Compressors and refrigeration equipment

Abstract

An embodiment of the present invention provides a compressor and a refrigeration device, the compressor includes a shell, a first air outlet port and a second air outlet port are provided on the shell, the first cylinder includes a first working chamber, the second cylinder includes a second working chamber, the second working chamber is connected to the second air outlet port through the inner cavity of the shell, the first partition is located between the first bearing and the first cylinder, the first exhaust port is provided on the first partition and is connected to the first working chamber, the first exhaust port is connected to the first air outlet port through an exhaust channel, the exhaust channel and the inner cavity of the shell are not connected to each other, the exhaust pressure of the first working chamber is greater than the exhaust pressure of the second working chamber, by adding a first partition between the first bearing and the first cylinder, and connecting the first working chamber to the first exhaust port opened on the first partition for exhaust, the sealing of the first working chamber during the exhaust process is effectively improved, so that the actual displacement from the first working chamber can be closer to the theoretically designed displacement, thereby improving the energy efficiency of the compressor.

Description

Technical Field

[0001] The embodiments of the present invention relate to the technical field of compressors, and in particular, to a compressor and a refrigeration device. Background Art

[0002] At present, the rolling rotor twin-cylinder compressor in the related technology refers to a compression assembly that includes two cylinders arranged in the axial direction of the crankshaft. The two cylinders can realize the refrigerant suction, compression and exhaust process. When exhausting, the two cylinders of the twin-cylinder compressor are discharged from the shell through different exhaust channels, thereby realizing the dual exhaust pressure that can only be achieved by two compressors, which can effectively save space and energy consumption. However, in the related technology, it is difficult to achieve complete sealing of the upper and lower cylinders in the twin-cylinder compressor during the exhaust process, resulting in the actual displacement of each exhaust circuit being lower than the theoretical design displacement, thereby affecting energy efficiency. Summary of the invention

[0003] The embodiments of the present invention are intended to solve at least one of the technical problems existing in the prior art.

[0004] To this end, a first aspect of an embodiment of the present invention provides a compressor.

[0005] A second aspect of an embodiment of the present invention provides a refrigeration device.

[0006] In view of this, according to a first aspect of an embodiment of the present invention, a compressor is provided, including a shell, and a first air outlet port and a second air outlet port are provided on the shell, a first bearing is arranged in the shell, a first cylinder is arranged in the shell, the first cylinder includes a first working chamber, and the second cylinder is arranged in the shell, wherein the second cylinder includes a second working chamber, and the second working chamber is connected to the second air outlet port through the inner cavity of the shell, a first partition is located between the first bearing and the first cylinder, a first exhaust port is arranged on the first partition, the first exhaust port is connected to the first working chamber, an exhaust channel is located in the shell, the first exhaust port is connected to the first air outlet port through the exhaust channel, and the exhaust channel and the inner cavity of the shell are not connected to each other, wherein the exhaust pressure of the first working chamber is greater than the exhaust pressure of the second working chamber.

[0007] The compressor provided by the embodiment of the present invention includes a shell, a first bearing, a first cylinder and a first partition, wherein the first partition is arranged between the first bearing and the first cylinder, specifically, the first cylinder includes a first working chamber, and the gas is compressed by the volume change of the first working chamber. Specifically, a first exhaust port is arranged on the side of the first partition facing the first cylinder, and the first exhaust port is connected to the first working chamber, that is, the first working chamber is exhausted through the first exhaust port when compressing the gas and exhausting the gas. Further, the compressor also includes an exhaust channel, and a first air outlet port is opened on the shell, wherein one end of the exhaust channel is connected to the first exhaust port, and the other end of the exhaust channel is connected to the first air outlet port, and the exhaust channel is not connected to the inner cavity of the shell, that is, the exhaust channel through which the first working chamber flows when exhausting the gas is not connected to the inner cavity of the shell, but is directly discharged from the compressor shell through the first air outlet port of the shell. By adding a first partition between the first bearing and the first cylinder and connecting the first working chamber to the first exhaust port opened on the first partition for exhaust, the sealing performance of the first working chamber during exhaust is effectively improved. That is to say, the leakage of the first working chamber to the inner cavity of the shell during exhaust is reduced, thereby increasing the pressure of the gas discharged from the first working chamber, so that the actual displacement from the first working chamber can be closer to the theoretically designed displacement, thereby improving the energy efficiency of the compressor.

[0008] Furthermore, the compressor also includes a second cylinder. Specifically, the second cylinder includes a second working chamber, and the second working chamber is connected to the second gas outlet port through the inner chamber of the shell, wherein the second cylinder and the first cylinder are distributed in the axial direction of the shell, and the two cylinders independently compress the gas, which is conducive to realizing the dual-pressure exhaust of the compressor. Specifically, the first cylinder and the second cylinder can both realize the suction, compression and exhaust processes of the refrigerant. This arrangement avoids the high cost problem caused by setting multiple compressors to realize the dual exhaust function in the related art. One compressor in the present application can realize the functions that can be realized by two compressors in the related art, which reduces the processing cost, reduces the space occupied by the compressor, and is conducive to improving the convenience of the compressor installation process. Furthermore, the present application stipulates that the exhaust pressure of the first working chamber is greater than the exhaust pressure of the second working chamber, that is, the exhaust pressures of the first cylinder and the second cylinder are different. Different exhaust pressures can make the time for the refrigerant to reach the predetermined temperature and the required energy different. It can be understood that according to different usage requirements of the compressor, the first cylinder and the second cylinder realize different exhaust pressures, so that the condensers corresponding to the first cylinder and the second cylinder can efficiently realize the condensation function, avoid wasting energy, make full use of the dual exhaust advantage of the dual-cylinder compressor, and significantly improve the energy efficiency of the compressor.

[0009] Among them, it should be noted that, for the case of a two-cylinder compressor, the first baffle defined in this application is arranged between the first bearing and the first cylinder, and it is not specifically limited that the first bearing and the first cylinder are the upper bearing and the upper cylinder in the two-cylinder compressor. It can be understood that the first bearing can be an upper bearing located in the axial direction of the compressor housing, and the first cylinder can be a lower bearing and a lower cylinder located in the axial direction of the compressor housing, that is, the first baffle can be located between the upper bearing and the upper cylinder, or between the lower bearing and the lower cylinder, and when the first baffle is located between the upper bearing and the upper cylinder, the first air outlet port is connected to the working chamber in the upper cylinder through the exhaust channel and the first exhaust port. Similarly, if the first baffle is located between the lower bearing and the lower cylinder, the first air outlet port is connected to the working chamber in the lower cylinder through the exhaust channel and the first exhaust port, so that the corresponding working chamber can be exhausted and sealed by adding the first baffle, reducing the leakage of the working chamber to the inner cavity of the shell when exhausting, thereby improving the energy efficiency of the compressor.

[0010] It should be noted that the compressor also includes a first piston and a second piston. The first cylinder is processed to have a first accommodating chamber, and the first piston is eccentrically arranged in the first accommodating chamber. The second cylinder is also processed to have a second accommodating chamber, and the second piston is eccentrically arranged in the second accommodating chamber. The first piston can reciprocate in the first accommodating chamber, so that the first piston can realize the suction, compression and exhaust processes by changing the volume of the first working chamber. The second piston can reciprocate in the second accommodating chamber, so that the second piston can realize the suction, compression and exhaust processes by changing the volume of the second working chamber. The dual exhaust function is realized by setting two cylinders and two pistons. The first cylinder and the second cylinder can both realize the suction, compression and exhaust processes of the refrigerant. This setting method avoids the problem of high cost caused by setting multiple compressors to realize the dual exhaust function in the related technology. One compressor in the present application can realize the functions that can be realized by two compressors in the related technology, reduces the processing cost, reduces the occupied space of the compressor, and is conducive to improving the convenience of the compressor installation process.

[0011] In addition, the compressor provided by the above technical solution of the present invention also has the following additional technical features:

[0012] In a possible design, the exhaust channel includes a first exhaust channel and a second exhaust channel, wherein the first exhaust channel is arranged on the first bearing, the first exhaust channel is connected to the first outlet port, the second exhaust channel is arranged on the first partition plate, one end of the second exhaust channel is connected to the first exhaust channel, and the other end of the second exhaust channel is connected to the first exhaust port.

[0013] In this design, the exhaust channel includes a first exhaust channel and a second exhaust channel, wherein, since the exhaust channel is not connected to the inner cavity of the shell, that is, neither of the first exhaust channel and the second exhaust channel is connected to the inner cavity of the shell, it is ensured that the first working chamber connected to the exhaust channel can be exhausted separately from the first outlet port. Specifically, the first exhaust channel is arranged on the first bearing, and the second exhaust channel is arranged on the first partition, wherein the second exhaust channel is arranged on the side of the first partition close to the first bearing, and the second exhaust channel is connected to the first exhaust port, and one end of the first exhaust channel connected to the second exhaust channel is opened on the side of the first bearing close to the first partition, and the first exhaust channel extends in the radial direction inside the first bearing to the end of the first bearing, and passes through the end of the first bearing and communicates with the first outlet port. By arranging the first exhaust channel and the second exhaust channel on the first bearing and combining them into a sealed cavity, the sealing effect of the exhaust channel is improved, and the leakage of the first working chamber to the inner cavity of the shell during exhaust is further prevented, thereby improving the energy efficiency of the compressor.

[0014] In addition, by setting the exhaust channel on the first partition and the first bearing and connecting it with the first cylinder, the originally required length of the exhaust channel is shortened, further reducing the leakage of the first working chamber to the inner cavity of the shell when exhausting, thereby increasing the exhaust pressure of the first working chamber, and eliminating the need to open an additional exhaust channel at a position of the first cylinder away from the vane groove, thereby effectively reducing damage to the first cylinder, ensuring the rigidity of the first cylinder, and thereby improving the reliability of the compressor.

[0015] In a possible design, an axial hole is formed on the first bearing, and the first exhaust channel includes a first side wall close to the axial hole, and a minimum distance between the first side wall and a side wall of the axial hole is L1, wherein L1≥0.5 mm.

[0016] In this design, the first exhaust channel has a first side wall on the side of the shaft hole close to the first bearing, and the minimum distance between the first side wall and the shaft hole side wall is greater than or equal to 0.5 mm. That is to say, by limiting the minimum distance between the first side wall and the shaft hole side wall, the setting position of the first exhaust channel relative to the shaft hole is also limited. If the distance between the first side wall and the shaft hole side wall is too small, the risk of the exhaust channel to the inner cavity of the shell will increase during the exhaust of the first working chamber. Therefore, the position of the first exhaust channel relative to the shaft hole of the first bearing is limited, so as to ensure the sealing of the first exhaust channel, further prevent leakage of the first working chamber during the exhaust process, and improve the energy efficiency of the compressor.

[0017] In a possible design, an axial hole is opened on the first partition plate, and the second exhaust channel includes a second side wall close to the axial hole, and the minimum distance between the second side wall and the side wall of the axial hole is L2, wherein L2≥0.5 mm.

[0018] In this design, the second exhaust channel has a second side wall on the side close to the shaft hole of the first partition, and the minimum distance between the second side wall and the side wall of the shaft hole of the first partition is greater than or equal to 0.5 mm. That is to say, by limiting the minimum distance between the second side wall and the side wall of the shaft hole of the first partition, the setting position of the second exhaust channel relative to the shaft hole of the first partition is also limited. If the distance between the second side wall and the side wall of the shaft hole is too small, the risk of the exhaust channel to the inner cavity of the shell will increase during the exhaust of the first working chamber. Therefore, the position of the second exhaust channel relative to the shaft hole of the first partition is limited, so as to ensure the sealing of the second exhaust channel, further prevent leakage of the first working chamber during the exhaust process, and improve the energy efficiency of the compressor.

[0019] In one possible design, the thickness of the first partition is H1, the depth of the second exhaust channel in the axial direction of the shell is D1, and the height of the first exhaust port in the axial direction of the shell is h1, wherein the thickness H1 of the first partition, the depth D1 of the second exhaust channel and the height h1 of the first exhaust port satisfy, H1-D1>5×min(D1-h1).

[0020] In this design, the relationship between the thickness of the first baffle, the depth of the second exhaust channel in the axial direction of the shell and the height of the first exhaust port in the axial direction of the shell is limited to meet H1-D1>5×min(D1-h1), that is, the height of the first exhaust port relative to the first baffle and the depth of the second exhaust channel opened on the first baffle are limited. Specifically, if the second exhaust channel is too deep, the structural strength of the first baffle will be reduced, and the stability of the compressor will be reduced. If the second exhaust channel is too shallow, the effective flow area of ​​the exhaust channel cannot be guaranteed. At the same time, if the height of the first exhaust port in the axial direction of the shell is too high, the second exhaust channel is connected to the first exhaust port. The depth of one section is shallow, and thus the gas flow area cannot be guaranteed. If the height of the first exhaust port in the axial direction of the shell is too low, the second exhaust channel is connected to the first exhaust channel and the first exhaust port at the same time, and the channel depth to be opened is deeper, thereby reducing the structural strength of the first partition. Therefore, the relationship between the thickness of the first partition, the depth of the second exhaust channel in the axial direction of the shell and the height of the first exhaust port in the axial direction of the shell is limited, that is, the processing technology of the first partition is limited, thereby ensuring the flatness of the sealing surface of the first partition, while improving the stability of the compressor, further preventing leakage of the first working chamber to the inner cavity of the shell when exhausting, thereby improving the energy efficiency of the compressor.

[0021] In one possible design, the thickness of the first bearing is H2, and the depth of the first exhaust channel along the axial direction of the shell is D2, wherein the thickness H2 of the first bearing, the depth D2 of the first exhaust channel and the height h1 of the first exhaust port satisfy, H2-D2>5×min(D2-h1).

[0022] In this design, the relationship between the thickness of the first bearing, the depth of the first exhaust channel in the axial direction of the shell and the height of the first exhaust port in the axial direction of the shell is limited to satisfy H2-D2>5×min(D2-h1). That is to say, the depth of the second exhaust channel opened on the first bearing is limited, that is, the effective flow area of ​​the sealed exhaust channel connected to the first working chamber is limited. Specifically, if the first exhaust channel is too deep, the structural strength of the first bearing will be reduced, and the stability of the compressor will be reduced. If the first exhaust channel is too shallow, the effective flow area of ​​the exhaust channel cannot be guaranteed. Therefore, the relationship between the thickness of the first bearing, the depth of the first exhaust channel in the axial direction of the shell and the height of the first exhaust port in the axial direction of the shell is limited, that is, the processing technology of the first bearing is limited, thereby ensuring the flatness of the sealing surface of the first bearing. While improving the stability of the compressor, it further prevents leakage to the inner cavity of the shell when the first working chamber is exhausted, thereby improving the energy efficiency of the compressor.

[0023] In a possible design, the maximum cross-sectional area of ​​the first exhaust port is S1, and the minimum cross-sectional area of ​​the exhaust passage is S2, wherein S1 and S2 satisfy:

[0024] In this design, the range of the ratio of the maximum cross-sectional area of ​​the first exhaust port to the minimum cross-sectional area of ​​the exhaust channel is further limited. Specifically, the ratio of the maximum cross-sectional area of ​​the first exhaust port to the minimum cross-sectional area of ​​the exhaust channel is greater than or equal to 0.6, thereby ensuring the flow area of ​​the exhaust channel.

[0025] In a possible design, a line is connected between a center point of the first exhaust port and a center point of the first partition, and the line extends in the axial direction of the shell to form a first surface; the exhaust channel includes a second exhaust port on one side close to the first outlet port, and the second exhaust port is respectively connected to the first outlet port and the first exhaust port, and the center line of the second exhaust port can pass through the center of the first bearing, and the center line extends in the axial direction of the shell to form a second surface; an angle θ is formed between the first surface and the second surface, wherein the angle θ satisfies, 140°≤θ≤330°.

[0026] In this design, the range of values ​​of the angle between the center line of the exhaust channel and the first exhaust port along the radial direction of the first partition is limited. Specifically, the center point of the first exhaust port is connected with the axis of the first partition, and the exhaust channel has a second exhaust port on the side close to the first outlet port, and the center line of the second exhaust port can pass through the center of the first bearing. The connecting line and the center line of the second exhaust port extend along the axial direction of the shell to form a first surface and a second surface, respectively, wherein the first surface and the second surface form an angle θ in the extension direction, and the angle θ satisfies 140°≤θ≤330°, which can reduce the tooling interference between the various parts of the compressor during the assembly process, facilitate the manufacture of the compressor, and improve the assembly efficiency.

[0027] In a possible design, the compressor further includes: a second bearing spaced apart from the first bearing, and the first cylinder and the second cylinder are located between the first bearing and the second bearing.

[0028] In this design, the compressor also includes a second bearing, wherein the second bearing and the first bearing are spaced apart in the axial direction of the shell, and the first cylinder and the second cylinder are arranged between the first bearing and the second bearing. Specifically, the first bearing can provide support for the crankshaft, and the second bearing can provide support for the first cylinder and the second cylinder, thereby improving the installation stability of the first cylinder and the second cylinder.

[0029] In a possible design, the compressor further includes: a second partition plate, the second partition plate is located between the first cylinder and the second cylinder; the first bearing and the second partition plate are in contact with the first cylinder, and the second bearing and the second partition plate are in contact with the second cylinder.

[0030] In this design, the compressor also includes a second partition. Specifically, the second partition is arranged between the first cylinder and the second cylinder, and the first cylinder and the second cylinder are also arranged between the first bearing and the second bearing, so that the first bearing and the second partition block the first accommodating cavity of the first cylinder located therebetween, and the second bearing and the second partition block the second accommodating cavity of the second cylinder located therebetween.

[0031] It should be noted that the compressor also includes a first vane assembly and a second vane assembly, wherein the first cylinder includes a first vane groove, the second cylinder includes a second vane groove, the first vane assembly is arranged in the first vane groove, the second vane assembly is arranged in the second vane groove, the first vane assembly, the outer peripheral surface of the first piston and the inner surface of the first cylinder form a first working chamber, the second vane assembly, the outer peripheral surface of the second piston and the inner surface of the second cylinder form a second working chamber, the movement of the first piston can change the volume of the first working chamber to compress the gas, and the movement of the second piston can change the volume of the second working chamber to compress the gas.

[0032] In a possible design, the compressor also includes: a second air outlet port, which is arranged on the shell; a third exhaust port, which is connected to the second working chamber, and the third exhaust port is connected to the second air outlet port through the inner cavity of the shell; an air outlet channel, and the third exhaust port is connected to the inner cavity of the shell through the air outlet channel; the air outlet channel and the exhaust channel are not connected to each other.

[0033] In this design, the compressor also includes a second air outlet port. Specifically, the second air outlet port is arranged at the top of the shell, and the third exhaust port is connected to the second working chamber, wherein the second working chamber is connected to the inner chamber of the shell through the air outlet channel from the third exhaust port, and is discharged from the shell through the second air outlet port. In other words, after the gas in the second working chamber is discharged through the third exhaust outlet, it diffuses into the inner chamber of the shell, and then is discharged through the second air outlet port. Since the exhaust pressure of the second cylinder is lower than the exhaust pressure of the first cylinder, the gas pressure in the inner chamber of the shell is relatively low, which is convenient for the oil return of the compressor and is conducive to ensuring the reliability of the operation of the compressor.

[0034] In a possible design, the compressor further includes: an air intake port is provided on the shell, the compressor further includes a first air intake channel and a second air intake channel, the first working chamber is connected to the air intake port via the first air intake channel, and the second working chamber is connected to the air intake port via the second air intake channel. Furthermore, the first air intake channel and the second air intake channel are connected to each other.

[0035] In this design, an air intake port may be provided on the housing, so that the first working chamber and the second working chamber are both connected to the air intake port. Specifically, the first working chamber is connected to the air intake port via the first air intake channel, and the second working chamber is connected to the air intake port via the second air intake channel. The first air intake channel and the second air intake channel are preferably connected to each other, so as to reduce the total length of the air intake channel, avoid excessive processing of components such as cylinders and bearings to affect rigidity, and reduce production costs.

[0036] In a possible design, the compressor also includes: two intake ports are provided on the shell, the compressor also includes a first intake channel and a second intake channel, the first working chamber is connected to one intake port through the first intake channel, the second working chamber is connected to another intake port through the second intake channel, and the first intake channel and the second intake channel are not connected to each other.

[0037] In this design, two intake ports are provided on the shell, and one working chamber is connected to one intake port, so that the gases in the two intake channels will not mix with each other, which is beneficial to ensure the intake volume of each cylinder.

[0038] It should be noted that the first air intake passage is arranged on the first cylinder or the first bearing or the second partition plate, and the second air intake passage is arranged on the second cylinder or the second bearing or the second partition plate.

[0039] According to a second aspect of the present invention, there is provided a refrigeration device, comprising a compressor as provided by any of the above technical solutions, thereby having all the beneficial technical effects of the compressor, which will not be described one by one here.

[0040] In one possible design, the refrigeration equipment also includes: a first condenser, connected to the first air outlet port of the compressor; a first throttling element, connected to the first condenser; a first evaporator, connected to the first throttling element; a first liquid reservoir, connected to the first evaporator and the first air intake channel of the compressor; a second condenser, connected to the second air outlet port of the compressor; a second throttling element, connected to the second condenser; a second evaporator, connected to the second throttling element; a second liquid reservoir, connected to the second evaporator and the second air intake channel of the compressor.

[0041] In this design, the compressor and the first condenser, the first throttling element, the first evaporator, and the first liquid reservoir form a first refrigeration system, and the compressor and the second condenser, the second throttling element, the second evaporator, and the second liquid reservoir form a second refrigeration system. The two independent refrigeration systems, that is, the refrigeration equipment realizes the multi-exhaust function realized by multiple compressors in the related art through one compressor, which reduces the processing cost of the refrigeration equipment, reduces the occupied space of the refrigeration equipment, and improves the convenience of installing the internal components of the refrigeration equipment. Since the exhaust pressures of the first cylinder and the second cylinder are different, the exhaust pressures reaching the first condenser and the second condenser are different, which can make the refrigeration equipment have double condensation temperatures and double evaporation temperatures, which is conducive to realizing the cascade utilization of energy and improving the energy efficiency of the refrigeration equipment. In particular, when the displacements of the first cylinder and the second cylinder are different, the amount of refrigerant condensed by the first condenser and the second condenser is also different, further improving the energy efficiency of the refrigeration equipment.

[0042] In one possible design, the refrigeration equipment also includes: a third condenser, connected to the first air outlet port of the compressor; a third throttling element, connected to the third condenser; a third evaporator, connected to the third throttling element; a third liquid reservoir, connecting the third evaporator and the first air intake channel and the second air intake channel of the compressor; a fourth condenser, connected to the second air outlet port of the compressor; a fourth throttling element, connected to the fourth condenser; a fourth evaporator, connected to the fourth throttling element; the third liquid reservoir also connects the fourth evaporator and the first air intake channel and the second air intake channel of the compressor.

[0043] In this design, the compressor and the third condenser, the third throttling element, the third evaporator, and the third liquid reservoir form a third refrigeration system, and the compressor and the fourth condenser, the fourth throttling element, the fourth evaporator, and the third liquid reservoir form a fourth refrigeration system. The two independent refrigeration systems, that is, the refrigeration equipment realizes the multi-exhaust function realized by multiple compressors in the related art through one compressor, which reduces the processing cost of the refrigeration equipment and the occupied space of the refrigeration equipment, and improves the convenience of installing the internal components of the refrigeration equipment. The first suction channel and the second suction channel are connected to the third liquid reservoir, so that the setting of one liquid reservoir can meet the suction function of the first cylinder and the second cylinder, reducing the number of components in the refrigeration equipment, further reducing the processing cost of the refrigeration equipment, effectively reducing the volume of the refrigeration equipment, and improving the convenience of installing the refrigeration equipment. Moreover, due to the different exhaust pressures of the first cylinder and the second cylinder, the exhaust pressures reaching the third condenser and the fourth condenser are different, which can make the refrigeration equipment have double condensation temperature and double evaporation temperature, which is conducive to realizing the cascade utilization of energy and improving the energy efficiency of the refrigeration equipment. In particular, when the displacements of the first cylinder and the second cylinder are different, the amounts of refrigerant condensed by the third condenser and the fourth condenser are also different, thereby further improving the energy efficiency of the refrigeration equipment.

[0044] Additional aspects and advantages according to the present invention will be given in part in the following description, and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0045] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0046] Figure 1 A schematic structural diagram of a compressor according to an embodiment of the present invention is shown;

[0047] Figure 2 A schematic structural diagram of a compressor according to another embodiment of the present invention is shown;

[0048] Figure 3 A schematic structural diagram of a first baffle according to an embodiment of the present invention is shown;

[0049] Figure 4 A schematic structural diagram of a first baffle according to another embodiment of the present invention is shown;

[0050] Figure 5 A schematic structural diagram of a first bearing according to an embodiment of the present invention is shown;

[0051] Figure 6 A schematic structural diagram of a first bearing according to another embodiment of the present invention is shown;

[0052] Figure 7 A schematic structural diagram of a compressor according to another embodiment of the present invention is shown;

[0053] Figure 8 A schematic structural diagram of a refrigeration device according to an embodiment of the present invention is shown;

[0054] Fig. 9 A structural schematic diagram of a refrigeration device according to another embodiment of the present invention is shown.

[0055] in, Figures 1 to 9 The corresponding relationship between the reference numerals and the component names is as follows:

[0056] 100 compressor, 110 housing, 112 first air outlet port, 114 second air outlet port, 120 first bearing, 130 second bearing, 140 first cylinder, 150 second cylinder, 160 first partition, 170 second partition, 180 first exhaust port, 190 exhaust channel, 192 first exhaust channel, 194 second exhaust channel, 200 crankshaft, 210 air outlet channel, 220 first exhaust valve, 300 first condenser, 310 first throttling element, 320 first evaporator, 330 first liquid reservoir, 340 second condenser, 350 second throttling element, 360 second evaporator, 370 second liquid reservoir, 380 first intake channel, 390 second intake channel, 400 third condenser, 410 third throttling element, 420 third evaporator, 430 third liquid reservoir, 440 fourth condenser, 450 fourth throttling element, 460 fourth evaporator. DETAILED DESCRIPTION

[0057] In order to more clearly understand the above-mentioned purpose, features and advantages of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict.

[0058] In the following description, many specific details are set forth to facilitate a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited to the specific embodiments disclosed below.

[0059] Refer to the following Figures 1 to 9 The compressor and refrigeration equipment provided according to some embodiments of the present invention are described.

[0060] Embodiment 1:

[0061] like Figure 1 , Figure 2 and Figure 6As shown, an embodiment of the first aspect of the present invention provides a compressor 100, including a shell 110, and a first air outlet port 112 and a second air outlet port 114 are provided on the shell 110, a first bearing 120 is arranged in the shell 110, a first cylinder 140 is arranged in the shell 110, the first cylinder 140 includes a first working chamber, and a second cylinder 150 is arranged in the shell 110, wherein the second cylinder 150 includes a second working chamber, and the second working chamber is connected to the second air outlet port 114 through the inner chamber of the shell 110, a first partition plate 160 is located between the first bearing 120 and the first cylinder 140, a first exhaust port 180 is provided on the first partition plate 160, and the first exhaust port 180 is connected to the first working chamber, an exhaust channel 190 is located in the shell 110, and the first exhaust port 180 is connected to the first air outlet port 112 through the exhaust channel 190, and the exhaust channel 190 is not connected to the inner chamber of the shell 110, wherein the exhaust pressure of the first working chamber is greater than the exhaust pressure of the second working chamber.

[0062] The compressor 100 provided in the embodiment of the present invention includes a housing 110, a first bearing 120, a first cylinder 140 and a first partition 160, wherein the first partition 160 is disposed between the first bearing 120 and the first cylinder 140, specifically, the first cylinder 140 includes a first working chamber, and the gas is compressed by the volume change of the first working chamber. Specifically, the first partition 160 is provided with a first exhaust port 180 on one side facing the first cylinder 140, and the first exhaust port 180 is connected to the first working chamber, that is, the first working chamber is exhausted through the first exhaust port 180 when compressing the gas and exhausting the gas. Furthermore, the compressor 100 also includes an exhaust channel 190, and a first air outlet port 112 is opened on the shell 110, wherein one end of the exhaust channel 190 is connected to the first exhaust port 180, and the other end of the exhaust channel 190 is connected to the first air outlet port 112, and the exhaust channel 190 is not connected to the inner cavity of the shell 110, that is, the exhaust channel 190 through which the first working chamber flows when exhausting is not connected to the inner cavity of the shell 110, but is directly discharged from the compressor 100 shell 110 through the first air outlet port 112 of the shell 110. By adding a first partition plate 160 between the first bearing 120 and the first cylinder 140, and connecting the first working chamber to the first exhaust port 180 opened on the first partition plate 160 for exhaust, the sealing performance of the first working chamber during the exhaust process is effectively improved. In other words, the leakage of the first working chamber to the inner cavity of the shell 110 during exhaust is reduced, thereby increasing the pressure of the gas discharged from the first working chamber, so that the actual displacement from the first working chamber can be closer to the theoretically designed displacement, thereby improving the energy efficiency of the compressor 100.

[0063] Furthermore, the compressor 100 also includes a second cylinder 150. Specifically, the second cylinder 150 includes a second working chamber, wherein the second cylinder 150 and the first cylinder 140 are distributed in the axial direction of the housing 110, and the two cylinders independently compress the gas, which is conducive to realizing the dual-pressure exhaust of the compressor 100. Specifically, the first cylinder 140 and the second cylinder 150 can both realize the suction, compression and exhaust processes of the refrigerant. This arrangement avoids the high cost problem caused by setting multiple compressors 100 in the related art to realize the dual exhaust function. In the present application, one compressor 100 can realize the functions that can be realized by two compressors 100 in the related art, which reduces the processing cost, reduces the occupied space of the compressor 100, and is conducive to improving the convenience of the installation process of the compressor 100. Furthermore, the present application stipulates that the exhaust pressure of the first working chamber is greater than the exhaust pressure of the second working chamber, that is, the exhaust pressures of the first cylinder 140 and the second cylinder 150 are different. Different exhaust pressures can make the time for the refrigerant to reach the predetermined temperature and the required energy different. It can be understood that according to different usage requirements of the compressor 100, the first cylinder 140 and the second cylinder 150 achieve different exhaust pressures, so that the condensers corresponding to the first cylinder 140 and the second cylinder 150 can efficiently realize the condensation function, avoid wasting energy, and make full use of the dual exhaust advantage of the dual-cylinder compressor 100, thereby significantly improving the energy efficiency of the compressor 100.

[0064] It should be noted that the compressor 100 also includes a first piston and a second piston. The first cylinder 140 is machined to have a first accommodating chamber, and the first piston is eccentrically arranged in the first accommodating chamber. The second cylinder 150 is also machined to have a second accommodating chamber, and the second piston is eccentrically arranged in the second accommodating chamber. The first piston can reciprocate in the first accommodating chamber, so that the first piston can realize the suction, compression and exhaust process by changing the volume of the first working chamber. The second piston can reciprocate in the second accommodating chamber, so that the second piston can realize the suction, compression and exhaust process by changing the volume of the second working chamber. The dual exhaust function is realized by setting two cylinders and two pistons. The first cylinder 140 and the second cylinder 150 can both realize the suction, compression and exhaust process of the refrigerant. This setting method avoids the problem of high cost caused by setting multiple compressors 100 in the related art to realize the dual exhaust function. One compressor 100 in the present application can realize the functions that can be realized by two compressors 100 in the related art, thereby reducing the processing cost, reducing the occupied space of the compressor 100, and being conducive to improving the convenience of the installation process of the compressor 100.

[0065] It should be noted that, for the case of a two-cylinder compressor 100, the first partition plate 160 defined in the present application is disposed between the first bearing 120 and the first cylinder 140, but does not specifically define the first bearing 120 and the first cylinder 140 as the upper bearing and the upper cylinder in the two-cylinder compressor 100. It can be understood that the first bearing 120 can be an upper bearing located in the axial direction of the compressor housing 110, and the first cylinder 140 can be a lower bearing and a lower cylinder located in the axial direction of the compressor housing 110. That is to say, the first partition plate 160 can be located between the upper bearing and the upper cylinder, or between the lower bearing and the lower cylinder. When the first partition plate 160 is located between the upper bearing and the upper cylinder, the first gas outlet port 112 is connected to the working chamber in the upper cylinder via the exhaust passage 190 and the first exhaust port 180. Similarly, if the first partition plate 160 is located between the lower bearing and the lower cylinder, the first gas outlet port 112 is connected to the working chamber in the lower cylinder via the exhaust passage 190 and the first exhaust port 180. Therefore, by adding the first partition plate 160, the corresponding working chamber can be exhausted and sealed, thereby reducing the leakage of the working chamber to the inner cavity of the housing 110 when exhausting, thereby improving the energy efficiency of the compressor 100.

[0066] In another specific embodiment, the first baffle 160 is disposed between the second bearing 130 and the second cylinder 150, the first exhaust port 180 is provided on the side of the first baffle 160 facing the second cylinder 150, the first exhaust port 180 is communicated with the second working chamber, a second exhaust channel 194 is provided on the side of the first baffle 160 facing the second bearing 130, a first exhaust channel 192 is provided on the side of the second bearing 130 facing the first baffle, one end of the first exhaust channel 192 is communicated with the second exhaust channel 194, the other end of the first exhaust channel 192 is provided inside the second bearing 130 and extends along the radial direction of the second bearing 130 to the end of the second bearing 130 and communicates with the first outlet port 112, so that the second working chamber is discharged from the first exhaust port 180 through the second exhaust channel 194, the first exhaust channel 192, and the first outlet port 112 to the housing. The first working chamber is diffused from the third exhaust port to the inner cavity of the housing through the outlet channel 210, and discharged to the housing through the second outlet port 114 at the top. By arranging the first partition 160 between the second bearing 130 and the second cylinder 150, the exhaust process of the second working chamber can be sealed to prevent the second working chamber from leaking into the inner cavity of the shell during exhaust, thereby increasing the pressure of the gas discharged from the second working chamber, making the actual displacement from the second working chamber closer to the theoretically designed displacement, thereby improving the energy efficiency of the compressor 100.

[0067] Embodiment 2:

[0068] Based on the above embodiment, the specific structure of the exhaust passage 190 is explained and illustrated. Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6 As shown, further, the exhaust channel 190 includes a first exhaust channel 192 and a second exhaust channel 194, wherein the first exhaust channel 192 is arranged on the first bearing 120, the first exhaust channel 192 is connected to the first outlet port 112, the second exhaust channel 194 is arranged on the first partition plate 160, one end of the second exhaust channel 194 is connected to the first exhaust channel 192, and the other end of the second exhaust channel 194 is connected to the first exhaust port 180.

[0069] In this embodiment, the exhaust channel 190 includes a first exhaust channel 192 and a second exhaust channel 194, wherein the exhaust channel 190 is not connected to the inner cavity of the housing 110, that is, neither of the first exhaust channel 192 and the second exhaust channel 194 is connected to the inner cavity of the housing 110, so as to ensure that the first working chamber connected to the exhaust channel 190 can be exhausted separately from the first gas outlet port 112. Specifically, the first exhaust channel 192 is arranged on the first bearing 120, and the second exhaust channel 194 is arranged on the first partition 160, wherein the second exhaust channel 194 is arranged on a side of the first partition 160 close to the first bearing 120, and the second exhaust channel 194 is connected to the first exhaust port 180, and one end of the first exhaust channel 192 connected to the second exhaust channel 194 is opened on a side of the first bearing 120 close to the first partition 160, and the first exhaust channel 192 extends in the radial direction inside the first bearing 120 to the end of the first bearing 120, and passes through the end of the first bearing 120 to communicate with the first gas outlet port 112. By arranging the first exhaust channel 192 and the second exhaust channel 194 on the first bearing 120 and the first partition plate 160 and combining them into a sealed cavity, the sealing effect of the exhaust channel 190 is improved, and the leakage of the first working chamber to the inner cavity of the shell 110 during exhaust is further prevented, thereby improving the energy efficiency of the compressor 100.

[0070] In addition, by setting the exhaust channel 190 on the first partition 160 and the first bearing 120 and connecting it with the first cylinder 140, the originally required length of the exhaust channel 190 is shortened, and the leakage to the inner cavity of the shell 110 when the first working chamber is exhausted is further reduced, thereby increasing the exhaust pressure of the first working chamber. There is no need to open an additional exhaust channel 190 at a position of the first cylinder 140 away from the vane groove, thereby effectively reducing damage to the first cylinder 140, ensuring the rigidity of the first cylinder 140, and further improving the reliability of the compressor 100.

[0071] Among them, it should be noted that a second exhaust groove is opened on the side of the first partition plate 160 facing the first bearing 120, and the second exhaust groove is connected to the first exhaust port 180. A first exhaust groove is opened on the side of the first bearing 120 facing the first partition plate 160, and the first exhaust groove and the second exhaust groove together constitute a sealed cavity. A third exhaust channel is also opened inside the first bearing 120, and the third exhaust channel is connected to the sealed cavity, so that the sealed cavity composed of the first exhaust groove and the second exhaust groove and the third exhaust channel together constitute an exhaust channel that is not connected to the inner cavity of the shell, and the exhaust channel is connected to the first working chamber, so that when the first working chamber inhales, compresses and exhausts, it is not connected to the first exhaust port 180 through the exhaust channel to the first outlet port 112, but is directly discharged from the compressor 100 shell 110 through the first outlet port 112 of the shell 110. Furthermore, by adding a first partition plate 160 between the first bearing 120 and the first cylinder 140, the leakage of the first working chamber into the inner cavity of the shell 110 during exhaust is effectively reduced, thereby increasing the pressure of the gas discharged from the first working chamber, making the actual displacement from the first working chamber closer to the theoretically designed displacement, thereby improving the energy efficiency of the compressor 100.

[0072] Embodiment three:

[0073] On the basis of any of the above embodiments, further, an axial hole is opened on the first bearing 120, and the first exhaust channel 192 includes a first side wall close to the axial hole, and the minimum distance between the first side wall and the side wall of the axial hole is L1, wherein L1≥0.5mm.

[0074] In this embodiment, the first exhaust channel 192 has a first side wall on the side of the shaft hole close to the first bearing 120, and the minimum distance between the first side wall and the shaft hole side wall is greater than or equal to 0.5 mm. That is, by limiting the minimum distance between the first side wall and the shaft hole side wall, the setting position of the first exhaust channel 192 relative to the shaft hole is also limited. If the distance between the first side wall and the shaft hole side wall is too small, the risk of the exhaust channel 190 to the inner cavity of the housing 110 will increase during the exhaust of the first working chamber. Therefore, the position of the first exhaust channel 192 relative to the shaft hole of the first bearing 120 is limited, so that the sealing of the first exhaust channel 192 can be ensured, further preventing leakage of the first working chamber during the exhaust process, and improving the energy efficiency of the compressor 100.

[0075] like Figure 3 and Figure 4 As shown, further, an axial hole is opened on the first partition plate 160, and the second exhaust channel 194 includes a second side wall close to the axial hole, and the minimum distance between the second side wall and the side wall of the axial hole is L2, wherein L2≥0.5mm.

[0076] In this embodiment, the second exhaust channel 194 has a second side wall on the side close to the shaft hole of the first partition 160, and the minimum distance between the second side wall and the side wall of the shaft hole of the first partition 160 is greater than or equal to 0.5 mm. That is, by limiting the minimum distance between the second side wall and the side wall of the shaft hole of the first partition 160, the setting position of the second exhaust channel 194 relative to the shaft hole of the first partition 160 is defined. If the distance between the second side wall and the side wall of the shaft hole is too small, the risk of the exhaust channel 190 to the inner cavity of the shell 110 will increase during the exhaust of the first working chamber. Therefore, the position of the second exhaust channel 194 relative to the shaft hole of the first partition 160 is limited, so as to ensure the sealing of the second exhaust channel 194, further prevent leakage of the first working chamber during the exhaust process, and improve the energy efficiency of the compressor 100.

[0077] Embodiment 4:

[0078] Based on any of the above embodiments, the relationship between the thickness of the first partition plate 160, the depth of the second exhaust channel 194 and the first exhaust port 180 is defined, such as: Figure 7 As shown, further, the thickness of the first baffle 160 is H1, the depth of the second exhaust channel 194 in the axial direction of the shell 110 is D1, and the height of the first exhaust port 180 in the axial direction of the shell 110 is h1, wherein the thickness H1 of the first baffle 160, the depth D1 of the second exhaust channel 194 and the height h1 of the first exhaust port 180 satisfy, H1-D1>5×min(D1-h1).

[0079] In this embodiment, the relationship between the thickness of the first baffle 160, the depth of the second exhaust channel 194 in the axial direction of the shell 110 and the height of the first exhaust port 180 in the axial direction of the shell 110 is defined to satisfy H1-D1>5×min(D1-h1), that is, the height of the first exhaust port 180 relative to the first baffle 160 and the depth of the second exhaust channel 194 opened on the first baffle 160 are defined. Specifically, if the second exhaust channel 194 is too deep, the structural strength of the first baffle 160 will be reduced, and the stability of the compressor 100 will be reduced. If the second exhaust channel 194 is too shallow, the effective flow area of ​​the exhaust channel 190 cannot be guaranteed. At the same time, if the height of the first exhaust port 180 in the axial direction of the shell 110 is too high, the second exhaust channel 194 and the first exhaust port 1 The depth of the section connected to 80 is relatively shallow, and thus the gas flow area cannot be guaranteed. If the height of the first exhaust port 180 in the axial direction of the shell 110 is too low, the second exhaust channel 194 is connected to the first exhaust channel 192 and the first exhaust port 180 at the same time, and the channel depth required to be opened is relatively deep, thereby reducing the structural strength of the first partition 160. Therefore, the relationship between the thickness of the first partition 160, the depth of the second exhaust channel 194 along the axial direction of the shell 110 and the height of the first exhaust port 180 in the axial direction of the shell 110 is limited, that is, the processing technology of the first partition 160 is limited, thereby ensuring the flatness of the sealing surface of the first partition 160, while improving the stability of the use of the compressor 100, further preventing the leakage of the first working chamber to the inner cavity of the shell 110 when exhausting, thereby improving the energy efficiency of the compressor 100.

[0080] Based on the above embodiment, the relationship between the thickness of the first bearing 120, the depth of the first exhaust passage 192 and the first exhaust port 180 is defined as follows: Figure 7 As shown, further, the thickness of the first bearing 120 is H2, and the depth of the first exhaust channel 192 along the axial direction of the housing 110 is D2, wherein the thickness H2 of the first bearing 120, the depth D2 of the first exhaust channel 192 and the height h1 of the first exhaust port 180 satisfy, H2-D2>5×min(D2-h1).

[0081] In this embodiment, the relationship between the thickness of the first bearing 120, the depth of the first exhaust passage 192 in the axial direction of the housing 110, and the height of the first exhaust port 180 in the axial direction of the housing 110 is defined to satisfy H2-D2>5×min(D2-h1), that is, the depth of the second exhaust passage 194 opened on the first bearing 120 is defined, that is, the effective flow area of ​​the sealed exhaust passage 190 connected to the first working chamber is defined. Specifically, if the first exhaust passage 192 is too deep, the structural strength of the first bearing 120 will be reduced, and the compressor 100 will be reduced. Stability in use: If the first exhaust channel 192 is too shallow, the effective flow area of ​​the exhaust channel 190 cannot be guaranteed. Therefore, the relationship between the thickness of the first bearing 120, the depth of the first exhaust channel 192 in the axial direction of the shell 110, and the height of the first exhaust port 180 in the axial direction of the shell 110 is limited, that is, the processing technology of the first bearing 120 is limited, thereby ensuring the flatness of the sealing surface of the first bearing 120. While improving the stability of use of the compressor 100, it further prevents leakage of the first working chamber into the inner cavity of the shell 110 when exhausting, thereby improving the energy efficiency of the compressor 100.

[0082] Embodiment five:

[0083] On the basis of any of the above embodiments, further, the maximum cross-sectional area of ​​the first exhaust port 180 is S1, and the minimum cross-sectional area of ​​the exhaust channel 190 is S2, wherein S1 and S2 satisfy:

[0084] In this embodiment, the value range of the ratio of the maximum cross-sectional area of ​​the first exhaust port 180 to the minimum cross-sectional area of ​​the exhaust channel 190 is further limited. Specifically, the ratio of the maximum cross-sectional area of ​​the first exhaust port 180 to the minimum cross-sectional area of ​​the exhaust channel 190 is greater than or equal to 0.6, thereby ensuring the flow area of ​​the exhaust channel 190.

[0085] Embodiment six:

[0086] On the basis of any of the above embodiments, further, a line is connected between the center point of the first exhaust port 180 and the center point of the first partition 160, and the line extends in the axial direction of the shell 110 to form a first surface; the exhaust channel 190 includes a second exhaust port on the side close to the first gas outlet port 112, and the second exhaust port is respectively connected to the first gas outlet port 112 and the first exhaust port 180, and the center line of the second exhaust port can pass through the center of the first bearing 120, and the center line extends in the axial direction of the shell 110 to form a second surface; an angle θ is formed between the first surface and the second surface, wherein the angle θ satisfies, 140°≤θ≤330°.

[0087] In this embodiment, the value range of the angle between the center line of the exhaust channel 190 and the first exhaust port 180 along the radial direction of the first partition 160 is limited. Specifically, the center point of the first exhaust port 180 is connected with the axis of the first partition 160, and the exhaust channel 190 has a second exhaust port on the side close to the first outlet port 112, and the center line of the second exhaust port can pass through the center of the first bearing 120. The connecting line and the center line of the second exhaust port extend along the axial direction of the shell 110 to form a first surface and a second surface, respectively, wherein the first surface and the second surface form an angle θ in the extension direction, and the angle θ satisfies 140°≤θ≤330°, which can reduce the tooling interference between the various components of the compressor 100 during the assembly process, facilitate the manufacture of the compressor 100, and improve the assembly efficiency.

[0088] Embodiment seven:

[0089] Based on any of the above embodiments, Figure 1 and Figure 2 As shown, further, the compressor 100 also includes: a second bearing 130 , which is spaced apart from the first bearing 120 , and the first cylinder 140 and the second cylinder 150 are located between the first bearing 120 and the second bearing 130 .

[0090] In this embodiment, the compressor 100 also includes a second bearing 130, wherein the second bearing 130 and the first bearing 120 are spaced apart in the axial direction of the housing 110, and the first cylinder 140 and the second cylinder 150 are arranged between the first bearing 120 and the second bearing 130. Specifically, the first bearing 120 can provide support for the crankshaft 200, and the second bearing 130 can provide support for the first cylinder 140 and the second cylinder 150, thereby improving the installation stability of the first cylinder 140 and the second cylinder 150.

[0091] like Figure 1 and Figure 2 As shown, further, the compressor 100 also includes: a second partition 170, the second partition 170 is located between the first cylinder 140 and the second cylinder 150; the first bearing 120 and the second partition 170 are abutted against the first cylinder 140, and the second bearing 130 and the second partition 170 are abutted against the second cylinder 150.

[0092] In this embodiment, the compressor 100 also includes a second partition plate 170. Specifically, the second partition plate 170 is disposed between the first cylinder 140 and the second cylinder 150. The first cylinder 140 and the second cylinder 150 are also disposed between the first bearing 120 and the second bearing 130, so that the first bearing 120 and the second partition plate 170 block the first accommodating cavity of the first cylinder 140 located therebetween, and the second bearing 130 and the second partition plate 170 block the second accommodating cavity of the second cylinder 150 located therebetween.

[0093] In a specific embodiment, further, the second plate includes a first plate and a second plate, and the first plate and the second plate form a cavity, so that a third exhaust port can be set on the second plate, so that the compressed air in the second working chamber can be discharged into the cavity of the second partition plate 170 through the third exhaust port, and then the compressed air is discharged to the second air outlet port 114 through the air outlet channel 210. At this time, a first exhaust port 180 is provided on the first partition plate 160, and the compressed air in the first working chamber can be discharged to the first air outlet port 112 through the first exhaust port 180, ensuring that the first cylinder 140 and the second cylinder 150 can realize independent exhaust functions, thereby realizing the dual-pressure exhaust function of the compressor 100.

[0094] In another specific embodiment, further, the second partition plate 170 includes a first plate, a second plate and a partition plate, and the partition plate separates the cavities in the first plate and the second plate, thereby dividing the cavities into two independent cavities. At this time, a first exhaust port 180 can be provided on the first plate, so that the compressed air in the first working chamber can be discharged into one of the cavities through the first exhaust port 180, and then the compressed air is discharged to the first air outlet port 112 through the exhaust channel 190. A third exhaust port can also be provided on the second plate, and the compressed air in the second working chamber is discharged into another cavity through the third exhaust port, and then the compressed air is discharged to the second air outlet port 114 through the inner cavity of the shell 110. It is ensured that the exhaust processes of the first cylinder 140 and the second cylinder 150 do not affect each other, and the dual-pressure exhaust function of the compressor 100 is realized.

[0095] Furthermore, the compressor 100 also includes a first vane assembly and a second vane assembly, wherein the first cylinder 140 includes a first vane groove, the second cylinder 150 includes a second vane groove, the first vane assembly is arranged in the first vane groove, the second vane assembly is arranged in the second vane groove, the first vane assembly, the outer peripheral surface of the first piston and the inner surface of the first cylinder 140 form a first working chamber, the second vane assembly, the outer peripheral surface of the second piston and the inner surface of the second cylinder 150 form a second working chamber, the movement of the first piston can change the volume of the first working chamber to compress the gas, and the movement of the second piston can change the volume of the second working chamber to compress the gas.

[0096] On the basis of the above embodiment, further, the first slide assembly includes a first slide and a first elastic member, the first slide presses the outer peripheral surface of the first piston, and the first elastic member is connected to the end of the first slide away from the first piston, so that during the movement of the first piston, the first elastic member can push the first slide to always keep pressing the outer peripheral surface of the first piston, ensuring the sealing of the first working chamber. Alternatively, the first slide assembly includes a first slide, and the first slide can be an integrated structure with the first piston, which can prevent the first slide from falling from the first slide groove, ensure the installation stability of the first slide, and improve the reliability of the product, and the mechanical properties of the integrated structure are good, so that the connection strength between the first slide and the first piston can be improved. In addition, the first slide is made integrally with the first piston, which is conducive to mass production, improves the processing efficiency of the product, and reduces the processing cost of the product. Of course, the first slide can also be hingedly connected to the first piston, which can also prevent the first slide from falling out of the first slide groove, so that the installation of the first slide is stable and the reliability of the product is improved.

[0097] The second slide assembly includes a second slide and a second elastic member, the second slide presses the outer peripheral surface of the second piston, and the second elastic member is connected to the end of the second slide away from the second piston, so that during the movement of the second piston, the second elastic member can push the second slide to always keep pressing the outer peripheral surface of the second piston, ensuring the sealing of the second working chamber. Alternatively, the second slide assembly includes a second slide, and the second slide can be an integrated structure with the second piston, which can prevent the second slide from falling from the second slide groove, ensure the installation stability of the second slide, improve the reliability of the product, and the mechanical properties of the integrated structure are good, so that the connection strength between the second slide and the second piston can be improved. In addition, the second slide is made integrally with the second piston, which is conducive to batch production, improves the processing efficiency of the product, and reduces the processing cost of the product. Of course, the second slide can also be hingedly connected to the second piston, which can also prevent the second slide from falling out of the second slide groove, so that the installation of the second slide is stable and the reliability of the product is improved.

[0098] Based on any of the above embodiments, Figure 1 As shown, further, the compressor 100 also includes: a crankshaft 200 and a motor assembly, the motor assembly includes a stator and a rotor, the crankshaft 200 has a first eccentric portion and a second eccentric portion, the first piston is connected to the first eccentric portion, and the second piston is connected to the second eccentric portion; the motor assembly is connected to the crankshaft 200 to drive the crankshaft 200 to rotate.

[0099] The compressor 100 also includes a crankshaft 200 and a motor assembly. The motor assembly can drive the crankshaft 200 to rotate. The crankshaft 200 has a first eccentric portion connected to the first piston and a second eccentric portion connected to the second piston. When the crankshaft 200 rotates, the first eccentric portion on the crankshaft 200 drives the first piston to rotate, and the rotating first piston realizes the functions of sucking, compressing and discharging the gas.

[0100] The second eccentric portion on the crankshaft 200 drives the second piston to rotate, and the rotating second piston realizes the functions of sucking, compressing and discharging gas.

[0101] As the crankshaft 200 drives the first piston and the second piston to rotate, a stream of low-pressure gas enters the first working chamber of the first cylinder 140 from the first air intake passage, completes the process of air intake, compression, and exhaust in the first working chamber, and exhausts through the first air outlet passage 210. Another stream of low-pressure gas enters the second working chamber of the second cylinder 150 through the second air intake passage, completes the process of air intake, compression, and exhaust in the second working chamber, and exhausts through the second air outlet passage 210. The exhaust process is completed twice for every rotation of the crankshaft 200.

[0102] like Figure 1 As shown, further, the compressor 100 also includes: a second air outlet port 114, which is arranged on the shell 110; a third exhaust port, which is connected to the second working chamber, and the third exhaust port is connected to the second air outlet port 114 through the inner cavity of the shell 110; an air outlet channel 210, and the third exhaust port is connected to the inner cavity of the shell 110 through the air outlet channel 210; the air outlet channel 210 and the exhaust channel 190 are not connected to each other.

[0103] In this embodiment, the compressor 100 further includes a second gas outlet port 114. Specifically, the second gas outlet port 114 is disposed at the top of the housing 110, and the third exhaust port is connected to the second working chamber, wherein the second working chamber is connected to the inner chamber of the housing 110 from the third exhaust port through the gas outlet channel 210, and is discharged from the housing 110 from the second gas outlet port 114. In other words, after the gas in the second working chamber is discharged through the third exhaust outlet, it diffuses into the inner chamber of the housing 110, and then is discharged through the second gas outlet port 114. Since the exhaust pressure of the second cylinder 150 is lower than the exhaust pressure of the first cylinder 140, the gas pressure in the inner chamber of the housing 110 is relatively low, which facilitates the oil return of the compressor 100 and helps to ensure the reliability of the operation of the compressor 100.

[0104] Furthermore, the compressor 100 also includes a first seal and a second seal. Specifically, the first seal partially covers the first bearing 120, and the second seal partially covers the second bearing 130. By setting the first seal and the second seal, the first seal and the second seal can respectively partially cover the first bearing 120 and the second bearing 130, which can effectively reduce the noise generated during the operation of the compressor 100 and improve the user experience.

[0105] In addition, an exhaust cavity is formed between the second seal and the second bearing 130, and the exhaust cavity is communicated with the gas outlet channel 210 and the third exhaust port, that is, the exhaust cavity is communicated with the second working cavity. By communicating the second working cavity with the gas outlet channel 210, and making the gas outlet channel 210 pass through the second bearing 130, the second cylinder 150, the second partition plate 170, the first cylinder 140 and the first bearing 120, and then communicating with the inner cavity of the housing 110, the gas in the second working cavity can reach the side of the first cylinder 140 through the outlet channel, and then diffuse into the inner cavity of the housing 110 and communicate with the second gas outlet port 114, thereby completing the exhaust process of the second working cavity.

[0106] It should be noted that the first sealing member and the second sealing member are covers or silencers, and the first sealing member and the second sealing member are connected to other positions by bolts or welding.

[0107] In a specific embodiment, the compressor 100 further includes a first exhaust valve 220 and a second exhaust valve. Specifically, the first exhaust valve is arranged on the first exhaust port 180, and the second exhaust valve is arranged on the gas outlet channel 210. The first exhaust valve 220 can open and close the first exhaust port 180, and the second exhaust valve can open and close the gas outlet channel 210.

[0108] Embodiment eight:

[0109] Based on any of the above embodiments, Fig. 9 As shown, further, the compressor 100 further includes: an air intake port is provided on the housing 110, the compressor 100 further includes a first air intake passage 380 and a second air intake passage 390, the first working chamber is connected to the air intake port via the first air intake passage 380, and the second working chamber is connected to the air intake port via the second air intake passage 390. Further, the first air intake passage 380 and the second air intake passage 390 are connected to each other.

[0110] In this embodiment, an air intake port may be provided on the housing 110, so that the first working chamber and the second working chamber are both connected to the air intake port. Specifically, the first working chamber is connected to the air intake port via the first air intake channel 380, and the second working chamber is connected to the air intake port via the second air intake channel 390. The first air intake channel 380 and the second air intake channel 390 are preferably connected to each other, so as to reduce the total length of the air intake channel, avoid excessive processing of components such as cylinders and bearings to affect rigidity, and reduce production costs.

[0111] In another specific embodiment, Figure 8 As shown, further, the compressor 100 also includes: two intake ports are provided on the shell 110, and the compressor 100 also includes a first intake channel 380 and a second intake channel 390. The first working chamber is connected to one intake port through the first intake channel 380, and the second working chamber is connected to another intake port through the second intake channel 390. The first intake channel 380 and the second intake channel 390 are not connected to each other.

[0112] In this embodiment, two air intake ports are provided on the housing 110 and one working chamber is connected to one air intake port, so that the gases in the two air intake passages will not mix with each other, thereby facilitating ensuring the air intake volume of each cylinder.

[0113] It should be noted that the first air intake passage 380 is disposed on the first cylinder 140 or the first bearing 120 or the second partition plate 170 , and the second air intake passage 390 is disposed on the second cylinder 150 or the second bearing 130 or the second partition plate 170 .

[0114] In a specific embodiment of the present embodiment, the first air intake channel 380 is arranged on the first cylinder 140, and the gas enters the first working chamber through the first air intake channel 380, thereby realizing the process of sucking the gas into the first working chamber; the second air intake channel 390 is arranged on the second cylinder 150 and is connected with the second working chamber, and the gas enters the second working chamber through the second air intake channel 390, thereby realizing the process of sucking the gas into the second working chamber.

[0115] In another specific embodiment, the first air intake channel 380 is arranged on the first cylinder 140 and is connected to the first working chamber. The gas enters the first working chamber through the first air intake channel 380, thereby realizing the process of sucking the gas into the first working chamber; the second air intake channel 390 is arranged on the second bearing 130 and is connected to the second working chamber. The gas enters the second working chamber through the second air intake channel 390, thereby realizing the process of sucking the gas into the second working chamber.

[0116] In another specific embodiment, the first air intake channel 380 is arranged on the first bearing 120 and is connected to the first working chamber. The gas enters the first working chamber through the first air intake channel 380, thereby realizing the process of sucking the gas into the first working chamber; the second air intake channel 390 is arranged on the second cylinder 150, and the gas enters the second working chamber through the second air intake channel 390, thereby realizing the process of sucking the gas into the second working chamber.

[0117] In another specific embodiment, the first air intake channel 380 is arranged on the first bearing 120, and the gas enters the first working chamber through the first air intake channel 380, thereby realizing the process of sucking the gas into the first working chamber; the second air intake channel 390 is arranged on the second bearing 130, and the gas enters the second working chamber through the second air intake channel 390, thereby realizing the process of sucking the gas into the second working chamber.

[0118] Embodiment nine:

[0119] According to a second aspect of the present invention, there is provided a refrigeration device, comprising a compressor 100 as provided in any of the above embodiments, and thus having all the beneficial technical effects of the compressor 100, which will not be described one by one here.

[0120] In a specific embodiment, Figure 8 As shown, further, the refrigeration equipment also includes: a first condenser 300, connected to the first air outlet port 112 of the compressor 100; a first throttling element 310, connected to the first condenser 300; a first evaporator 320, connected to the first throttling element 310; a first liquid reservoir 330, connecting the first evaporator 320 and the first air intake channel 380 of the compressor 100; a second condenser 340, connected to the second air outlet port 114 of the compressor 100; a second throttling element 350, connected to the second condenser 340; a second evaporator 360, connected to the second throttling element 350; a second liquid reservoir 370, connecting the second evaporator 360 and the second air intake channel 390 of the compressor 100.

[0121] In this embodiment, the compressor 100 and the first condenser 300, the first throttling element 310, the first evaporator 320, and the first liquid reservoir 330 form a first refrigeration system, and the compressor 100 and the second condenser 340, the second throttling element 350, the second evaporator 360, and the second liquid reservoir 370 form a second refrigeration system. The two groups of independent refrigeration systems, that is, the refrigeration equipment realizes the multi-exhaust function realized by multiple compressors 100 in the related art through one compressor 100, which reduces the processing cost of the refrigeration equipment, reduces the occupied space of the refrigeration equipment, and improves the convenience of installing the internal components of the refrigeration equipment. Since the exhaust pressures of the first cylinder 140 and the second cylinder 150 are different, the exhaust pressures reaching the first condenser 300 and the second condenser 340 are different, so that the refrigeration equipment can have double condensing temperatures and double evaporating temperatures, which is conducive to realizing the cascade utilization of energy and improving the energy efficiency of the refrigeration equipment. In particular, when the displacements of the first cylinder 140 and the second cylinder 150 are different, the amounts of refrigerant condensed by the first condenser 300 and the second condenser 340 are also different, thereby further improving the energy efficiency of the refrigeration equipment.

[0122] The flow process of refrigerant is as follows:

[0123] The first air outlet port 112 of the compressor 100 is connected to the first condenser 300 through components such as pipelines, and the refrigerant flows into the first evaporator 320 through the first expansion valve, and flows from the first evaporator 320 to the first air intake channel 380 of the first cylinder 140 via the air intake channel of the first liquid reservoir 330; the first air outlet port 112 is connected to the second condenser 340 through a pipeline component, and the refrigerant flows into the second evaporator 360 through the second expansion valve, and flows from the second evaporator 360 to the second air intake channel 390 of the second cylinder 150 via the air intake channel of the second liquid reservoir 370.

[0124] In another specific embodiment, Fig. 9 As shown, further, the refrigeration equipment also includes: a third condenser 400, which is connected to the first air outlet port 112 of the compressor 100; a third throttling element 410, which is connected to the third condenser 400; a third evaporator 420, which is connected to the third throttling element 410; a third liquid reservoir 430, which is connected to the third evaporator 420 and the first air intake channel 380 and the second air intake channel 390 of the compressor 100; a fourth condenser 440, which is connected to the second air outlet port 114 of the compressor 100; a fourth throttling element 450, which is connected to the fourth condenser 440; a fourth evaporator 460, which is connected to the fourth throttling element 450; the third liquid reservoir 430 also connects the fourth evaporator 460 and the first air intake channel 380 and the second air intake channel 390 of the compressor 100.

[0125] In this embodiment, the compressor 100 and the third condenser 400, the third throttling element 410, the third evaporator 420, and the third liquid reservoir 430 form a third refrigeration system, and the compressor 100 and the fourth condenser 440, the fourth throttling element 450, the fourth evaporator 460, and the third liquid reservoir 430 form a fourth refrigeration system. The two independent refrigeration systems, that is, the refrigeration equipment realizes the multi-exhaust function realized by multiple compressors 100 in the related technology through one compressor 100, reduces the processing cost of the refrigeration equipment, reduces the occupied space of the refrigeration equipment, and improves the convenience of installing the internal components of the refrigeration equipment. The first suction channel 380 and the second suction channel 390 are connected to the third liquid reservoir 430, so that setting a liquid reservoir can meet the suction function of the first cylinder 140 and the second cylinder 150, reduces the number of components in the refrigeration equipment, further reduces the processing cost of the refrigeration equipment, effectively reduces the volume of the refrigeration equipment, and improves the convenience of installing the refrigeration equipment. Moreover, since the exhaust pressures of the first cylinder 140 and the second cylinder 150 are different, the exhaust pressures reaching the third condenser 400 and the fourth condenser 440 are different, so that the refrigeration equipment can have double condensation temperatures and double evaporation temperatures, which is conducive to realizing the cascade utilization of energy and improving the energy efficiency of the refrigeration equipment. In particular, when the displacement of the first cylinder 140 and the second cylinder 150 is different, the amount of refrigerant condensed by the third condenser 400 and the fourth condenser 440 is also different, further improving the energy efficiency of the refrigeration equipment.

[0126] The above two specific embodiments realize the function of dual exhaust parameters of a single compressor 100, and utilize the heat of high and low temperatures of the dual rows to effectively save energy consumption. At the same time, the range of the dual cylinder parameter ratio is reasonably stipulated, which can give full play to the advantages of the dual row cycle and improve energy efficiency.

[0127] In the description of this specification, the terms "connection", "installation", "fixation" and the like should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0128] In the description of this specification, the description of the terms "one embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0129] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A compressor, characterized in that: include: A housing, wherein a first air outlet port and a second air outlet port are provided on the housing; A first bearing is disposed in the housing; A first cylinder is disposed in the housing, wherein the first cylinder includes a first working chamber; A second cylinder is disposed in the housing, the second cylinder comprises a second working chamber, and the second working chamber is connected to the second gas outlet port through the inner chamber of the housing; a first partition plate, located between the first bearing and the first cylinder; a first exhaust port, disposed on the first baffle, the first exhaust port being in communication with the first working chamber; an exhaust channel, located in the shell, the first exhaust port is connected to the first exhaust port through the exhaust channel, and the exhaust channel is not connected to the inner cavity of the shell; Wherein, the exhaust pressure of the first working chamber is greater than the exhaust pressure of the second working chamber; The exhaust passage comprises: a first exhaust passage, disposed on the first bearing, the first exhaust passage being in communication with the first outlet port; a second exhaust channel, disposed on the first baffle, wherein one end of the second exhaust channel is communicated with the first exhaust channel, and the other end of the second exhaust channel is communicated with the first exhaust port; The second exhaust channel is arranged on a side of the first partition plate close to the first bearing, and one end of the first exhaust channel connected to the second exhaust channel is opened on a side of the first bearing close to the first partition plate, and the first exhaust channel extends in a radial direction inside the first bearing to the end of the first bearing, and passes through the end of the first bearing to be connected with the first outlet port.

2. The compressor according to claim 1, characterized in that An axial hole is formed on the first bearing, and the first exhaust passage includes a first side wall close to a side of the axial hole. The minimum distance between the first side wall and the side wall of the axial hole is L1, wherein L1≥0.5 mm.

3. The compressor according to claim 1, characterized in that An axial hole is formed on the first partition plate, and the second exhaust channel includes a second side wall close to the axial hole. The minimum distance between the second side wall and the side wall of the axial hole is L2, wherein L2≥0.5 mm.

4. The compressor according to claim 1, characterized in that The thickness of the first partition is H1, the depth of the second exhaust passage in the axial direction of the shell is D1, and the height of the first exhaust port in the axial direction of the shell is h1. The thickness H1 of the first partition plate, the depth D1 of the second exhaust channel and the height h1 of the first exhaust port satisfy the following: H1-D1>5×min(D1-h1).

5. The compressor according to claim 1, characterized in that The thickness of the first bearing is H2, the depth of the first exhaust passage along the axial direction of the housing is D2, The thickness H2 of the first bearing, the depth D2 of the first exhaust channel and the height h1 of the first exhaust port satisfy: H2-D2>5×min(D2-h1).

6. The compressor according to any one of claims 1 to 5, characterized in that The maximum cross-sectional area of ​​the first exhaust port is S1, and the minimum cross-sectional area of ​​the exhaust passage is S2, wherein S1 and S2 satisfy:

7. The compressor according to any one of claims 1 to 5, characterized in that A line between a center point of the first exhaust port and a center point of the first partition, the line extending in the axial direction of the shell to form a first plane; The exhaust passage comprises a second exhaust port on one side close to the first exhaust port, the second exhaust port is communicated with the first exhaust port and the first exhaust port respectively, a center line of the second exhaust port can pass through the center of the first bearing, and the center line extends in the axial direction of the housing to form a second plane; The first surface and the second surface form an angle θ, wherein the angle θ satisfies, 140° ≤θ≤330°.

8. The compressor according to any one of claims 1 to 5, characterized in that The compressor also includes: The shell is provided with an air intake port, the compressor further comprises a first air intake channel and a second air intake channel, the first working chamber is connected to the air intake port via the first air intake channel, the second working chamber is connected to the air intake port via the second air intake channel, and the first air intake channel and the second air intake channel are connected to each other; or The shell is provided with two intake ports, and the compressor further includes a first intake channel and a second intake channel. The first working chamber is connected to one of the intake ports via the first intake channel, and the second working chamber is connected to the other intake port via the second intake channel. The first intake channel and the second intake channel are not connected to each other.

9. A refrigeration device, characterized in that: include: A compressor as claimed in any one of claims 1 to 8.

10. The refrigeration device according to claim 9, characterized in that: The refrigeration equipment also includes: a first condenser, connected to a first gas outlet port of the compressor; a first throttling element, in communication with the first condenser; a first evaporator, connected to the first throttling element; a first liquid accumulator communicating with the first evaporator and a first air intake passage of the compressor; a second condenser, connected to a second gas outlet port of the compressor; a second throttling element, in communication with the second condenser; a second evaporator, in communication with the second throttling element; The second liquid accumulator is connected to the second evaporator and the second air intake passage of the compressor.

11. The refrigeration device according to claim 9, characterized in that: The refrigeration equipment also includes: a third condenser, connected to the first gas outlet port of the compressor; a third throttling element, connected to the third condenser; a third evaporator, connected to the third throttling element; a third liquid accumulator, communicating the third evaporator with the first air intake passage and the second air intake passage of the compressor; a fourth condenser, connected to the second gas outlet port of the compressor; a fourth throttling element, connected to the fourth condenser; a fourth evaporator, connected to the fourth throttling element; The third accumulator is also connected to the fourth evaporator and the first and second suction passages of the compressor.

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