Compressor system and heat pump system

Abstract

The present disclosure relates to a compressor system and a heat pump system, the compressor system comprising: a compressor (1) having a bearing cavity (2) and a rotor cavity (3); an oil cooling device (4) in communication with the bearing cavity (2) and configured to cool lubricating oil flowing therethrough; wherein the oil cooling device (4), the bearing cavity (2) and the rotor cavity (3) are connected in series through flow channels in sequence, and the rotor cavity (3) is configured to receive lubricating oil heated by the bearing cavity (2).

Description

Technical Field

[0001] This disclosure relates to the field of compressor technology, and more particularly to a compressor system and a heat pump system. Background Technology

[0002] During the operation of a screw compressor, refrigeration oil, as a key lubricating and functional medium, must simultaneously perform core functions such as bearing lubrication, thermal management, and rotor sealing. Its performance directly determines the operating efficiency and reliability of the compressor.

[0003] In related technologies, cooled lubricating oil is supplied separately to the intake-side bearing, exhaust-side bearing, and the meshing area of ​​the male and female rotors through parallel oil supply. This uniform low-temperature oil supply method leads to excessively low oil temperature in the rotor area. Especially for high-temperature vapor heat pump compressors, excessively low rotor oil temperature will over-cool the refrigerant gas in the compression chamber, causing a drop in exhaust temperature. This results in a decrease in the heating capacity and system efficiency of the heat pump system. Furthermore, parallel oil supply also has disadvantages such as high oil circuit system cost, high complexity, and low reliability. Utility Model Content

[0004] In view of this, the present disclosure provides a compressor system and a heat pump system that can take into account both the lubricating oil cooling requirements of the bearing cavity and the exhaust temperature.

[0005] In one aspect of this disclosure, a compressor system is provided, comprising:

[0006] A compressor has a bearing chamber and a rotor chamber;

[0007] An oil cooling device, connected to the bearing cavity, is configured to cool the flowing lubricating oil.

[0008] The oil cooling device, bearing cavity, and rotor cavity are connected in series via flow channels, and the rotor cavity is configured to receive the lubricating oil heated by the bearing cavity.

[0009] In some embodiments, the bearing cavity includes a first bearing cavity near the compressor suction side and a second bearing cavity near the compressor discharge side;

[0010] The compressor system includes:

[0011] The first flow channel is connected at both ends to the inlet of the first bearing cavity and the outlet of the oil cooling device, respectively.

[0012] The second flow channel is connected at both ends to the outlet of the first bearing cavity and the inlet of the second bearing cavity, respectively; and

[0013] The third flow channel is connected at both ends to the outlet of the second bearing cavity and the inlet of the rotor cavity, respectively.

[0014] In some embodiments, the compressor system further includes:

[0015] A first throttling device is disposed at the inlet of the first bearing cavity and / or the inlet of the second bearing cavity. The first throttling device has a throttling orifice and is configured to limit the flow rate of lubricating oil entering the first bearing cavity and / or the second bearing cavity.

[0016] In some embodiments, the diameter of the throttling orifice is positively correlated with the target temperature of the lubricating oil required for the first bearing cavity and / or the second bearing cavity.

[0017] In some embodiments, the oil cooling device includes:

[0018] The second throttling device is configured to regulate the flow rate of lubricating oil entering the bearing cavity.

[0019] In some embodiments, the compressor further includes:

[0020] An oil separator is configured to separate lubricating oil from gaseous refrigerant. The inlet of the oil separator is connected to the outlet of the rotor chamber, and the oil outlet of the oil separator is connected to the inlet of the oil cooling device.

[0021] In some embodiments, the compressor further includes:

[0022] The loading and unloading chamber is connected to the outlet of the oil separator so that the lubricating oil can cool the loading and unloading chamber.

[0023] In some embodiments, the second and third flow channels are located within the compressor housing and on the sides of the bearing cavity and rotor cavity.

[0024] In some embodiments, the inlet of the second bearing cavity is located above the outlet of the first bearing cavity, and the inlet of the second bearing cavity is closer to the inside of the compressor than the outlet of the first bearing cavity.

[0025] The second flow channel includes sub-flow channels that are inclined relative to the vertical direction.

[0026] In another aspect of this disclosure, a heat pump system is provided, comprising:

[0027] compressor systems such as any of the above

[0028] The evaporator is connected to the compressor's air inlet; and

[0029] The condenser is connected to the gaseous refrigerant outlet of the oil separator.

[0030] Therefore, according to the embodiments of this disclosure, the oil cooling device, bearing cavity, and rotor cavity are connected in series in sequence. The lubricating oil heated by passing through the bearing cavity is used for the temperature-sensitive rotor seal, realizing the cascade utilization of energy within the system. Lubricating oil at corresponding temperatures is provided for different parts of the compressor, taking into account the lubricating oil cooling requirements of the compressor bearing cavity, the sealing requirements of the rotor cavity, and the exhaust temperature. This satisfies the bearing cavity's need for low-temperature lubricating oil, optimizes the bearing lubrication effect, and extends the bearing service life. It also prevents excessively low-temperature lubricating oil from entering the rotor cavity and excessively lowering the refrigerant temperature, thereby preventing the compressor exhaust temperature from dropping to a dangerous range. This improves the separation ability of the lubricating oil from the gaseous refrigerant, increases the purity and lubrication ability of the lubricating oil, and enhances the heating capacity and energy efficiency ratio of the compressor system. Attached Figure Description

[0031] The accompanying drawings, which form part of this specification, illustrate embodiments of this disclosure and, together with the specification, serve to explain the principles of this disclosure.

[0032] This disclosure will become clearer with reference to the accompanying drawings and the following detailed description, wherein:

[0033] Figure 1 These are schematic diagrams of the structure of some embodiments of the compressor system according to this disclosure;

[0034] Figure 2 These are cross-sectional views of some embodiments of the compressor system according to this disclosure;

[0035] Figure 3 These are cross-sectional views of some embodiments of the first bearing cavity of the compressor system according to this disclosure;

[0036] Figure 4A These are cross-sectional views of some embodiments of the second flow path of the compressor system according to this disclosure;

[0037] Figure 4B yes Figure 4A Cross-sectional views of some embodiments of the central region C;

[0038] Figure 5A These are cross-sectional views of some other embodiments of the second flow path of the compressor system according to this disclosure;

[0039] Figure 5B yes Figure 5A Cross-sectional views of some embodiments of the central region D;

[0040] Figure 6 These are cross-sectional views of some embodiments of the third flow channel of the compressor system according to this disclosure;

[0041] Figure 7 These are cross-sectional views of some other embodiments of the third flow path of the compressor system according to this disclosure;

[0042] Figure 8A These are schematic diagrams of the structure of some embodiments of the first throttling device of the compressor system according to this disclosure;

[0043] Figure 8B This is a cross-sectional view of some embodiments of the first throttling device of the compressor system according to the present disclosure.

[0044] In the picture:

[0045] 1. Compressor; 11. Compressor oil inlet; 12. Compressor oil outlet; 13. Machine body; 14. Suction side end cover; 15. Discharge side end cover; 16. Slide valve; 17. Discharge side bearing housing; 18. Cylinder body; 19. Oil separator end component;

[0046] 2. Bearing cavity; 21. First bearing cavity; 211. First main oil passage; 212. First female rotor bearing; 213. First male rotor bearing; 22. Second bearing cavity; 221. Second female rotor bearing; 222. Second male rotor bearing;

[0047] 3. Rotor cavity;

[0048] 4. Oil cooling device;

[0049] 51. First flow channel; 52. Second flow channel; 53. Third flow channel; 54. Fourth flow channel;

[0050] 6. Oil separation device;

[0051] 71. First throttling device; 711. Throttling orifice;

[0052] 8. Loading / unloading chamber; 81. Oil supply port for loading / unloading chamber.

[0053] It should be understood that the dimensions of the various parts shown in the accompanying drawings are not drawn to actual scale. Furthermore, the same or similar reference numerals denote the same or similar components. Detailed Implementation

[0054] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The descriptions of the exemplary embodiments are merely illustrative and are in no way intended to limit the present disclosure or its application or use. The present disclosure may be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that the present disclosure will be thorough and complete, and will fully express the scope of the disclosure to those skilled in the art. It should be noted that, unless specifically stated otherwise, the relative arrangement of components and steps, the composition of materials, numerical expressions, and values ​​set forth in these embodiments should be interpreted as exemplary only and not as limiting.

[0055] The terms "first," "second," and similar words used in this disclosure do not indicate any order, quantity, or importance, but are merely used to distinguish different parts. Words such as "including" or "contains" mean that the element preceding the word encompasses the element listed after it, and do not exclude the possibility of encompassing other elements as well. Terms such as "above," "below," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, this relative positional relationship may also change accordingly.

[0056] In this disclosure, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not be present between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may be not directly connected to the other devices but have an intermediary device.

[0057] All terms used in this disclosure (including technical or scientific terms) have the same meaning as understood by one of ordinary skill in the art to which this disclosure pertains, unless otherwise specifically defined. It should also be understood that terms defined in a general dictionary, such as a dictionary, should be interpreted as having a meaning consistent with their meaning in the context of the relevant art, and not as having an idealized or highly formalized meaning, unless expressly defined herein.

[0058] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0059] During the operation of a screw compressor, refrigeration oil, as a key lubricating and functional medium, must simultaneously perform core functions such as bearing lubrication, thermal management, and rotor sealing. Its performance directly determines the operating efficiency and reliability of the compressor.

[0060] Specifically, intake and exhaust bearings need to withstand alternating loads and high-temperature environments during high-speed operation. This requires the refrigeration oil to have suitable viscosity characteristics in order to form a uniform and stable liquid oil film on the bearing friction surface. This not only effectively reduces frictional resistance but also dissipates bearing frictional heat, ensuring that the bearing is within a suitable operating temperature range, thereby avoiding direct metal-to-metal wear caused by oil film rupture.

[0061] Furthermore, the meshing clearance between the male and female rotors also relies on refrigeration oil for dynamic sealing to prevent refrigerant gas leakage and maintain the compressor's volumetric efficiency. Insufficient lubricating oil performance may lead to decreased sealing effectiveness, resulting in problems such as reduced efficiency, increased energy consumption, and system instability.

[0062] In related technologies, the oil circuit system of a compressor typically includes an oil separator, an oil cooler, etc. After the refrigeration oil is collected by the oil separator, it is cooled down by the oil cooler. Finally, the cooled lubricating oil is supplied to the suction side bearing, the exhaust side bearing, and the male and female rotor meshing area through parallel oil supply.

[0063] This uniform low-temperature oil supply method can lead to excessively low oil temperature in the rotor area. Especially for high-temperature steam heat pump compressors, excessively low oil temperature in the rotor area will overcool the refrigerant gas in the compression chamber, resulting in a drop in exhaust temperature. This leads to a decrease in the heating capacity and system efficiency of the heat pump system. In addition, parallel oil supply also has the disadvantages of high oil circuit system cost, high complexity, and low reliability.

[0064] For high-temperature heat pump compressors, there are significant contradictions between the oil circuit system and the parallel oil supply scheme in related technologies regarding the bearing cooling requirements (requiring low-temperature oil) and the rotor sealing / efficiency requirements (requiring higher-temperature oil). This makes it difficult for traditional oil supply systems to simultaneously meet the coordinated requirements of bearing heat dissipation and rotor sealing, and will lead to technical bottlenecks such as reduced exhaust temperature and decreased energy efficiency ratio.

[0065] In view of this, in one aspect of the present disclosure, a compressor system is provided that can take into account both the lubricating oil cooling requirements of the bearing cavity and the exhaust temperature.

[0066] Figure 1 These are schematic diagrams illustrating the structure of some embodiments of the compressor system according to this disclosure. Figure 2 These are cross-sectional views of some embodiments of the compressor system according to this disclosure. Figure 1 , 2 The arrows in the diagram indicate the direction of lubricant flow. (Reference) Figure 1 and Figure 2 The compressor system includes compressor 1 and oil cooling device 4.

[0067] Compressor 1 is a screw compressor, having a bearing chamber 2 and a rotor chamber 3. An oil cooling device 4 is connected to the bearing chamber 2 and is configured to cool the flowing lubricating oil. The oil cooling device 4, the bearing chamber 2, and the rotor chamber 3 are connected in series via flow channels. The rotor chamber 3 is configured to receive the lubricating oil heated by the bearing chamber 2.

[0068] The lubricating oil in bearing cavity 2 plays a role in cooling the bearing temperature and lubricating the bearing contact surface. The bearing has a minimum viscosity requirement for the lubricating oil. If the viscosity is too low, the lubricating oil will be difficult to adhere to the bearing contact surface, resulting in dry friction and reducing the working life of the bearing.

[0069] The rotor chamber 3 includes a female rotor and a male rotor, and the refrigerant is compressed by the meshing of the female and male rotors. The compressor 1 may be equipped with a motor to drive the female and male rotors.

[0070] The lubricating oil in the rotor cavity 3 plays a role in lubrication, sealing and cooling. It seals the gap between the female and male rotors, cools the refrigerant in the rotor cavity 3 during the compression process, and appropriately reduces the outlet exhaust temperature of the compressor.

[0071] The compressor system can be used in both heat pump and refrigeration systems, both of which can provide heating or cooling. The oil cooling device 4 may include a heat exchanger or heat pipes, etc.

[0072] The oil cooling device 4 is connected to the oil inlet 11 and the oil outlet 12 of the compressor respectively. The high-temperature lubricating oil flows to the oil cooling device 4 through the oil outlet 12 of the compressor to achieve cooling. Then, it flows into the compressor 1 through the pipeline and the oil inlet 11 of the compressor, and enters the bearing cavity 2 and the rotor cavity 3 in sequence.

[0073] The oil cooling device 4, bearing cavity 2, and rotor cavity 3 are connected in series through flow channels. The heat generated by the bearing itself in bearing cavity 2 is used to heat the lubricating oil with a lower temperature provided by oil cooling device 4. The oil temperature entering rotor cavity 3 is increased and the viscosity is suitable to form a stable oil film seal on the rotor meshing surface, reduce internal leakage of the working fluid, and improve volumetric efficiency and compression efficiency.

[0074] Compared to the conflicting requirements of bearing cooling (requiring low-temperature lubricating oil) and rotor sealing and operation (requiring high-temperature lubricating oil) in related technologies, this embodiment sets the bearing cavity 2 and rotor cavity 3 in a series oil circuit. The lubricating oil absorbs heat when passing through the bearing cavity 2, making the oil temperature entering the rotor cavity 3 higher than the oil temperature provided by the oil cooling device 4. Moreover, its temperature is determined by the heat generated by the bearing. There is no need to set up additional sensors, diverter valves, temperature control valves or control systems for active adjustment, which can reduce system complexity and cost and improve system reliability.

[0075] In this embodiment, by connecting the oil cooling device 4, bearing cavity 2, and rotor cavity 3 in series, the heat generated by the bearing cavity 2 heats the frozen lubricating oil, raising its temperature and achieving a more suitable viscosity. This allows the lubricating oil to fill the temperature-sensitive rotor gaps, achieving a stable oil film seal, reducing internal leakage of the working fluid, and converting the bearing heat into a useful heat source. This enables the cascade utilization of energy within the system, providing lubricating oil at corresponding temperatures for different parts of the compressor 1. It balances the lubricating oil cooling needs of the bearing cavity 2, the sealing needs of the rotor cavity 3, and the exhaust temperature. This satisfies the bearing cavity 2's need for low-temperature lubricating oil, optimizing bearing lubrication and extending bearing life. It also prevents excessively low-temperature lubricating oil from entering the rotor cavity 3 and excessively lowering the refrigerant temperature, thus preventing the compressor exhaust temperature from dropping to a dangerous range. Furthermore, it improves the separation ability of the lubricating oil from the gaseous refrigerant, increases the purity and lubrication capacity of the lubricating oil, and enhances the heating capacity and energy efficiency ratio of the compressor system.

[0076] Figure 3 These are cross-sectional views of some embodiments of the first bearing cavity of the compressor system according to this disclosure. Figure 4A These are cross-sectional views of some embodiments of the second flow path of the compressor system according to this disclosure. Figure 4B yes Figure 4A Cross-sectional views of some embodiments of region C, Figure 5A These are cross-sectional views of some other embodiments of the second flow path of the compressor system according to this disclosure. Figure 5B yes Figure 5A Cross-sectional views of some embodiments of region D, Figure 6 These are cross-sectional views of some embodiments of the third flow channel of the compressor system according to this disclosure. Figure 7 These are cross-sectional views of some other embodiments of the third flow path of the compressor system according to this disclosure. Figures 3-7 The arrows in the diagram indicate the direction of lubricant flow. (Reference) Figures 1-7 In some embodiments, the bearing cavity 2 includes a first bearing cavity 21 near the suction side of the compressor 1 and a second bearing cavity 22 near the discharge side of the compressor.

[0077] The compressor system includes a first flow channel 51, a second flow channel 52, and a third flow channel 53 to guide the flow of lubricating oil. The two ends of the first flow channel 51 are connected to the inlet of the first bearing cavity 21 and the outlet of the oil cooling device 4, respectively. The two ends of the second flow channel 52 are connected to the outlet of the first bearing cavity 21 and the inlet of the second bearing cavity 22, respectively. The two ends of the third flow channel 53 are connected to the outlet of the second bearing cavity 22 and the inlet of the rotor cavity 3, respectively.

[0078] The first bearing cavity 21 has a first main oil passage 211, a first female rotor bearing 212 and a first male rotor bearing 213. Lubricating oil enters the first main oil passage 211 through the first flow channel 51 and then flows to the first female rotor bearing 212 and the first male rotor bearing 213 respectively.

[0079] The second bearing cavity 22 contains a second female rotor bearing 221 and a second male rotor bearing 222. There are two second flow channels 52, which connect the first female rotor bearing 212 and the second female rotor bearing 221, and respectively connect the first male rotor bearing 213 and the second male rotor bearing 222.

[0080] The lubricating oil then flows through the second flow channel 52 from the first female rotor bearing 212 to the second female rotor bearing 221, and through the second flow channel 52 from the first male rotor bearing 213 to the second male rotor bearing 222.

[0081] There are two third flow channels 53. After the bearing is lubricated, the lubricating oil flows from the second female rotor bearing 221 and the second male rotor bearing 222 to the rotor cavity 3 through the two third flow channels 53 respectively. The heated lubricating oil seals the rotor meshing gap in the rotor cavity 3.

[0082] The low-temperature lubricating oil flowing out of the outlet of the oil cooling device 4 flows through the first bearing cavity 21 and the second bearing cavity 22 in sequence. While cooling and lubricating the intake and exhaust bearings, it absorbs heat. Finally, after being heated twice, the temperature of the low-temperature lubricating oil is increased in stages. The lubricating oil with a significantly increased temperature enters the rotor cavity 3, avoiding excessive cooling of the refrigerant gas in the compression cavity by the low-temperature refrigerated lubricating oil, thereby stabilizing the exhaust temperature.

[0083] The temperature rise of the lubricating oil varies with the refrigerant, the type of matching lubricating oil, and the ambient temperature in different seasons. In some embodiments, if the temperature of the lubricating oil entering the first bearing cavity 21 is 60~80℃, the temperature of the lubricating oil entering the second bearing cavity 22 is expected to be 100±5℃, and finally the temperature of the lubricating oil entering the rotor cavity 3 is 140℃. The temperature of the gaseous refrigerant at the suction port of the compressor 1 is 40℃, the exhaust temperature of the lubricating oil when it is discharged together with the gaseous refrigerant is 140℃, and the oil temperature of the lubricating oil after separation by the oil separator 6 is 130℃.

[0084] The series-connected flow channels eliminate the need for multiple branch oil circuits, resulting in a more reliable structure. They also reduce the need for flow dividers, thereby lowering system complexity and cost.

[0085] In this embodiment, the heat generated by the bearing that requires energy cooling in the refrigeration system of the related technology is converted into an effective heat source through a series oil circuit. The low-temperature lubricating oil is heated twice by the first bearing cavity 21 and the second bearing cavity 22 to achieve a step-by-step temperature rise of the lubricating oil. The temperature is significantly increased when it enters the rotor cavity 3. By utilizing the energy in the system in a step-by-step manner, the problem of excessive cooling of compressed gas and reduction of exhaust temperature caused by the direct entry of overcooled lubricating oil into the rotor cavity 3 is avoided. This can improve the heating capacity and energy efficiency ratio of the compressor system.

[0086] Figure 8A These are schematic diagrams illustrating the structure of some embodiments of the first throttling device of the compressor system according to this disclosure. Figure 8B This is a cross-sectional view of some embodiments of the first throttling device of the compressor system according to the present disclosure, with reference to... Figure 5B , Figure 8A and Figure 8B In some embodiments, the compressor system further includes a first throttling device 71 disposed at the inlet of the first bearing cavity 21 and / or the inlet of the second bearing cavity 22, the first throttling device 71 having a throttling orifice 711 configured to limit the flow rate of lubricating oil entering the first bearing cavity 21 and / or the second bearing cavity 22.

[0087] The first throttling device 71 is detachably installed at the inlet of the first bearing cavity 21 and / or the inlet of the second bearing cavity 22 to control the flow rate of lubricating oil entering the first bearing cavity 21 and / or the second bearing cavity 22, thereby allowing for targeted adjustment of the cooling effect of the lubricating oil.

[0088] In this embodiment, by setting a first throttling device 71 at the inlet of the first bearing cavity 21 and / or the inlet of the second bearing cavity 22, the flow rate of the lubricating oil entering the first bearing cavity 21 and / or the second bearing cavity 22 can be adjusted. This can avoid the situation where the lubricating oil flow rate is too large, which increases the energy consumption of the oil pump and reduces the efficiency of the compressor 1. It can also avoid the situation where the lubricating oil flow rate is too small, which leads to insufficient cooling and causes the bearing to overheat and affect the operational stability. This allows the lubricating oil to efficiently and accurately remove the heat generated by the bearing, providing a suitable cooling temperature to the bearing while increasing the temperature of the discharged lubricating oil.

[0089] refer to Figure 5B , Figure 8A and Figure 8B In some embodiments, the diameter of the throttle orifice 711 is positively correlated with the target temperature of the lubricating oil required for the first bearing cavity 21 and / or the second bearing cavity 22.

[0090] The first throttling device 71 is cylindrical, and the throttling orifice 711 extends through the inside of the first throttling device 71 along the flow direction of the lubricating oil. The throttling orifice 711 includes, but is not limited to, a through hole with the same diameter d or a diameter d that varies with the flow direction of the lubricating oil.

[0091] The first throttling device 71 is a standard part, and the throttling orifice 711 has different diameter specifications. Users can select the first throttling device 71 with different throttling orifice 711 diameters according to actual application conditions, such as adjusting according to the current bearing temperature, the target bearing temperature and / or the lubricating oil temperature entering the rotor cavity 3.

[0092] When the target bearing temperature in bearing cavity 2 is high, the user uses a first throttling device 71 with a larger diameter throttling orifice 711 to increase the flow rate of lubricating oil entering bearing cavity 2, thereby increasing the bearing temperature.

[0093] When the target bearing temperature in bearing cavity 2 is low, the user uses a first throttling device 71 with a smaller diameter throttling orifice 711 to reduce the flow rate of lubricating oil entering bearing cavity 2, thereby keeping the bearing temperature low.

[0094] Users can also select first throttling devices 71 with different diameter throttling orifices 711 based on the difference between the current temperature of bearing cavity 2 and the target bearing temperature. When the temperature of bearing cavity 2 is lower than the target bearing temperature, the user uses the first throttling device 711 with a smaller diameter throttling orifice 711 to reduce the flow rate of lubricating oil entering bearing cavity 2, thereby raising the bearing temperature to the target bearing temperature. When the temperature of bearing cavity 2 is higher than the target bearing temperature, the user uses the first throttling device 711 with a larger diameter throttling orifice 711 to increase the flow rate of lubricating oil entering bearing cavity 2, thereby lowering the bearing temperature to the target bearing temperature.

[0095] In this embodiment, the user may adjust the diameter of the throttling orifice 711 of the first throttling device 71 according to the required lubricating oil temperature, the specific model of the compressor 1 and the actual application conditions, so as to achieve better cooling and lubrication in the bearing cavity 2 and sealing and compression efficiency in the rotor cavity 3.

[0096] In some embodiments, the oil cooling device 4 includes a second throttling device configured to regulate the flow rate of lubricating oil entering the bearing cavity 2, the second throttling device including a throttle valve.

[0097] The flow rate of the lubricating oil is regulated by the second throttling device of the oil cooling device 4 to adjust the initial temperature of the lubricating oil when it enters the first bearing cavity 21, so as to ensure reliable lubrication and cooling of the bearing and efficient operation of the compressor 1.

[0098] When the initial supply temperature of the lubricating oil is lower than the target value, the user can increase the flow rate of the lubricating oil through the oil cooling device 4 by adjusting the second throttling device, thereby increasing the initial supply temperature of the lubricating oil.

[0099] When the initial supply temperature of the lubricating oil is higher than the target value, the user can reduce the flow rate of the lubricating oil through the oil cooling device 4 by adjusting the second throttling device, thereby reducing the initial supply temperature of the lubricating oil.

[0100] In this embodiment, the flow rate of the lubricating oil through the oil cooling device 4 is adjusted by setting a second throttling device, thereby adjusting the initial oil supply temperature of the lubricating oil entering the bearing cavity 2, so that the lubricating oil can reliably lubricate and cool the bearing and meet the temperature requirements of the rotor cavity 3, and enable the compressor 1 to operate efficiently.

[0101] refer to Figure 2 In some embodiments, the compressor 1 further includes an oil separator 6, the inlet of which is connected to the outlet of the rotor cavity 3, and the oil outlet of which is connected to the inlet of the oil cooling device 4. The oil separator 6 is configured to separate lubricating oil from the gaseous refrigerant. The oil separator 6 can be a centrifugal lubricating oil separation structure, or a filter type, packing type, or washing type lubricating oil separation structure.

[0102] The lubricating oil and refrigerant discharged from the rotor chamber 3 are mixed and separated by the oil separation device 6 built into the compressor 1. The separated lubricating oil is discharged through the oil outlet 12 of the compressor to the oil cooling device 4. The lubricating oil cooled by the oil cooling device 4 flows back into the compressor 1 through the oil inlet 11 of the compressor.

[0103] In this embodiment, the lubricating oil and refrigerant are separated by an oil separation device 6, so that the high-temperature lubricating oil is cooled by the oil cooling device 4 before being supplied to the bearing cavity 2, thereby improving the heat exchange efficiency of the compressor system and reducing energy consumption.

[0104] refer to Figure 1 and Figure 2 In some embodiments, the compressor 1 further includes a loading / unloading chamber 8, which is connected to the outlet of the oil separator 6 to allow lubricating oil to cool the loading / unloading chamber 8. The loading / unloading chamber 8 uses a solenoid valve to control the loading / unloading and pressure ratio adjustment of the compressor 1.

[0105] The compressor system also includes a fourth flow channel 54, which is connected to the outlet of the oil separator 6 and the loading / unloading chamber 8 respectively. The fourth flow channel 54 is connected in parallel with the first flow channel 51, the second flow channel 52 and the third flow channel 53.

[0106] When the loading / unloading chamber 8 requires cooling, lubricating oil enters the loading / unloading chamber 8 through the fourth flow channel 54 to cool the loading / unloading chamber 8. The loading / unloading chamber oil supply port 81 of the loading / unloading chamber 8 is located above the body 13 of the compressor 1.

[0107] In this embodiment, by connecting the loading / unloading chamber 8 to the oil separation device 6 for cooling and lubrication of the loading / unloading chamber 8, a more stable and controllable thermal environment can be provided for the loading / unloading process of the compressor 1, which helps to improve the volumetric efficiency and energy efficiency of the compressor system.

[0108] refer to Figure 4A , Figure 4B , Figure 5A , Figure 6 and Figure 7 In some embodiments, the second flow channel 52 and the third flow channel 53 are located inside the body 13 of the compressor 1 and on the side of the bearing cavity 2 and the rotor cavity 3, including but not limited to the left or right side.

[0109] Flow channels are formed by drilling holes in the side walls of the compressor body 13 and the exhaust side bearing housing 17. For different models of compressor 1, the specific positions of the second flow channel 52 and the third flow channel 53 can be flexibly adjusted according to the processing difficulty and the opening space.

[0110] The height of the flow channel can be adjusted according to the specific oil level of the bearing. The oil level of different compressors can be adjusted according to actual needs to prevent the oil level from being too high, which would increase the mechanical stirring work, or to avoid the situation where the bearing cannot be quickly lubricated, especially during startup, when the oil level is too low.

[0111] When the lubricating oil in the first bearing cavity 21 is higher than the set oil storage height, the lubricating oil will be discharged from the first bearing cavity 21 and flow to the second bearing cavity 22 through the second flow channel 52 to achieve bearing cooling and lubrication. The lubricating oil absorbs the heat of the bearing and the temperature rises.

[0112] When the lubricating oil in the second bearing cavity 22 is higher than the set oil storage height, the lubricating oil will be discharged from the second bearing cavity 22 and then flow to the rotor cavity 3 through the third flow channel 53, ultimately achieving the sealing of the rotor meshing gap and stabilizing the exhaust temperature.

[0113] In this embodiment, based on actual processing considerations, the second flow channel 52 and the third flow channel 53 are opened on the side of the housing 13 and the exhaust side bearing seat 17 to improve processing convenience, reduce interference with the internal structure of the compressor 1, and reduce manufacturing costs and complexity.

[0114] refer to Figure 4B In some embodiments, the inlet of the second bearing cavity 22 is located above the outlet of the first bearing cavity 21, and the inlet of the second bearing cavity 22 is closer to the inside of the compressor 1 relative to the outlet of the first bearing cavity 21. The second flow channel 52 includes a sub-flow channel that is inclined relative to the vertical direction.

[0115] In this embodiment, the position of the second flow channel 52 can be flexibly adjusted according to the positional relationship between the inlet of the second bearing cavity 22 and the outlet of the first bearing cavity 21. When the inlet of the second bearing cavity 22 is located above the outlet of the first bearing cavity 21 and the inlet of the second bearing cavity 22 is closer to the inner side of the compressor 1 than the outlet of the first bearing cavity 21, the second flow channel 52 is provided with a sub-flow channel that is inclined inward and extends upward in the vertical direction, so as to meet the flow requirements of lubricating oil according to the spatial layout inside the body 13 and facilitate processing and manufacturing.

[0116] refer to Figure 2 The compressor 1 also includes an intake side end cover 14, an exhaust side end cover 15, a slide valve 16, an exhaust side bearing seat 17, an oil cylinder body 18, and an oil separator end component 19.

[0117] In another aspect of this disclosure, a heat pump system is provided, including a compressor system, an evaporator, and a condenser as described in any of the above embodiments. The evaporator is connected to the air inlet of the compressor 1, and the condenser is connected to the gaseous refrigerant outlet of the oil separator 6.

[0118] In this embodiment, the heat pump system can provide lubricating oil at corresponding temperatures for different parts of the compressor. This satisfies the bearing cavity 2's need for low-temperature lubricating oil, optimizes bearing lubrication, and extends bearing life. It also prevents excessively low-temperature lubricating oil from entering the rotor cavity 3 and excessively lowering the refrigerant temperature, thereby preventing the compressor's exhaust temperature from dropping to a dangerous range. This improves the lubricating oil's ability to separate from the gaseous refrigerant, enhances the lubricating oil's purity and lubrication capacity, and balances the lubricating oil cooling needs of the compressor 1's bearing cavity 2 with the compressor 1's exhaust temperature. This allows the compressor's oil temperature control to reach a balanced state, stabilizes the exhaust temperature, and improves the compressor system's heating capacity and energy efficiency ratio, thus enhancing the heat pump system's heating capacity and energy efficiency.

[0119] The embodiments of this disclosure have now been described in detail. To avoid obscuring the concept of this disclosure, some details known in the art have not been described. Those skilled in the art can fully understand how to implement the technical solutions disclosed herein based on the above description.

[0120] While specific embodiments of this disclosure have been described in detail by way of examples, those skilled in the art should understand that the examples are for illustrative purposes only and not intended to limit the scope of this disclosure. Those skilled in the art should understand that modifications can be made to the above embodiments or equivalent substitutions can be made to some technical features without departing from the scope and spirit of this disclosure. The scope of this disclosure is defined by the appended claims.

Claims

1. A compressor system, characterized in that, include: The compressor (1) has a bearing cavity (2) and a rotor cavity (3); and An oil cooling device (4) is connected to the bearing cavity (2) and is configured to cool the flowing lubricating oil. The oil cooling device (4), the bearing cavity (2) and the rotor cavity (3) are connected in series through a flow channel, and the rotor cavity (3) is configured to receive the lubricating oil heated by the bearing cavity (2).

2. The compressor system as described in claim 1, characterized in that, The bearing cavity (2) includes a first bearing cavity (21) near the suction side of the compressor (1) and a second bearing cavity (22) near the discharge side of the compressor. The compressor system includes: The first flow channel (51) has two ends connected to the inlet of the first bearing cavity (21) and the outlet of the oil cooling device (4), respectively. The second flow channel (52) has its two ends connected to the outlet of the first bearing cavity (21) and the inlet of the second bearing cavity (22), respectively; and The third flow channel (53) has its two ends connected to the outlet of the second bearing cavity (22) and the inlet of the rotor cavity (3), respectively.

3. The compressor system as described in claim 2, characterized in that, Also includes: A first throttling device (71) is disposed at the inlet of the first bearing cavity (21) and / or the inlet of the second bearing cavity (22), the first throttling device (71) having a throttling orifice (711) configured to limit the flow rate of lubricating oil entering the first bearing cavity (21) and / or the second bearing cavity (22).

4. The compressor system as described in claim 3, characterized in that, The diameter of the throttling orifice (711) is positively correlated with the target temperature of the lubricating oil required for the first bearing cavity (21) and / or the second bearing cavity (22).

5. The compressor system as described in claim 1, characterized in that, The oil cooling device (4) includes: The second throttling device is configured to regulate the flow rate of the lubricating oil entering the bearing cavity (2).

6. The compressor system as described in claim 2, characterized in that, The compressor (1) also includes: An oil separator (6) is provided, the inlet of which is connected to the outlet of the rotor chamber (3), and the oil outlet of which is connected to the inlet of the oil cooling device (4). The oil separator (6) is configured to separate lubricating oil from the gaseous refrigerant.

7. The compressor system as described in claim 6, characterized in that, The compressor (1) also includes: The loading / unloading chamber (8) is connected to the outlet of the oil separator (6) so that the lubricating oil cools the loading / unloading chamber (8).

8. The compressor system as described in claim 2, characterized in that, The second flow channel (52) and the third flow channel (53) are located inside the body (13) of the compressor (1) and on the side of the bearing cavity (2) and the rotor cavity (3).

9. The compressor system as described in claim 2, characterized in that, The inlet of the second bearing cavity (22) is located above the outlet of the first bearing cavity (21), and the inlet of the second bearing cavity (22) is closer to the inside of the compressor (1) than the outlet of the first bearing cavity (21); The second flow channel (52) includes a sub-flow channel that is inclined relative to the vertical direction.

10. A heat pump system, characterized in that, include: The compressor system as described in any one of claims 1 to 9; The evaporator is connected to the air inlet of the compressor (1); and The condenser is connected to the gaseous refrigerant outlet of the oil separator (6).

Images