Compressor and air conditioner

Abstract

The invention relates to the technical field of refrigerating systems, and provides a compressor and an air conditioner. A heat exchange channel is formed in the middle plate, and the liquid storage device communicates with the heat exchange channel through a drainage pipe and is used for introducing a liquid refrigerant into the heat exchange channel; the two air cylinders are arranged on the two opposite sides of the middle plate correspondingly. The crankshaft rotates relative to the shell, the crankshaft sequentially penetrates through one air cylinder, the middle plate and the other air cylinder in the axial direction of the crankshaft, a piston of the crankshaft and the inner circumferential wall of the air cylinder form a working cavity, the liquid storage device communicates with the working cavity through an air suction pipe and is used for introducing gaseous refrigerants into the working cavity, and the heat exchange channel communicates with the working cavity. Therefore, due to the fact that phase change exists in the refrigerant, namely the refrigerant can absorb a large amount of heat in the process of converting from the liquid state to the gas state, power consumption of the compressor in the compression process is reduced, and the working efficiency of the compressor is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration systems, and particularly to a compressor and an air conditioner. Background Art

[0002] In the compression process of a traditional high-back pressure compressor, according to the relationship between the temperature in the compression chamber and the temperature of the external environment of the pump body, it can be divided into two processes: endothermic compression and exothermic compression. The entire compression process experiences endothermic and exothermic processes, which are approximately isentropic compression, but the actual compression work is greater than or equal to the isentropic compression work.

[0003] To ensure the stability and reliability of the air-conditioning system and the compressor components, a certain degree of superheat needs to be ensured at the outlet of the evaporator. Therefore, the refrigerant at the inlet of the evaporator is in a gas-liquid two-phase state, and the refrigerant at the outlet of the evaporator is in a gas phase. This results in the heat exchange state of the refrigerant in the evaporator being gas-liquid heat exchange and gas-gas heat exchange, and there is an order-of-magnitude difference between the heat transfer coefficients of the two, reducing the average heat transfer coefficient of the heat exchanger.

[0004] In an air-conditioning system, the exhaust port of the evaporator is connected to the intake port of the compressor. Since the outlet of the evaporator always maintains a superheated state, the gas discharged is high-temperature gas. The high-temperature gas enters the working chamber of the cylinder through the intake port of the compressor. Under the extrusion work of the crankshaft, a large amount of heat is continuously generated, resulting in the continuous high temperature of the working chamber. This not only increases the power consumption of the compressor during the compression process but also causes the exhaust temperature of the compressor to be too high under multiple working conditions, affecting the reliability of the compressor.

[0005] Therefore, there is an urgent need for a compressor and an air conditioner to solve the above technical problems. Summary of the Invention

[0006] The purpose of the present invention is to provide a compressor and an air conditioner that can further reduce the temperature of the working chamber of the cylinder, thereby reducing the power consumption of the compressor during the compression process and improving the working efficiency of the compressor.

[0007] To achieve this purpose, the present invention adopts the following technical solutions:

[0008] A compressor, comprising:

[0009] A liquid receiver in which a refrigerant is stored, and the refrigerant includes a gas-liquid two-phase;

[0010] A housing;

[0011] An intermediate plate in which a heat exchange channel is formed, and the liquid receiver is connected to the heat exchange channel through a drain pipe for introducing the liquid refrigerant into the heat exchange channel;

[0012] Two cylinders, which are respectively arranged on opposite sides of the intermediate plate;

[0013] A crankshaft, the crankshaft rotates relative to the housing, the crankshaft axially penetrates one of the cylinders, the intermediate plate, and the other cylinder in sequence, a piston is installed on the crankshaft, the piston and the inner peripheral wall of the cylinder form a working chamber, the liquid reservoir is communicated with the working chamber through an intake pipe to introduce the gaseous refrigerant into the working chamber, and the heat exchange channel is communicated with the working chamber.

[0014] As a preferred technical solution of the compressor, one end of the drain pipe is communicated with the heat exchange channel, and the other end is inserted into the liquid reservoir and is located at the bottom of the liquid reservoir.

[0015] As a preferred technical solution of the compressor, one end of the intake pipe is communicated with the working chamber, and the other end is inserted into the liquid reservoir and is located at the upper part of the liquid reservoir.

[0016] As a preferred technical solution of the compressor, the heat exchange channel is arranged in a meandering shape within the intermediate plate.

[0017] As a preferred technical solution of the compressor, the heat exchange channel includes an inlet and two outlets, the inlet is connected to the drain pipe, and the two outlets are respectively communicated with the two working chambers in one-to-one correspondence.

[0018] As a preferred technical solution of the compressor, the outlet of the heat exchange channel is adjacent to the suction port of the working chamber.

[0019] As a preferred technical solution of the compressor, the cross-sectional area of the heat exchange channel gradually increases from its inlet to its outlet.

[0020] As a preferred technical solution of the compressor, the height of the heat exchange channel is H1, the height of the intermediate plate is H, and 1 / 4*H ≤ H1 ≤ 2 / 3*H is satisfied, and the width of the heat exchange channel is D1, and the distance between the mounting hole of the intermediate plate and the central through hole of the intermediate plate is D, and 1 / 3*D ≤ D1 ≤ 2 / 3*D is satisfied.

[0021] As a preferred technical solution of the compressor, the cross-section of the heat exchange channel is formed into a circular shape.

[0022] An air conditioner is also provided, including an evaporator and the above-mentioned compressor, the exhaust port of the evaporator is communicated with the intake port of the compressor, and the intake port is communicated with the working chamber.

[0023] Advantages of the present invention:

[0024] A compressor is provided, which includes a liquid receiver, a housing, an intermediate plate, a cylinder and a crankshaft. Among them, the liquid receiver stores refrigerant, and the refrigerant includes a gas-liquid two-phase; a heat exchange channel is provided in the intermediate plate, and the liquid receiver is communicated with the heat exchange channel through a drainage pipe for introducing the liquid refrigerant into the heat exchange channel; two cylinders are provided and are respectively arranged on opposite sides of the intermediate plate; the crankshaft rotates relative to the housing, and the crankshaft sequentially penetrates through one of the cylinders, the intermediate plate and the other cylinder along its axial direction. A piston is installed on the crankshaft, and a working chamber is formed between the piston and the inner peripheral wall of the cylinder. The liquid receiver is communicated with the working chamber through a suction pipe for introducing the gaseous refrigerant into the working chamber, and the heat exchange channel is communicated with the working chamber.

[0025] Since there is a phase change in the refrigerant, that is, a large amount of heat can be absorbed during the process of the refrigerant changing from liquid to gas. In this way, the temperature in the working chamber can be reduced. Further, the vaporized refrigerant and the gaseous refrigerant in the liquid receiver are both introduced into the working chamber and directly exchange heat with the high-temperature gas inside the working chamber, so as to fully cool the working chamber, reduce the power consumption during the compression process of the compressor, and improve the working efficiency of the compressor. Description of the Drawings

[0026] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly introduce the drawings required for the description of the embodiments of the present invention. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on the content of the embodiments of the present invention and these drawings.

[0027] Figure 1 It is a schematic structural diagram of the compressor provided by the embodiment of the present invention;

[0028] Figure 2 It is a front view of the intermediate plate provided by the embodiment of the present invention;

[0029] Figure 3 It is a top view of the intermediate plate provided by the embodiment of the present invention.

[0030] In the figure:

[0031] 10. Liquid receiver; 11. Drainage pipe; 12. Suction pipe;

[0032] 20. Housing;

[0033] 30. Intermediate plate; 31. Heat exchange channel; 311. Inlet; 312. Outlet;

[0034] 40. Cylinder. Detailed Embodiments

[0035] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It can be understood that the specific embodiments described herein are only for explaining the present invention and not for limiting the present invention. In addition, it should be noted that for the sake of description, only the parts related to the present invention rather than all the structures are shown in the drawings.

[0036] In the description of the present invention, unless otherwise clearly defined and limited, the terms "connected", "connected to", and "fixed" shall be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0037] In the present invention, unless otherwise clearly defined and limited, the first feature being "above" or "below" the second feature may include the direct contact between the first and second features, or may include the situation where the first and second features are not in direct contact but in contact through other features therebetween. Moreover, the first feature being "above", "over", and "on" the second feature includes that the first feature is directly above and obliquely above the second feature, or simply means that the first feature is at a higher horizontal height than the second feature. The first feature being "below", "under", and "beneath" the second feature includes that the first feature is directly below and obliquely below the second feature, or simply means that the first feature is at a lower horizontal height than the second feature.

[0038] In the description of this embodiment, the orientation or positional relationships such as "above", "below", "right", etc. are based on the orientation or positional relationships shown in the drawings, and are only for the convenience of description and simplifying the operation, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus cannot be understood as a limitation to the present invention. In addition, the terms "first" and "second" are only used for distinction in description and have no special meanings.

[0039] Such as Figures 1 to 3As shown in the figure, the present application provides a compressor, which includes a liquid reservoir 10, a housing 20, an intermediate plate 30, a cylinder 40, and a crankshaft. Among them, the liquid reservoir 10 stores refrigerant, and the refrigerant includes a gas-liquid two-phase; a heat exchange channel 31 is provided in the intermediate plate 30, and the liquid reservoir 10 is communicated with the heat exchange channel 31 through a drainage pipe 11 for introducing the liquid refrigerant into the heat exchange channel 31; two cylinders 40 are provided and are respectively arranged on opposite sides of the intermediate plate 30; the crankshaft rotates relative to the housing 20, and the crankshaft sequentially penetrates through one cylinder 40, the intermediate plate 30, and the other cylinder 40 along its axial direction. A piston is installed on the crankshaft, and the piston and the inner peripheral wall of the cylinder 40 form a working chamber. The liquid reservoir 10 is communicated with the working chamber through a suction pipe 12 for introducing gaseous refrigerant into the working chamber, and the heat exchange channel 31 is communicated with the working chamber.

[0040] Specifically, the intermediate plate 30 is fixed between the cylinder blocks of the two cylinders 40. The piston installed on the crankshaft is located in the cylinder 40. The piston and the peripheral side of the cylinder 40 enclose a working chamber, and the two axial ends of the intermediate plate 30 are respectively in contact with the working chambers on both sides. When the compressor works, the crankshaft rotates relative to the housing 20, and the crankshaft drives the piston to reciprocally compress the gas in the working chamber to do work, generating a large amount of heat, and the initial temperature of the gas in the working chamber is also relatively high. In order to reduce the temperature in the working chamber, the liquid reservoir 10 stores a gas-liquid two-phase refrigerant, that is, the refrigerant includes gaseous refrigerant and liquid refrigerant. Among them, the gaseous refrigerant directly enters the working chamber from the liquid reservoir 10 along the suction pipe 12. At the same time, the liquid refrigerant also enters the heat exchange channel 31 of the intermediate plate 30 from the liquid reservoir 10 along the drainage pipe 11. The liquid refrigerant exchanges heat with the high-temperature gas in the working chamber through the intermediate plate 30 in the heat exchange channel 31. The liquid refrigerant absorbs heat and vaporizes into gaseous refrigerant, and then is discharged from the heat exchange channel 31 into the working chamber to be mixed with the gaseous refrigerant inhaled by the suction pipe 12 and enters the normal compression process.

[0041] Since there is a phase change in the refrigerant, that is, the process of the refrigerant changing from liquid to gas can absorb a large amount of heat. In this way, the temperature in the working chamber can be reduced. Further, the vaporized refrigerant and the gaseous refrigerant in the liquid reservoir 10 are both introduced into the working chamber and directly exchange heat with the high-temperature gas inside the working chamber. In this way, the working chamber is fully cooled, the power consumption during the compression process of the compressor is reduced, and the working efficiency of the compressor is improved.

[0042] Further, the mixing of the gaseous refrigerant in the heat exchange channel 31 and the gaseous refrigerant in the suction pipe 12 at a specific high rotational speed can achieve the effect of suction supercharging.

[0043] In this embodiment, two suction pipes 12 are provided and are respectively inserted into the two working chambers in a one-to-one correspondence.

[0044] In other embodiments, the compressor has single-cylinder suction. For the convenience of description, the two cylinders 40 are respectively denoted as the first cylinder and the second cylinder. That is, the working chamber of the first cylinder is communicated with the liquid storage tank 10 through the suction pipe 12, and the working chamber of the second cylinder is communicated with the working chamber of the first cylinder. In this way, the gaseous refrigerant first enters the working chamber of the first cylinder and then is discharged into the working chamber of the second cylinder.

[0045] In other embodiments, the intermediate plate 30 is respectively communicated with the suction pipe 12 and the drainage pipe 11. The liquid storage tank 10 feeds the refrigerant in a gas-liquid two-phase state into the intermediate plate 30 together. The refrigerant first exchanges heat with the working chamber by means of the intermediate plate 30. Subsequently, the refrigerant is discharged from the intermediate plate 30 into the two working chambers for direct heat exchange.

[0046] Generally, for the same refrigerant, the density of its liquid state is greater than that of its gaseous state. Therefore, the liquid refrigerant is at the bottom of the liquid storage tank 10, and the gaseous refrigerant is at the upper part of the liquid storage tank 10. Therefore, in this embodiment, one end of the drainage pipe 11 is communicated with the heat exchange channel 31, and the other end is inserted into the liquid storage tank 10 and is located at the bottom of the liquid storage tank 10.

[0047] Optionally, one end of the suction pipe 12 is communicated with the working chamber, and the other end is inserted into the liquid storage tank 10 and is located at the upper part of the liquid storage tank 10.

[0048] Optionally, the heat exchange channel 31 is arranged in a meandering shape in the intermediate plate 30. With this arrangement, the length of the heat exchange channel 31 opened in the intermediate plate 30 can be extended, which can not only extend the residence time of the liquid refrigerant in the heat exchange channel 31, but also increase the contact area between the heat exchange channel 31 and the working chamber, so that the liquid refrigerant can fully exchange heat with the working chamber through the intermediate plate 30.

[0049] Optionally, the heat exchange channel 31 includes an inlet 311 and two outlets 312. The inlet 311 is connected to the drainage pipe 11, and the two outlets 312 are respectively communicated with the two working chambers in one-to-one correspondence.

[0050] Optionally, the outlet 312 of the heat exchange channel 31 is adjacent to the suction port of the working chamber. In this way, the refrigerant vaporized in the intermediate plate 30 enters the vicinity of the suction ports of the two cylinders 40 respectively and is mixed with the gaseous refrigerant introduced by the suction pipe 12.

[0051] Optionally, the projection of the outlet of the heat exchange channel 31 facing the working chamber at least partially overlaps with the extension direction of the flow channel of the suction pipe 12 in the cylinder 40.

[0052] As the liquid refrigerant absorbs heat within the heat exchange channel 31, it begins to vaporize. Moreover, the density of the gaseous refrigerant is smaller and its volume is larger than that of the liquid refrigerant, exerting a squeezing effect on the inner peripheral wall of the heat exchange channel 31, resulting in the inability of the gaseous refrigerant to uniformly and continuously enter the working chamber. Therefore, in this embodiment, the cross-sectional area of the heat exchange channel 31 gradually increases from its inlet 311 to its outlet 312. In this way, space is reserved for the volume expansion that occurs when the refrigerant vaporizes.

[0053] In other embodiments, the cross-sectional area of the heat exchange channel 31 is equal from its inlet 311 to its outlet 312.

[0054] Optionally, the height of the heat exchange channel 31 is H1 and the height of the intermediate plate 30 is H, satisfying 1 / 4*H ≤ H1 ≤ 2 / 3*H, and the width of the heat exchange channel 31 is D1, and the effective width of the intermediate plate 30 is D, satisfying 1 / 3*D ≤ D1 ≤ 2 / 3*D. With such a design, it is possible to enhance the heat exchange area as much as possible while ensuring the strength of the intermediate plate 30.

[0055] Specifically, as Figure 2 shown, the width D of the intermediate plate 30 refers to the distance between the mounting hole of the intermediate plate 30 and the central through hole of the intermediate plate 30, satisfying D = R4 - R1, where R4 refers to the radius of the circle where the axes of the mounting holes of several intermediate plates 30 are located, and R1 refers to the radius of the central through hole of the intermediate plate 30; the width D1 of the heat exchange channel 31 satisfies R3 - R2, where R3 refers to the maximum radius of the circle where the channel wall of the heat exchange channel 31 far from the center of the intermediate plate 30 is located, and R2 refers to the minimum radius of the circle where the channel wall of the heat exchange channel 31 close to the center of the intermediate plate 30 is located.

[0056] Optionally, the cross-section of the heat exchange channel 31 is circular.

[0057] An air conditioner is also provided, including an evaporator and the above-mentioned compressor. The exhaust port of the evaporator is communicated with the intake port of the compressor, and the intake port is communicated with the working chamber. In this way, the high-temperature gas discharged from the evaporator enters the working chamber of the compressor from the intake port. The liquid refrigerant within the intermediate plate 30 exchanges heat with the high-temperature gas to reduce the gas temperature. At the same time, the gaseous refrigerant directly enters the working chamber and mixes with the high-temperature gas for heat exchange. In this way, the temperature of the working chamber is reduced, the working efficiency of the compressor and the air-conditioning system is improved, and at the same time, the temperature of the gas discharged from the compressor is reduced, enhancing the reliability of the compressor operation.

[0058] In addition, the above are only the preferred embodiments of the present invention and the technical principles applied. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein. Various obvious changes, re-adjustments, and substitutions can be made by those skilled in the art without departing from the protection scope of the present invention. Therefore, although the present invention has been described in more detail through the above embodiments, the present invention is not limited to the above embodiments. Without departing from the concept of the present invention, more other equivalent embodiments can be included, and the scope of the present invention is determined by the scope of the appended claims.

Claims

1. Compressor, characterized in that, Comprising: A liquid reservoir (10) storing a refrigerant therein, and the refrigerant includes a gas-liquid two-phase; A housing (20); An intermediate plate (30) having a heat exchange channel (31) formed therein, and the liquid reservoir (10) is communicated with the heat exchange channel (31) through a drain pipe (11) for introducing the liquid refrigerant into the heat exchange channel (31); Two cylinders (40) respectively arranged on opposite sides of the intermediate plate (30); A crankshaft rotatably relative to the housing (20), the crankshaft axially penetrates through one of the cylinders (40), the intermediate plate (30) and the other cylinder (40) in sequence, a piston is mounted on the crankshaft, the piston and the inner peripheral wall of the cylinder (40) form a working chamber, the liquid reservoir (10) is communicated with the working chamber through a suction pipe (12) for introducing the gaseous refrigerant into the working chamber, and the heat exchange channel (31) is communicated with the working chamber.

2. The compressor according to claim 1, wherein, One end of the drain pipe (11) is communicated with the heat exchange channel (31), and the other end is inserted into the liquid reservoir (10) and located at the bottom of the liquid reservoir (10).

3. The compressor according to claim 1, wherein One end of the suction pipe (12) is communicated with the working chamber, and the other end is inserted into the liquid reservoir (10) and located at the upper part of the liquid reservoir (10).

4. The compressor according to claim 1, characterized in that, The heat exchange channel (31) is formed in a meandering shape within the intermediate plate (30).

5. The compressor according to claim 4, characterized in that, The heat exchange channel (31) includes an inlet (311) and two outlets (312), the inlet (311) is connected to the drain pipe (11), and the two outlets (312) are respectively communicated with the two working chambers in one-to-one correspondence.

6. The compressor according to claim 5, characterized in that, The outlet (312) of the heat exchange channel (31) is adjacent to the suction port of the working chamber.

7. The compressor according to claim 5, characterized in that, The cross-sectional area of the heat exchange channel (31) gradually increases from its inlet (311) to its outlet (312).

8. The compressor according to claim 1, wherein The height of the heat exchange channel (31) is H1 and the height of the intermediate plate (30) is H, satisfying 1 / 4*H ≤ H1 ≤ 2 / 3*H, and the width of the heat exchange channel (31) is D1, the distance between the mounting hole of the intermediate plate (30) and the central through hole of the intermediate plate (30) is D, satisfying 1 / 3*D ≤ D1 ≤ 2 / 3*D.

9. The compressor according to claim 1, characterized in that, The cross-section of the heat exchange channel (31) is formed as a circle.

10. An air conditioner, characterized in that, Including an evaporator and the compressor according to any one of claims 1-9, an exhaust port of the evaporator is communicated with an intake port of the compressor, and the intake port is communicated with the working chamber.

Images