Compressor device and heat exchange system
By designing the flow adjustment component in the compressor device, using the flow angle and flow channel difference, the problem of insufficient return oil in the twin cylinder design is solved, ensuring uniform distribution of lubricating oil, and improving the reliability and efficiency of the system.
Patent Information
- Application Number
- CN202510570620.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-04-30
- Publication Date
- 2025-07-11
AI Technical Summary
In the existing compressor device with a dual-cylinder design, one compression mechanism returns less oil, resulting in insufficient lubricating oil supply, increasing friction and wear of mechanical components, and affecting the reliability and stability of the system.
The flow adjustment component design is adopted to allow the difference in flow direction angles of the pipeline and the difference in the size of the flow channel to make the lubricating oil more easily flow into the first liquid storage chamber, ensuring that the compression cylinder on the non-direct side is fully supplied with lubricating oil, and avoiding wear and efficiency reduction on the direct side.
It solves the problem of less oil return in the compressor device, improves the supply of lubricating oil, avoids wear and efficiency of the compression mechanism, reduces maintenance costs, and enhances the reliability and stability of the system.
Smart Images
Figure CN120292073A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to the technical field of electrical equipment, and particularly to a compressor device and a heat exchange system. Background Art
[0002] In the existing design of a compressor device with a double-suction and double-row function (double-cylinder design), two independent compression mechanisms are used to discharge refrigerants of two different pressures to achieve an efficient refrigeration or heating effect. However, in the actual application process, it is found that in this compressor device with a double-cylinder design, there is a problem that one of the compression mechanisms has less oil return. Summary of the Invention
[0003] The main object of the present invention is to propose a compressor device and a heat exchange system, aiming to solve the problem that one of the compression mechanisms in a compressor device with a double-cylinder design has less oil return.
[0004] To achieve the above object, a compressor device proposed by the present invention includes:
[0005] A compressor, including a housing and a compression mechanism disposed in the housing. The housing has a first exhaust port and a second exhaust port, and the compression mechanism has a first compression cylinder and a second compression cylinder arranged vertically.
[0006] A liquid storage mechanism, having a first liquid storage chamber and a second liquid storage chamber. The outlet of the first liquid storage chamber is communicated with the inlet of the first compression cylinder, the outlet of the first compression cylinder is communicated with the first exhaust port through the inner cavity of the housing, the outlet of the second liquid storage chamber is communicated with the inlet of the second compression cylinder, and the outlet of the second compression cylinder is directly communicated with the second exhaust port.
[0007] A flow rate regulating assembly, having an inlet, a first outlet and a second outlet that are interconnected with the inlet. The first outlet is communicated with the inlet of the first liquid storage chamber, the second outlet is communicated with the inlet of the second liquid storage chamber, and the flow rate regulating assembly is used to distribute the lubricating oil flowing back from the inlet to the first liquid storage chamber and the second liquid storage chamber, and make the lubricating oil flowing back to the first liquid storage chamber greater than the lubricating oil flowing back to the second liquid storage chamber.
[0008] In an embodiment, the flow rate regulating assembly has a first flow channel, a second flow channel and a third flow channel. The first flow channel has the inlet, and the gas outlet of the first flow channel, the gas inlet of the second flow channel and the gas inlet of the third flow channel are interconnected in a tee shape. The second flow channel has the first outlet, and the third flow channel has the second outlet.
[0009] The first flow channel is connected to the second flow channel at a first included angle, the first flow channel is connected to the third flow channel at a second included angle, and the first included angle is greater than the second included angle, so that the flow rate of the first flow channel flowing into the second flow channel is greater than the flow rate of the first flow channel flowing into the third flow channel.
[0010] In one embodiment, the third flow channel is connected to the second flow channel at a third included angle, and the third included angle is an acute angle.
[0011] In one embodiment, the third flow channel is connected to the second flow channel at a third included angle, and the third included angle is a right angle or an obtuse angle.
[0012] In one embodiment, the first flow channel and the second flow channel are arranged to extend along a first direction.
[0013] In one embodiment, the first direction is the vertical direction.
[0014] In one embodiment, the third flow channel includes a first section and a second section that are interconnected. The first section is interconnected with the air outlet of the first flow channel and the air inlet of the second flow channel in a tee shape, and the second section is connected to the inlet of the second liquid storage chamber.
[0015] In one embodiment, the first section is arranged to extend along the horizontal direction, the second section is arranged to extend along the vertical direction, and the second section is connected to the first section in a bent shape.
[0016] In one embodiment, the first flow channel includes a third section and a fourth section that are interconnected. The third section has the inlet, and the fourth section has the air outlet;
[0017] The third section is connected to the fourth section in a bent shape, and the fourth section and the second flow channel are arranged to extend along the first direction.
[0018] In one embodiment, the third section is arranged to extend along the horizontal direction.
[0019] In one embodiment, the first direction is the vertical direction.
[0020] In one embodiment, the second flow channel includes a fifth section and a sixth section that are interconnected. The fifth section, the air outlet of the first flow channel and the air inlet of the second flow channel are interconnected in a tee shape, and the sixth section is communicated with the inlet of the first liquid storage chamber;
[0021] The fifth section is connected to the sixth section in a bent shape, and the fifth section and the first flow channel are arranged to extend along a second direction.
[0022] In one embodiment, the second direction is the horizontal direction.
[0023] In one embodiment, the sixth section extends in the vertical direction.
[0024] The present invention also provides a heat exchange system, which includes the above-mentioned compressor device, and the specific structure of the compressor device refers to the above embodiments. Since the compressor device adopts all the technical solutions of the above-mentioned embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, and will not be elaborated here one by one.
[0025] The refrigerant of the inlet return air of the flow regulating component in the present invention will carry lubricating oil and enter the first liquid storage chamber and the second liquid storage chamber through the first outlet 3 and the second outlet respectively, and then return the oil to the first compression cylinder and the second compression cylinder through the first liquid storage chamber and the second liquid storage chamber respectively. Since the density and inertia of the lubricating oil are usually greater than those of the refrigerant, this means that the lubricating oil is more difficult to be driven by the flowing gas. The flow regulating component can make the flow rate of the lubricating oil flowing into the inlet of the first liquid storage chamber greater than the flow rate of the lubricating oil flowing into the inlet of the second liquid storage chamber through the difference in the flow direction angle and the flow channel size of the pipeline, so that the first compression cylinder on the non-direct discharge side can receive more lubricating oil through the first liquid storage chamber, ensuring the supply of lubricating oil. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved, and furthermore, the problems of wear and efficiency reduction of the compression mechanism on the direct discharge side are avoided. There is no need to add an oil returner and the pipeline for controlling oil return, and the control of oil return can be realized by a simple structure instead of complex and high-cost devices, which has great market advantages. BRIEF DESCRIPTION OF THE DRAWINGS
[0026] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on the structures shown in these drawings without creative efforts.
[0027] Figure 1 Schematic structural diagram of an embodiment of the compressor device provided by the present invention;
[0028] Figure 2 Schematic structural diagram of another embodiment of the compressor device provided by the present invention;
[0029] Figure 3 Partial schematic structural diagram of still another embodiment of the compressor device provided by the present invention;
[0030] Figure 4 Partial schematic structural diagram of another embodiment of the compressor device provided by the present invention.
[0031] Description of the attached drawing reference numerals:
[0032] 10. Compressor; 11. Housing; 12. Compression mechanism; 11a. First exhaust port; 11b. Second exhaust port; 13. First compression cylinder; 13a. Inlet of the first compression cylinder; 13b. Outlet of the first compression cylinder; 14. Second compression cylinder; 14a. Inlet of the second compression cylinder; 14b. Outlet of the second compression cylinder; 20. Liquid storage mechanism; 21. First liquid storage chamber; 21a. Inlet of the first liquid storage chamber; 21b. Outlet of the first liquid storage chamber; 22. Second liquid storage chamber; 22a. Inlet of the second liquid storage chamber; 22b. Outlet of the second liquid storage chamber; 30. Flow rate regulating assembly; 30a. Inlet; 30b. First outlet; 30c. Second outlet; 31. First flow channel; 31b. Gas outlet of the first flow channel; 311. Third section; 312. Fourth section; 32. Second flow channel; 32a. Gas inlet of the second flow channel; 32b. Gas outlet of the second flow channel; 321. Fifth section; 322. Sixth section; 33. Third flow channel; 33a. Gas inlet of the third flow channel; 33b. Gas outlet of the third flow channel; 331. First section; 332. Second section.
[0033] The realization, functional features and advantages of the purpose of the present invention will be further described in conjunction with the embodiments with reference to the accompanying drawings. Specific embodiments
[0034] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without making creative efforts fall within the protection scope of the present invention.
[0035] It should be noted that if there are directional indications (such as up, down, left, right, front, back...) involved in the embodiments of the present invention, the directional indications are only used to explain the relative position relationship and movement conditions between the components in a specific posture. If the specific posture changes, the directional indications will also change accordingly.
[0036] In addition, if the embodiments of the present invention involve descriptions such as "first" and "second", the descriptions of "first", "second", etc. are only for descriptive purposes and should not be construed as indicating or implying their relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In addition, if "and / or" or "and / or" appears throughout the text, its meaning includes three parallel scenarios. Taking "A and / or B" as an example, it includes scenario A, or scenario B, or the scenario where both A and B are satisfied simultaneously. In addition, the technical solutions between various embodiments can be combined with each other, but it must be based on the ability of those of ordinary skill in the art to implement. When the combination of technical solutions results in contradictions or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.
[0037] In the design of existing compressor devices with double-suction and double-row functions, two independent compression mechanisms are used to discharge refrigerants of two different pressures to achieve efficient refrigeration or heating effects. However, during the actual application process, it is found that in this compressor device with a double-cylinder design, there is a problem that less oil returns to one of the compression mechanisms.
[0038] After long-term observation, research, and analysis, it is found that this phenomenon is mainly caused by the imperfect lubrication system. For the non-direct discharge side, the lubricating oil follows the refrigerant and is discharged from the muffler into the compressor housing, realizing the circulation of the lubricating oil; for the direct discharge side, the lubricating oil follows the refrigerant and is discharged from the direct discharge pipe outside the compressor, which directly leads to a reduction in the lubricating oil inside the compressor.
[0039] Since the oil discharge volume on the direct discharge side is large, but the oil return mechanism fails to effectively recover and redistribute the lubricating oil to the key parts that need lubrication, resulting in the problem of insufficient lubricating oil supply. This not only fails to provide sufficient lubrication protection for relevant components, exacerbating the friction and wear between mechanical components, but also increases the maintenance cost and downtime, affecting the reliability and stability of the overall system.
[0040] The present invention proposes a compression device that can be applied to various heat exchange systems, especially multi-connected units, such as multi-connected unit air conditioners, multi-connected unit hot water heat exchange systems, washing and drying integrated machines, and multi-connected unit composite heat exchange systems formed by at least two combinations of washing and drying heat exchangers and air conditioners and hot water heat exchangers. In the compression device of the present invention, by redistributing the lubricating oil, the problem that less oil returns to one of the compression mechanisms in the compressor device with a double-cylinder design is solved.
[0041] Please refer to Figure 1 、 Figure 2 、 Figure 3 or Figure 4 , in an embodiment of the present invention, the compressor device includes:
[0042] A compressor 10, comprising a housing 11 and a compression mechanism 12 disposed within the housing 11. The housing 11 has a first exhaust port 11a and a second exhaust port 11b. The compression mechanism 12 has a first compression cylinder 13 and a second compression cylinder 14 arranged vertically.
[0043] A liquid storage mechanism 20, having a first liquid storage chamber 21 and a second liquid storage chamber 22. The outlet 21b of the first liquid storage chamber is communicated with the inlet 13a of the first compression cylinder. The outlet 13b of the first compression cylinder is communicated with the first exhaust port 11a through the inner cavity of the housing 11. The outlet 22b of the second liquid storage chamber is communicated with the inlet 14a of the second compression cylinder. The outlet 14b of the second compression cylinder is directly communicated with the second exhaust port 11b.
[0044] A flow rate regulating assembly 30, having an inlet 30a, a first outlet 30b and a second outlet 30c that are communicated with each other. The first outlet 30b is communicated with the inlet 21a of the first liquid storage chamber. The second outlet 30c is communicated with the inlet 22a of the second liquid storage chamber. The flow rate regulating assembly 30 is used to distribute the lubricating oil flowing back from the inlet to the first liquid storage chamber 21 and the second liquid storage chamber 22, and make the lubricating oil flowing back to the first liquid storage chamber 21 greater than the lubricating oil flowing back to the second liquid storage chamber 22.
[0045] It can be understood that the first compression cylinder 13 and the second compression cylinder 14 are arranged vertically, and gravity is used for oil return. Since the lubricating oil in the first compression cylinder 13 located above will flow back to the second compression cylinder 14, therefore, the oil return of the first compression cylinder 13 needs to be greater than that of the second compression cylinder 14. Then, when designing the oil return, it can be designed that more lubricating oil returns to the first compression cylinder 13 above to solve the problem of oil shortage.
[0046] In this embodiment, the first exhaust port 11a can be correspondingly arranged at the upper part of the compressor, especially at the top. The outlet 13b of the first compression cylinder 13 is communicated with the inner cavity of the housing 11, and then is connected to the first exhaust port 11a through the inner cavity of the housing 11. The second exhaust port 11b is arranged on the side wall of the compressor and close to the second compression cylinder 14. The second compression cylinder 14 is directly communicated with the second exhaust port 11b, which can improve the gas transmission pressure and energy efficiency.
[0047] When the compressor works, when the refrigerant discharged from the first compression cylinder 13 is discharged from the first exhaust port 11a through the inner cavity of the housing 11, the inner cavity of the housing 11 and its internal structure (such as a muffler, a stator-rotor assembly, etc.) can form the function of an oil return device, and a part of the lubricating oil can be recovered, avoiding too much lubricating oil being discharged to the external circulation pipeline through the first exhaust port 11a. Here, the first compression cylinder 13 corresponds to the non-direct discharge side described above.
[0048] The refrigerant discharged from the second compression cylinder 14 is directly discharged into the heat exchange system through the second exhaust port 11b. This is equivalent to the refrigerant being discharged without oil return, and the lubricating oil carried by the refrigerant will directly discharge from the second exhaust port 11b in excessive amounts, resulting in an increase in the lubricating oil entering the pipeline. Here, the second compression cylinder 14 corresponds to the direct discharge side described above.
[0049] In this embodiment, the first liquid storage chamber 21 and the second liquid storage chamber 22 can adopt a split structure, that is, two tanks are used, or an integral liquid storage device can be adopted, that is, the inner cavity of the integral liquid storage device is partitioned to form independent first and second liquid storage chambers 21 and 22 to serve as the first and second liquid storage chambers 21 and 22, which is not limited herein.
[0050] In this embodiment, when the compressor device is applied to the heat exchange system, the inlet of the flow regulating component 30 is used to connect to the heat exchange system for the compressor to return gas. Since the fluidity of the refrigerant gas is good, even in a system containing lubricating oil, the refrigerant gas can still smoothly pass through the flow dividing device and be evenly distributed without being affected by the presence of lubricating oil. And since the density and inertia of the lubricating oil are usually greater than those of the refrigerant, this means that it is more difficult for the lubricating oil to be driven by the flowing gas. Under the action of the flow regulating component 30, the lubricating oil can be distributed in a predetermined direction (usually the direction of returning to the compressor). Specifically, the refrigerant returning gas through the inlet of the flow regulating component 30 will carry the lubricating oil and enter the first liquid storage chamber 21 and the second liquid storage chamber 22 through the first outlet 30b and the second outlet 30c respectively, and then return the oil to the first compression cylinder 13 and the second compression cylinder 14 through the first liquid storage chamber 21 and the second liquid storage chamber 22 respectively.
[0051] In this embodiment, the flow regulating component 30 can achieve the distribution of oil return by differences in the flow direction angle of the pipeline, differences in the flow channel size, or internal valve control of the flow rate, so that the lubricating oil flowing back to the first liquid storage chamber 21 is greater than the lubricating oil flowing back to the second liquid storage chamber 22.
[0052] It can be understood that through the flow regulating component 30 of the present invention, the flow rate of the lubricating oil flowing into the inlet 21a of the first liquid storage chamber can be made greater than the flow rate of the lubricating oil flowing into the inlet 22a of the second liquid storage chamber, so that the first compression cylinder 13 on the non-direct discharge side can receive more lubricating oil through the first liquid storage chamber 21, ensuring the supply of lubricating oil. In this way, the problem that one of the compression mechanisms in a compressor device with a double-cylinder design has less oil return is solved, and furthermore, the problems of wear and efficiency reduction of the compression mechanism on the direct discharge side are further avoided. There is no need to add an oil returner and the pipeline for controlling oil return. The control of oil return can be achieved by a simple structure instead of complex and high-cost devices, which has great market advantages.
[0053] In the above embodiments, it should be noted that in order to further reduce the discharge of lubricating oil on the non-direct-discharge side, a professional oil returner can be added. The oil returner can be arranged on the top of the compressor or accommodated in the inner cavity of the compressor housing. With this design, the first compression cylinder 13 can be directly connected to the oil returner through a pipeline and then to the first exhaust port 11a.
[0054] Please refer to Figure 1 、 Figure 2 、 Figure 3 or Figure 4 In an embodiment of the present invention, the flow rate regulating assembly 30 has a first flow channel 31, a second flow channel 32, and a third flow channel 33. The first flow channel 31 has the inlet. The outlet 31b of the first flow channel, the inlet 32a of the second flow channel, and the inlet 33a of the third flow channel are interconnected in a tee shape. The second flow channel 32 has the first outlet, and the third flow channel 33 has the second outlet;
[0055] The first flow channel 31 is connected to the second flow channel 32 at a first angle, and the first flow channel 31 is connected to the third flow channel 33 at a second angle. The first angle is greater than the second angle, so that the flow rate of the first flow channel 31 flowing into the second flow channel 32 is greater than the flow rate of the first flow channel 31 flowing into the third flow channel 33.
[0056] The first flow channel 31 serves as the main input channel. Through the tee interconnection method, its outlet 31b can be simultaneously connected to the inlet 32a of the second flow channel 32 and the inlet 33a of the third flow channel 33, which means that the medium flowing out of the first flow channel 31 will be distributed to the second flow channel 32 and the third flow channel 33. The two flow channels, the second flow channel 32 and the third flow channel 33, are respectively responsible for delivering the medium to the first liquid storage chamber 21 and the second liquid storage chamber 22. Among them, the outlet 32b of the second flow channel is directly communicated with the inlet 21a of the first liquid storage chamber, and the outlet 33b of the third flow channel is communicated with the inlet 22a of the second liquid storage chamber. The outlet 31b of the first flow channel 31 is connected to the second flow channel 32 and the third flow channel 33 at different angles. The first angle between the first flow channel 31 and the second flow channel 32 is greater than the second angle between the first flow channel 31 and the third flow channel 33, so as to ensure that more lubricating oil flows to the second flow channel 32, that is, the first liquid storage chamber 21.
[0057] The lubricating oil first enters the flow rate regulating assembly 30 through the inlet of the first flow channel 31. At the air outlet 31b of the first flow channel 31, the lubricating oil is divided into two paths. One path enters the second flow channel 32, and the other path enters the third flow channel 33. Due to the design that the first included angle is greater than the second included angle, more lubricating oil will naturally tend to flow into the second flow channel 32. Based on the principle of fluid mechanics, a larger included angle results in less fluid resistance. Therefore, more lubricating oil will flow into the second flow channel 32 and then enter the first liquid storage cavity 21. Relatively, less lubricating oil flows through the third flow channel 33 to the second liquid storage cavity 22. Through the above process, the lubricating oil is respectively introduced into the first liquid storage cavity 21 and the second liquid storage cavity 22. Due to the angle design, more lubricating oil can be retained in the housing 11 through the direct discharge side, reducing the lubricating oil discharged from the direct discharge side. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved. Moreover, the wear and efficiency reduction problems of the compression mechanism on the direct discharge side are further avoided.
[0058] It should be noted that in the design of the heat exchange system, for the convenience of system pressure design, the pipe diameters of the first flow channel 31, the second flow channel 32, and the third flow channel 33 are the same or basically the same.
[0059] In this embodiment, by designing the branch angles of the second flow channel 32 and the third flow channel 33, the flow path of the fluid in the pipeline can be changed. For example, if more lubricating oil is desired to flow into the second flow channel 32, the branch leading to the second flow channel 32 can be designed to have a more straight and less curved angle, which can reduce the flow resistance and make more lubricating oil naturally flow along this path. On the contrary, the branch leading to the third flow channel 33 can be designed to have a larger curved angle or increase the number of bends to increase the flow resistance, thereby reducing the amount of lubricating oil entering this path. According to the inertia effect in fluid mechanics, the fluid tends to flow along the outer side when turning. Therefore, this characteristic can be utilized in the design. By reasonably setting the angle and direction at the turning point, more lubricating oil can flow in the desired direction, and more flows into the second flow channel 32.
[0060] Please refer to Figure 1 , in an embodiment of the present invention, the third flow channel 33 is connected to the second flow channel 32 at a third included angle, and the third included angle is an acute angle.
[0061] The first included angle between the first flow channel 31 and the second flow channel 32 is greater than the second included angle between the first flow channel 31 and the third flow channel 33, and the third flow channel 33 is connected to the second flow channel 32 at an acute angle, ensuring that more lubricating oil flows into the second flow channel 32. By adjusting the included angles between the flow channels, especially the acute angle formed between the third flow channel 33 and the second flow channel 32, the flow direction and resistance of the lubricating oil can be effectively controlled. Since the first included angle is greater than the second included angle, it is equivalent to that the curvature of the flow path formed by the first flow channel 31 and the second flow channel 32 is smaller than the curvature of the flow path formed by the first flow channel 31 and the third flow channel 33. Thus, more lubricating oil will naturally flow into the second flow channel 32, and less lubricating oil will flow through the third flow channel 33 to the second liquid storage cavity 22, enabling more lubricating oil to enter the first liquid storage cavity 21 and then flow into the non-direct discharge side and remain in the housing 11, reducing the lubricating oil discharged from the direct discharge side. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved, and furthermore, the problems of wear and efficiency reduction of the compression mechanism on the direct discharge side are avoided.
[0062] Please refer to Figure 2 、 Figure 3 or Figure 4 , in an embodiment of the present invention, the third flow channel 33 is connected to the second flow channel 32 at a third included angle, and the third included angle is a right angle or an obtuse angle.
[0063] When the third flow channel 33 is connected to the second flow channel 32 at a right angle or an obtuse angle, it further makes the second included angle between the first flow channel 31 and the third flow channel 33 smaller than the first included angle between the first flow channel 31 and the second flow channel 32. Since the first included angle between the first flow channel 31 and the second flow channel 32 is greater than the second included angle between the first flow channel 31 and the third flow channel 33, it is equivalent to that the curvature of the flow path formed by the first flow channel 31 and the second flow channel 32 is smaller than the curvature of the flow path formed by the first flow channel 31 and the third flow channel 33. More lubricating oil naturally tends to flow into the second flow channel 32, and less lubricating oil flows through the third flow channel 33 to the second liquid storage cavity 22, enabling more lubricating oil to enter the first liquid storage cavity 21 and then flow into the non-direct discharge side and remain in the housing 11, reducing the lubricating oil discharged from the direct discharge side. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved, and furthermore, the problems of wear and efficiency reduction of the compression mechanism on the direct discharge side are avoided.
[0064] Please refer to Figure 1 or Figure 2 , in an embodiment of the present invention, the first flow channel 31 and the second flow channel 32 extend along a first direction.
[0065] In this embodiment, the first flow channel 31 and the second flow channel 32 extend along the first direction, which means that the first flow channel 31 and the second flow channel 32 are arranged in the same direction. In this straight flow channel, the resistance of the lubricating oil flow is the smallest and the inertia is the largest.
[0066] In addition, it can be understood that the first flow channel 31 and the second flow channel 32 extending along the first direction also means that the first included angle between the first flow channel 31 and the second flow channel 32 is 180 degrees. When the third included angle between the third flow channel 33 and the second flow channel 32 is a right angle or an obtuse angle, obviously the third included angle is less than 180 degrees, so as to ensure that more lubricating oil flows into the second flow channel 32, and then enters the first liquid storage cavity 21, so that more lubricating oil can be retained in the housing 11 through the non-direct discharge side, reducing the lubricating oil discharged from the direct discharge side. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved. Moreover, the problems of wear and efficiency reduction of the compression mechanism on the direct discharge side are further avoided.
[0067] In the above embodiment, further, the first direction is the vertical direction.
[0068] Since the first flow channel 31 and the second flow channel 32 are arranged in the vertical direction, the vertical design may be beneficial to utilize the gravity to assist the flow of the lubricating oil. Especially when the system is stationary or running at a low speed, it can help the lubricating oil flow more smoothly to the second flow channel 32, ensure that the first compression cylinder 13 as the non-direct discharge side can obtain more lubricating oil, reduce the amount of lubricating oil supplied to the second compression cylinder 14, and avoid excessive lubricating oil being directly discharged with the compressed gas.
[0069] Please refer to Figure 2 , in an embodiment of the present invention, the third flow channel 33 includes a first section 331 and a second section 332 that are interconnected. The first section 331 is in a tee connection with the air outlet 31b of the first flow channel and the air inlet 32a of the second flow channel, and the second section 332 is connected to the inlet 22a of the second liquid storage cavity.
[0070] It can be understood that another alternative embodiment is provided in this embodiment. In this embodiment, the curvature of the third flow channel 33 is greater than Figure 1 the curvature of the third flow channel 33 in the shown embodiment. With this flow channel design, the oil return amount of the first flow channel 31 is larger. In this way, the appropriate third flow channel 33 can be selected according to the system requirements to design the scheme. In addition, the corresponding shape can also be selected for installation according to different installation environments. Among them, the first section 331 includes but is not limited to a straight pipe structure, and can also be a bent or arc-shaped pipe. The second section 332 includes but is not limited to a straight pipe structure.
[0071] Please refer to Figure 2, in an embodiment of the present invention, the first section 331 extends horizontally, the second section 332 extends vertically, and the second section 332 is bent and connected to the first section 331.
[0072] When the first section 331 extends horizontally, that is, the third angle between the third flow channel 33 and the second flow channel 32 is a right angle. Obviously, the third angle is less than 180 degrees, so as to ensure that more lubricating oil flows into the second flow channel 32 and then enters the first liquid storage cavity 21, enabling more lubricating oil to be retained in the housing 11 through the non-direct discharge side and reducing the lubricating oil discharged from the direct discharge side. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved. Moreover, the wear and efficiency reduction problems of the compression mechanism on the direct discharge side are further avoided. Furthermore, the bent connection between the first section 331 and the second section 332 allows the designer to flexibly arrange the flow channels within a limited space to meet different mechanical structure requirements. This is particularly important for compact devices as it can maximize the use of available space without sacrificing performance.
[0073] Please refer to Figure 3 , in an embodiment of the present invention, the first flow channel 31 includes a third section 311 and a fourth section 312 that are connected to each other. The third section 311 has the inlet, and the fourth section 312 has the air outlet 31b;
[0074] The third section 311 and the fourth section 312 are bent and connected, and the fourth section 312 and the second flow channel 32 extend in a first direction.
[0075] In this embodiment, the fourth section 312 and the second flow channel 32 extend in a first direction, which means they are in the same direction. In this case of a straight flow channel, the resistance of the lubricating oil flow is the smallest and the inertia is the largest.
[0076] In addition, it can be understood that the fourth section 312 and the second flow channel 32 extending along the first direction also means that the first included angle between the fourth section 312 and the second flow channel 32 is 180 degrees. When the third included angle between the third flow channel 33 and the second flow channel 32 is a right angle or an obtuse angle, obviously the third included angle is less than 180 degrees, so as to ensure that more lubricating oil flows into the second flow channel 32, and then enters the first liquid storage cavity 21, so that more lubricating oil can be retained in the housing 11 through the non-direct discharge side, reducing the lubricating oil discharged from the direct discharge side. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved. Moreover, the wear and efficiency reduction problems of the compression mechanism on the direct discharge side are further avoided. Furthermore, the bent connection between the third section 311 and the fourth section 312 allows the designer to flexibly arrange the flow channels in a limited space to meet different mechanical structure requirements. This is particularly important for compact devices because it can maximize the use of available space without sacrificing performance.
[0077] It can be understood that the third section 311 includes but is not limited to a straight pipe structure, and can also be a bent or arc-shaped pipe. The fourth section 312 includes but is not limited to a straight pipe structure.
[0078] Please refer to Figure 3 , in an embodiment of the present invention, the third section 311 extends along the horizontal direction.
[0079] The design in the horizontal direction generally means a more direct path, reducing unnecessary bends and turns, thereby reducing the resistance in fluid flow. This helps to maintain the stability of the lubricating oil flow and improve the overall efficiency of the system. In some installation environments, especially those with limited vertical space, adopting a horizontal flow channel design can effectively utilize the lateral space of the device and avoid design problems caused by height limitations.
[0080] In the above embodiment, further, the first direction is the vertical direction.
[0081] The fourth section 312 and the second flow channel 32 are arranged to extend in the vertical direction, which also means that the first included angle between the fourth section 312 and the second flow channel 32 is 180 degrees. Since the fourth section 312 and the second flow channel 32 are arranged in the vertical direction, obviously the third included angle is less than 180 degrees, so as to ensure that more lubricating oil flows into the second flow channel 32 and then enters the first liquid storage chamber 21, enabling more lubricating oil to be retained in the housing 11 through the non-direct discharge side and reducing the lubricating oil discharged from the direct discharge side. Further, since the vertical direction design may be beneficial to utilizing gravity to assist the flow of lubricating oil, especially when the system is stationary or running at a low speed, it can help the lubricating oil flow more smoothly towards the second flow channel 32, ensuring that the first compression cylinder 13 as the non-direct discharge side can obtain more lubricating oil and reducing the amount of lubricating oil supplied to the second compression cylinder 14. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved, and furthermore, the problems of wear and efficiency reduction of the compression mechanism on the direct discharge side are further avoided.
[0082] Please refer to Figure 4 , in an embodiment of the present invention, the second flow channel 32 includes a fifth section 321 and a sixth section 322 that are connected to each other. The fifth section 321, the air outlet 31b of the first flow channel 31, and the air inlet 32a of the second flow channel 32 are interconnected in a tee shape, and the sixth section 322 is communicated with the inlet 21a of the first liquid storage chamber;
[0083] The fifth section 321 and the sixth section 322 are arranged in a bent connection. The fifth section 321 and the first flow channel 31 are arranged to extend in the second direction.
[0084] In this embodiment, the first flow channel 31 and the fifth section 321 are arranged to extend in the second direction, which means that the first flow channel 31 and the fifth section 321 are arranged in the same direction. In this straight flow channel, the resistance of the lubricating oil flow is the smallest and the inertia is the largest.
[0085] In addition, it can be understood that the first flow channel 31 and the fifth section 321 extending along the first direction also means that the first included angle between the first flow channel 31 and the fifth section 321 is 180 degrees. When the third included angle between the third flow channel 33 and the second flow channel 32 is a right angle or an obtuse angle, obviously the third included angle is less than 180 degrees, so as to ensure that more lubricating oil flows into the second flow channel 32, and then enters the first liquid storage cavity 21, so that more lubricating oil can be retained in the housing 11 through the non-direct discharge side, reducing the lubricating oil discharged from the direct discharge side. In this way, the problem that one of the compression mechanisms in the compressor device with a double-cylinder design has less oil return is solved. Moreover, the wear and efficiency reduction problems of the compression mechanism on the direct discharge side are further avoided. Furthermore, the bent connection between the fifth section 321 and the sixth section 322 allows the designer to flexibly arrange the flow channels within a limited space to meet different mechanical structure requirements. This is particularly important for compact devices because it can maximize the use of available space without sacrificing performance.
[0086] It can be understood that the fifth section 321 includes but is not limited to a straight pipe structure, and can also be a bent or arc-shaped pipe. The sixth section 322 includes but is not limited to a straight pipe structure.
[0087] Please refer to Figure 4 , in an embodiment of the present invention, the second direction is the horizontal direction.
[0088] The design of the horizontal direction usually means a more direct path, reducing unnecessary bends and turns, thereby reducing the resistance in fluid flow. This helps to maintain the stability of the lubricating oil flow and improve the overall efficiency of the system. In some installation environments, especially those with limited vertical space, using the horizontal flow channel design can effectively utilize the lateral space of the equipment and avoid design problems caused by height restrictions.
[0089] Please refer to Figure 4 , in an embodiment of the present invention, the sixth section 322 extends along the vertical direction.
[0090] Since the sixth section 322 is arranged along the vertical direction, the vertical direction design may be beneficial to using gravity to assist the flow of the lubricating oil. Especially when the system is stationary or running at a low speed, it can help the lubricating oil flow more smoothly to the first liquid storage cavity 21, ensure that the first compression cylinder 13 as the non-direct discharge side can obtain more lubricating oil, reduce the amount of lubricating oil supplied to the second compression cylinder 14, and avoid excessive lubricating oil being directly discharged with the compressed gas.
[0091] The present invention also provides a heat exchange system, which includes the above compressor device, and the specific structure of the compressor device refers to the above embodiments. Since the compressor device adopts all the technical solutions of all the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments, and will not be elaborated one by one here.
[0092] The above are only exemplary embodiments of the present invention, and do not limit the patent scope of the present invention. Any equivalent structural transformation made under the technical concept of the present invention by using the content of the specification and drawings of the present invention, or directly / indirectly applied to other related technical fields, is included in the patent protection scope of the present invention.
Claims
1. A compressor device, characterized in that, Comprising: A compressor, including a housing and a compression mechanism disposed within the housing. The housing has a first exhaust port and a second exhaust port, and the compression mechanism has a first compression cylinder and a second compression cylinder arranged vertically. A liquid storage mechanism, having a first liquid storage chamber and a second liquid storage chamber. The outlet of the first liquid storage chamber is communicated with the inlet of the first compression cylinder, the outlet of the first compression cylinder is communicated with the first exhaust port through the inner cavity of the housing, the outlet of the second liquid storage chamber is communicated with the inlet of the second compression cylinder, and the outlet of the second compression cylinder is directly communicated with the second exhaust port. And A flow rate regulating assembly, having an inlet, a first outlet and a second outlet that communicate with each other. The first outlet is communicated with the inlet of the first liquid storage chamber, the second outlet is communicated with the inlet of the second liquid storage chamber. The flow rate regulating assembly is used to distribute the lubricating oil flowing back from the inlet to the first liquid storage chamber and the second liquid storage chamber, and make the lubricating oil flowing back to the first liquid storage chamber greater than the lubricating oil flowing back to the first liquid storage chamber.
2. The compressor device according to claim 1, wherein The flow rate regulating assembly has a first flow channel, a second flow channel and a third flow channel. The first flow channel has the inlet, and the outlet of the first flow channel, the inlet of the second flow channel and the inlet of the third flow channel are interconnected in a tee shape. The second flow channel has the first outlet, and the third flow channel has the second outlet. The first flow channel is connected to the second flow channel at a first angle, the first flow channel is connected to the third flow channel at a second angle, and the first angle is greater than the second angle, so that the flow rate of the first flow channel flowing into the second flow channel is greater than the flow rate of the first flow channel flowing into the third flow channel.
3. The compressor device according to claim 2, characterized in that, The third flow channel is connected to the second flow channel at a third angle, and the third angle is an acute angle.
4. The compressor device according to claim 2, characterized in that, The third flow channel is connected to the second flow channel at a third angle, and the third angle is a right angle or an obtuse angle.
5. The compressor device according to any one of claims 2 to 4, characterized in that The first flow channel and the second flow channel extend along a first direction.
6. The compressor device according to claim 5, wherein, The first direction is the vertical direction.
7. The compressor device according to claim 6, wherein, The third flow channel includes a first section and a second section that communicate with each other. The first section is interconnected in a tee shape with the outlet of the first flow channel and the inlet of the second flow channel, and the second section is connected to the inlet of the second liquid storage chamber.
8. The compressor device according to claim 7, characterized in that, The first section extends along the horizontal direction, the second section extends along the vertical direction, and the second section is connected to the first section in a bent shape.
9. The compressor device according to any one of claims 2 to 4, characterized in that, The first flow channel includes a third section and a fourth section that communicate with each other. The third section has the inlet, and the fourth section has the outlet. The third section is connected to the fourth section in a bent shape, and the fourth section and the second flow channel extend along the first direction.
10. The compressor device according to claim 9, characterized in that, The third section extends along the horizontal direction, and / or, the first direction is the vertical direction.
11. The compressor device according to any one of claims 2 to 4, characterized in that, The second flow channel includes a fifth section and a sixth section that communicate with each other. The fifth section, the outlet of the first flow channel and the inlet of the second flow channel are interconnected in a tee shape, and the sixth section is communicated with the inlet of the first liquid storage chamber. The fifth section is connected to the sixth section in a bent shape, and the fifth section and the first flow channel extend along a second direction.
12. The compressor device according to claim 11, wherein, The second direction is a horizontal direction, and / or the sixth section is arranged in the vertical direction.
13. A heat exchange system, the heat exchange system comprising a compressor device as described in any one of claims 1 to 12.