanes 127 in the connecting pipe 112. Under the flow of refrigerant, the guide vanes 127 will rotate. The guide vanes 127 can drive the base frame 125 to rotate as a whole through the spring spring 128. When the base frame 125 rotates, the ball bearings 124 on its periphery will collide with the inverted cone tube 121, thereby condensing and adhering liquid around the inverted cone tube 121. The vibration of the refrigerant is beneficial to the refrigerant circulation. During this process, the greater the working intensity of the refrigeration system, the faster the refrigerant circulation, and the greater the impact force on the guide vanes 127. This results in a faster rotation speed of the base frame 125 and the inverted cone tube 121, and consequently, a higher vibration frequency of the inverted cone tube 121. Combined with the auxiliary cooling structure that synchronously accelerates the working frequency inside the liquid outlet chamber 107, this effectively increases the liquefaction rate of the refrigerant under high-intensity working conditions, promotes the condensation of the gaseous refrigerant in the upper part of the liquid storage chamber 109 under high-intensity working conditions, and improves the effective storage of liquid refrigerant. The proportion is designed to prevent insufficient condensation of the pre-condenser when the refrigerant is circulating at high speed, and to assist in the liquefaction of the refrigerant, facilitating subsequent refrigeration cycles. Furthermore, the cooperation between the spring spring 128 and the corrugated section 141 allows for timely adjustment of the relative height of the base frame 125. When the refrigerant is circulating at low frequency, the spring spring 128 is in its normally contracted state, resulting in a higher relative position for the base frame 125. At this time, the guide vanes 127 rotate at a lower speed due to the lower refrigerant input rate. When the base frame 125 rotates, the contact between the ball bearing 124 and the inverted cone tube 121... With more contact points, the vibration effect on the inverted cone tube 121 can be maintained under low-frequency rotation. When the refrigerant is working at high frequency, the refrigerant input is higher, and the impact force on the base frame 125 when the refrigerant falls is stronger. This causes the spring spring 128 and the corrugated section 141 to be in an extended state, which in turn causes the overall position of the base frame 125 to move downward. This reduces the number of contact points between the base frame 125 and the ball bearing 124 when rotating, thereby reducing the contact area with the inverted cone tube 121 when it vibrates at high frequency, thus preventing the inverted cone tube 121 from being damaged by high-frequency impact.

[0027] The tank body 101 is filled with a heat insulation layer 111 between the interior of the tank body 101 and the liquid storage chamber 109 and the liquid outlet chamber 107. A reserved opening 106 is provided on one side of the heat insulation layer 111. The reserved opening 106 is located on the upper part of the liquid outlet chamber 107. Uniformly distributed heat dissipation fins 105 are fixedly connected to the upper part of the outer periphery of the liquid outlet chamber 107. All heat dissipation fins 105 are located inside the reserved opening 106. One side of the reserved opening 106 penetrates the side wall of the tank body 101. The front and rear sides of the upper part of the heat insulation layer 111 are provided with through openings 102. The openings 102 are connected to the interior of the reserved opening 106. The internal diameter of the openings 102 gradually increases from the middle to both ends. Furthermore, in specific implementation, some of the heat generated after the gas is compressed can be transferred to the heat dissipation fins 105 through the upper cavity wall of the liquid outlet chamber 107. The heat dissipation fins 105 exchange heat with the external environment through the reserved port 106, thereby reducing the heat accumulation in the upper gas phase region of the liquid outlet chamber 107. When the piston plate 116 moves downward to expand the gas, the gas temperature decreases accordingly. Combined with the heat insulation effect of the insulation layer 111 on the circumferential region of the liquid storage chamber 109 and the liquid outlet chamber 107, the disordered transfer of external heat to the refrigerant region can be reduced, thus maintaining the refrigerant state inside the liquid outlet chamber 107. The system maintains relative stability. Meanwhile, the reserved port 106 penetrates the side wall of the tank 101, and the opening 102 is connected to the reserved port 106. External air can enter the reserved port 106 through the opening 102 and come into contact with the heat dissipation fins 105. Through the structure of the opening 102 gradually expanding from the middle to both ends, the air has a large flow cross section when entering and exiting the reserved port 106, which is conducive to improving the air exchange capacity around the heat dissipation fins 105. Thus, while maintaining the heat preservation effect of the liquid storage chamber 109, the heat generated by gas compression in the upper part of the liquid outlet chamber 107 can be preferentially released to the outside.

[0028] Working principle: In actual use, after the refrigerant is condensed by the condenser, it enters the liquid storage chamber 109 inside the tank 101 through the liquid inlet pipe 103. The liquid storage chamber 109 allows for initial storage of the refrigerant. Simultaneously, through the cooperation of the piston plate 120 and the top spring 119, the liquid storage chamber 109 can change its volume when storing the refrigerant. When the refrigerant enters the liquid storage chamber 109, gravity exerts a downward force on the piston plate 120, compressing the top spring 119. After the top spring 119 is compressed, the gas below the piston plate 120 enters the bottom of the reserved sliding cavity 137 through the bottom pipe 114 and the connecting hole 138. After entering the reserved sliding cavity 137, the gas lifts the bottom plate 139. The upper valve core moves upward to overcome the downward pressure of the top spring 134, changing the relative position of the valve core and the connecting channel 136. This allows the connecting channel 136 to be connected, enabling the refrigerant to enter the liquid outlet chamber 107. Once inside the liquid outlet chamber 107, the refrigerant deposits at the bottom. The downstream system uses the liquid outlet pipe 104 to extract the deposited refrigerant and direct it into the subsequent expansion valve, thus completing the refrigerant circulation. By changing the traditional single-space storage tank to a dual-chamber design, the storage chamber 109 first receives the gas-liquid two-phase refrigerant input from the condenser, and then... The variable connection is achieved using the connecting seat 115, allowing liquid refrigerant to be introduced into the outlet chamber 107. This maintains a stable internal pressure in the outlet chamber 107, preventing continuous changes in the output due to pressure fluctuations inside the liquid tank when the outlet pipe 104 outputs refrigerant, which could affect the operation of the subsequent expansion valve. During the operation of the connecting channel 136, when the refrigeration system is working at full capacity, the refrigerant circulation speed increases. When a large amount of refrigerant is input into the liquid storage chamber 109, the downward pressure of the piston plate 120 increases synchronously under the action of gravity. This increases the amount of gas entering the reserved sliding cavity 137, thereby synchronously increasing the overall upward movement of the valve core. Through the inverted cone design of the inverted cone section 113 and the reduced diameter design of the lower column section 140, the connection can be achieved. The synchronous increase in the flow path of the flow channel 136 allows the valve core to move upward when the internal pressure of the liquid storage chamber 109 increases, thereby increasing the flow rate through the flow channel 136. Conversely, when the internal pressure of the liquid storage chamber 109 decreases, the piston plate 120 rises under the action of the top spring 119, and the bottom spring 134 presses down, causing the valve core to descend synchronously, thus synchronously reducing the flow rate through the flow channel 136. This achieves variable flow rate regulation of the liquid refrigerant. By realizing adaptive adjustment of the flow rate between the liquid storage chamber 109 and the outlet chamber 107, pressure changes can be effectively limited within the liquid storage chamber 109, thereby ensuring stable pressure inside the outlet chamber 107. This is beneficial for the stable output of the liquid refrigerant during refrigeration system start-up, shutdown, or frequency adjustment.When the refrigerant circulation rate fluctuates, the liquid level inside the outlet chamber 107 changes rapidly due to continuous pumping and replenishment. During this process, since the movement of piston plate 116 is directly driven by the change in the refrigerant liquid level inside the outlet chamber 107, when the refrigerant demand of the refrigeration system increases and the outlet speed increases, the movement amplitude of piston plate 116 increases accordingly, and the auxiliary cooling process is enhanced. When the refrigerant demand decreases, the movement amplitude of piston plate 116 decreases, and the auxiliary cooling effect decreases simultaneously, so that the auxiliary cooling process can adapt to the actual operating state of the refrigeration system. Specifically, when the liquid level inside the outlet chamber 107 rises, float plate 118 moves upward under the buoyancy of the liquid refrigerant and is carried by connecting column 135. The piston plate 116 moves upward, reducing the gas phase space in the upper part of the outlet chamber 107 and the connected conduit 108. The gaseous refrigerant in this area is compressed, and its pressure and temperature increase accordingly. The heat generated during compression is transferred through the upper wall of the outlet chamber 107 to the heat dissipation fins 105, and exchanges heat with the outside air through the reserved port 106, thus releasing some of the heat generated during the compression of the gaseous refrigerant to the external environment. This ensures that the gaseous refrigerant has a lower initial heat state during subsequent expansion. When the liquid level in the outlet chamber 107 drops, the float 118 moves downward, causing the piston plate 116 to move downward as well. This gradually increases the gas phase space in the upper part of the outlet chamber 107 and the connected conduit 108. The gaseous refrigerant, having been compressed and released some heat in the previous stage, expands as its volume increases. As the gas pressure decreases, its temperature further drops, creating a relatively low-temperature gaseous region in the upper part of the conductive pipe 108 and the liquid outlet chamber 107. Since the conductive pipe 108 is connected to the upper part of the liquid storage chamber 109, the gaseous refrigerant in the upper part of the liquid storage chamber 109 can exchange heat with this low-temperature region. The heat from the gaseous refrigerant in the liquid storage chamber 109 is transferred to the low-temperature gaseous region through the wall of the conductive pipe 108, causing the temperature of the gaseous refrigerant in the upper part of the liquid storage chamber 109 to decrease. When its temperature drops to near the condensation temperature at the corresponding pressure, some of the gaseous refrigerant releases heat and condenses to form liquid refrigerant. The condensed liquid refrigerant collects downwards along the outer wall of the inverted cone pipe 121 and enters the liquid storage chamber. Inside cavity 109, the proportion of gaseous refrigerant in the upper part of the liquid storage cavity 109 is reduced, and the storage capacity of liquid refrigerant is increased. Simultaneously, the insulation layer 111 reduces disordered heat exchange between the circumferential areas of the liquid storage cavity 109 and the outlet cavity 107 and the external environment, allowing the temperature changes generated by the reciprocating motion of piston plate 116 to act more on the gaseous refrigerant in the upper part of the liquid storage cavity 109, thus forming a periodic auxiliary cooling process. Some of the heat generated after the gas is compressed can be transferred through the upper cavity wall of the outlet cavity 107 to the heat dissipation fins 105. The heat dissipation fins 105 exchange heat with the external environment through the reserved opening 106, thereby reducing heat accumulation in the gaseous region above the outlet cavity 107. When piston plate 116 moves downwards, causing the gas to expand, the gas temperature decreases accordingly.The insulation layer 111, in conjunction with the insulation effect on the circumferential areas of the liquid storage chamber 109 and the liquid outlet chamber 107, reduces the disorderly transfer of external heat to the refrigerant area, keeping the refrigerant state inside the liquid outlet chamber 107 relatively stable. Simultaneously, the reserved port 106 penetrates the side wall of the tank body 101, and the opening 102 communicates with the reserved port 106, allowing external air to enter the reserved port 106 through the opening 102 and contact the heat dissipation fins 105. The structure of the opening 102, which gradually widens from the middle to both ends, provides a large flow cross-section for air entering and exiting the reserved port 106, which is beneficial for improving the air exchange capacity around the heat dissipation fins 105. Thus, while maintaining the insulation effect around the liquid storage chamber 109, the heat generated by gas compression in the upper part of the liquid outlet chamber 107 is reduced. The refrigerant can be preferentially released to the outside. When the refrigerant enters the liquid storage chamber 109 through the condenser and the liquid inlet pipe 103, it first enters the connecting pipe 112 through the liquid inlet pipe 103, and then comes into contact with the guide vanes 127 in the connecting pipe 112. Under the flow of refrigerant, the guide vanes 127 will rotate. The guide vanes 127 can drive the base frame 125 to rotate as a whole by means of the spring spring 128. When the base frame 125 rotates, the ball bearings 124 on its periphery will collide with the inverted cone tube 121, thereby shaking off the liquid refrigerant condensed and adhered on the periphery of the inverted cone tube 121, which is beneficial to the refrigerant circulation. In this process, the greater the working intensity of the refrigeration system, the faster the refrigerant circulation, and the greater the impact force on the guide vanes 127. This results in a faster rotation speed of the base frame 125 and the inverted cone tube 121, leading to a higher vibration frequency of the inverted cone tube 121. Combined with the auxiliary cooling structure that synchronously accelerates the internal working frequency of the liquid outlet chamber 107, this effectively increases the liquefaction rate of the refrigerant under high-intensity operating conditions. It also promotes the condensation of the gaseous refrigerant in the upper part of the liquid storage chamber 109 under high-intensity operating conditions, increasing the effective storage ratio of liquid refrigerant. This prevents the pre-condenser from having an insufficient condensation effect when the refrigerant is circulating at high speed, assisting in the liquefaction of the refrigerant and facilitating subsequent circulating refrigeration. Furthermore, the cooperation of the spring spring 128 and the corrugated section 141 allows for timely adjustment of the relative height of the base frame 125. When the refrigerant is circulating at low frequency, the spring spring 128... In the normal contraction state (section 8), the base frame 125 is positioned relatively high. At this time, due to the low refrigerant input rate, the guide vanes 127 rotate at a low speed. When the base frame 125 rotates, there is more contact between the ball bearing 124 and the inverted cone tube 121, thus maintaining a vibration effect on the inverted cone tube 121 during low-frequency rotation. When the refrigerant is circulating at high frequency, the refrigerant input is higher, resulting in a stronger impact force on the base frame 125 when the refrigerant falls. This causes the spring spring 128 and the corrugated section 141 to be in an extended state, lowering the overall position of the base frame 125. This reduces the contact area between the base frame 125 and the ball bearing 124 during rotation, thereby reducing the contact area with the inverted cone tube 121 during high-frequency vibration.This avoids damage to the inverted tapered tube 121 due to high-frequency impact.

[0029] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely principles of the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claimed invention. The scope of protection claimed by the appended claims and their equivalents is defined.

Claims

1. A refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system, comprising a tank (101), characterized in that: The tank body (101) has a liquid storage chamber (109) and a liquid outlet chamber (107) on its two sides. A float plate (118) and a piston plate (116) are slidably connected inside the liquid outlet chamber (107). A piston plate (120) is slidably connected to the lower part of the liquid storage chamber (109). A top spring (119) is fixedly connected to the bottom of the piston plate (120). The top spring (119) is fixedly connected to the bottom of the liquid storage chamber (109). A connecting seat (115) is fixedly connected in the middle between the liquid storage chamber (109) and the liquid outlet chamber (107). A connecting flow channel (136) is transversely penetrating the middle of the connecting seat (115). The connecting channel (136) is used to connect the liquid storage chamber (109) and the liquid outlet chamber (107). The connecting seat (115) has a reserved sliding cavity (137) perpendicular to the connecting channel (136) in the middle. A valve core is slidably connected inside the reserved sliding cavity (137). The valve core consists of an upper column section (132), an inverted cone section (113), a lower column section (140), and a base plate (139) from top to bottom. The valve core is used to adjust the connection state of the connecting channel (136). A connecting hole (138) is connected to the bottom of the reserved sliding cavity (137). A bottom connecting pipe (114) is fixedly connected to the bottom of the connecting hole (138). The bottom of the bottom tube (114) is fixedly connected to the bottom of the liquid storage cavity (109). A top spring (134) is fixedly connected to the top of the reserved sliding cavity (137). A straight through hole (133) penetrating the top wall of the connecting seat (115) is connected to the top of the reserved sliding cavity (137). A guide tube (108) is fixedly connected to the upper part of the liquid storage cavity (109). The bottom of the guide tube (108) is fixedly connected to evenly distributed inverted conical tubes (121). The ends of the guide tubes (108) all penetrate the side wall of the liquid storage cavity (109) and are fixedly connected to the top of the liquid outlet cavity (107). The inner side of the guide tube (108) is fixedly connected to... A connecting plate (110) is fixedly connected to a connecting pipe (112) in the middle. A guide vane (127) is provided inside the connecting pipe (112). The bottom of the shaft of the guide vane (127) is set as a corrugated section (141). An elastic spring (128) is provided inside the corrugated section (141). A base frame (125) is fixedly connected to the bottom of the corrugated section (141). Uniformly distributed hoses (131) are fixedly connected to the outer periphery of the base frame (125). A ball (124) is fixedly connected to the end of each hose (131). A connecting spring (126) is installed inside each hose (131).

2. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 1, characterized in that: An inlet pipe (103) is fixedly connected to one side of the top of the tank (101), and an outlet pipe (104) is fixedly connected to the other side of the top of the tank (101).

3. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 2, characterized in that: The top inlet of the liquid inlet pipe (103) is used to connect to the condenser, and the bottom outlet of the liquid inlet pipe (103) is connected to the top of the connecting pipe (112).

4. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 3, characterized in that: The top outlet of the liquid outlet pipe (104) is used to connect to the expansion valve, and the bottom inlet of the liquid outlet pipe (104) is located at the bottom of the liquid outlet chamber (107) to extract the liquid refrigerant at the bottom of the liquid outlet chamber (107).

5. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 1, characterized in that: The interior of the tank (101) is filled with a heat insulation layer (111) between the liquid storage chamber (109) and the liquid outlet chamber (107). A reserved opening (106) is provided on one side of the heat insulation layer (111), and the reserved opening (106) is located on the upper part of the liquid outlet chamber (107).

6. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 5, characterized in that: The upper part of the outer periphery of the liquid outlet cavity (107) is fixedly connected with uniformly distributed heat dissipation fins (105). The heat dissipation fins (105) are all arranged inside the reserved port (106). One side of the reserved port (106) penetrates the side wall of the tank body (101).

7. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 6, characterized in that: The insulation layer (111) has through openings (102) on both the front and rear sides of the upper part. The openings (102) are connected to the interior of the reserved opening (106). The internal diameter of the openings (102) gradually increases from the middle to both ends.

8. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 1, characterized in that: The top of the float plate (118) is fixedly connected to a plurality of connecting columns (135), the top of each connecting column (135) is fixedly connected to the bottom of the piston plate (116), and a one-way valve (123) is installed on the front and rear sides of the middle of the piston plate (116). The middle of the float plate (118) and the piston plate (116) are both penetrated by the liquid outlet pipe (104), and the float plate (118) and the piston plate (116) are slidably connected to the liquid outlet pipe (104).

9. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 8, characterized in that: A one-way valve (122) is fixedly connected at the upper part between the liquid outlet chamber (107) and the liquid storage chamber (109), and multiple through conical holes (117) are opened on the outer side of the middle part of the float plate (118).

10. The refrigerant pressure stabilizing and liquid storage auxiliary device for a multi-model universal refrigeration system according to claim 1, characterized in that: The guide vane (127) is fixedly connected to the lower part of the outer circumference of the middle shaft with a limiting ring (130), and a fixing frame (129) is rotatably connected to the inner side of the limiting ring (130). The fixing frame (129) is fixedly connected to the lower part of the connecting pipe (112).

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