WO2020042457A1 - 空调系统、压缩供油装置及其控制方法 - Google Patents

空调系统、压缩供油装置及其控制方法 Download PDF

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Publication number
WO2020042457A1
WO2020042457A1 PCT/CN2018/122223 CN2018122223W WO2020042457A1 WO 2020042457 A1 WO2020042457 A1 WO 2020042457A1 CN 2018122223 W CN2018122223 W CN 2018122223W WO 2020042457 A1 WO2020042457 A1 WO 2020042457A1
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WIPO (PCT)
Prior art keywords
oil supply
compressor
oil
throttle
valve
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Ceased
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PCT/CN2018/122223
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English (en)
French (fr)
Inventor
张仕强
焦华超
武连发
冯涛
李立民
周冰
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Publication of WO2020042457A1 publication Critical patent/WO2020042457A1/zh
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present application relates to the technical field of air conditioning equipment, and in particular, to an air conditioning system, a compression oil supply device, and a control method thereof.
  • the compressor is supplied from the compressor suction port. Because the supplied refrigerated oil is high temperature, after the high temperature refrigerated oil sucked by the compressor suction port is mixed with the refrigerant gas sucked by the compressor, the refrigerant oil heats the refrigerant gas to increase the temperature of the refrigerant gas, resulting in refrigerant suction.
  • the increase in air specific volume reduces the mass flow of the refrigerant cycle on the one hand and affects the performance of the air conditioner, and on the other hand increases the intake temperature, which in turn increases the exhaust temperature and affects the performance and reliability of the compressor.
  • a compression oil supply device includes:
  • the first oil supply component includes:
  • a first oil supply line connecting the oil supply hole and the air supply port
  • a first valve provided on the first oil supply line the first valve is used to control the on-off of the first oil supply line.
  • the first fuel supply assembly further includes a first throttle component, and the first throttle component is disposed on the first fuel supply pipeline for restricting the first fuel supply pipe. Lubricant flow in the road.
  • the first throttle component includes an electronic expansion valve, an orifice plate, a capillary tube, or a throttle valve.
  • the first throttle component includes a throttle tube, and a diameter of the throttle tube is 0.1 to 0.8 times a diameter of the first fuel supply pipeline;
  • Both ends of the throttle pipe are respectively connected to the first oil supply pipe, or the throttle pipe is disposed in the first oil supply pipe.
  • the compressor further has an air inlet
  • the compression oil supply device further includes a second oil supply component, and the second oil supply component connects the air inlet and the oil supply hole.
  • the second fuel supply component includes:
  • a second oil supply line connecting the oil supply hole and the air inlet
  • a second valve provided on the second oil supply pipeline is used to control the on-off of the second oil supply pipeline.
  • the second fuel supply assembly further includes a second throttle component, and the second throttle component is disposed on the second fuel supply pipeline for restricting the second fuel supply pipe. Lubricant flow in the road.
  • the second throttle component includes an electronic expansion valve, an orifice plate, a throttle tube, a capillary tube, or a throttle valve.
  • the second throttling component includes a throttling tube, and a diameter of the throttling tube is 0.1 to 0.8 times a diameter of the second oil supply pipeline;
  • Both ends of the throttle pipe are respectively connected to the second oil supply pipe, or the throttle pipe is disposed in the second oil supply pipe.
  • a control method of a compression oil supply device which is applied to the compression oil supply device according to any of the above technical features, includes the following steps:
  • the first valve of the compressor is opened, the second valve is closed, and the compressor's charge port is returned to oil;
  • the first valve and the second valve of the compressor are opened at the same time, and the compressor's make-up port and suction port return oil at the same time.
  • the operating conditions where the actual demand is higher than the compressor's normal demand include at least frequency-increasing operating conditions and / or low-temperature operating conditions.
  • An air conditioning system including a heat exchanger and a compression oil supply device according to any one of the above technical features
  • the heat exchanger is connected to an air outlet of the oil separator, and is used for heat exchange treatment of the refrigerant.
  • the first oil supply component sends the lubricating oil of the oil separator to the compressor through the supplementary air port to meet the lubrication needs of the compressor during operation.
  • the lubricating oil enters the compressor through the compressor's make-up port, and the temperature of the lubricating oil is not much different from the temperature of the refrigerant at the make-up port, so there is no problem of heating the refrigerant. Effectively solve the current problem of large refrigerant suction specific volume caused by the heating of the refrigerant by the lubricating oil at the suction port.
  • the specific volume of the refrigerant can be reduced, the suction temperature of the compressor can be lowered, and the exhaust temperature can be lowered to improve the reliability of the compressor operation.
  • the mass flow of the refrigerant cycle can be increased to improve the performance of the air conditioning system.
  • FIG. 1 is a schematic diagram of a compression oil supply device according to an embodiment of the present application.
  • connection and “connection” in this application include direct and indirect connections (connections) unless otherwise specified.
  • the first feature "on” or “down” of the second feature may be the first and second features in direct contact, or the first and second features indirectly through an intermediate medium. contact.
  • the first feature is “above”, “above”, and “above” the second feature.
  • the first feature is directly above or obliquely above the second feature, or only indicates that the first feature is higher in level than the second feature.
  • the first feature is “below”, “below”, and “below” of the second feature.
  • the first feature may be directly below or obliquely below the second feature, or it may simply indicate that the first feature is less horizontal than the second feature.
  • the present application provides a compression oil supply device 100.
  • the compression oil supply device 100 is applied in an air-conditioning system to realize the oil supply of the compressor 110.
  • the compression oil supply device 100 of the present application can reduce the specific volume of the refrigerant, improve the performance and operation reliability of the compressor 110, and improve the performance of the air conditioning system.
  • the compression oil supply device 100 includes a compressor 110, an oil separator 120, and a first oil supply assembly 130.
  • the compressor 110 includes an air supply port 111 and an exhaust port 112.
  • the compressor 110 is used to compress a refrigerant gas.
  • the compressor 110 also has an air inlet 113.
  • the refrigerant is sucked into the compressor 110 through the suction port 113, is compressed, and is discharged from the exhaust port 112.
  • the compressor 110 also replenishes refrigerant through the air supply port 111 to ensure the performance of the compressor 110.
  • the oil separator 120 includes an air inlet 121 and an oil supply hole 122.
  • the exhaust port 112 of the compressor 110 is in communication with the intake port 121 of the oil separator 120.
  • the oil separator 120 is used to separate lubricating oil and refrigerant.
  • the lubricating oil separated by the oil separator 120 can be continuously delivered to the compressor 110 to ensure the lubrication performance of the compressor 110, and at the same time, the circulation of the lubricating oil can be realized, the amount of lubricating oil injected can be reduced, and the cost can be saved.
  • the oil separator 120 also has an air outlet 123 for discharging the separated refrigerant.
  • the refrigerant separated by the oil separator 120 is processed by a heat exchanger such as a condenser or an evaporator, and then is sucked back to the compressor 110 through the suction port 113 or the supplemental port 111 to be compressed to realize the circulation of the refrigerant.
  • the compressor 110, the oil separator 120, and the heat exchanger are connected through a circulation pipeline, which is used to realize the circulating transmission of the refrigerant.
  • the compression oil supply device 100 of the present application connects the compressor 110 and the oil separator 120 through the first oil supply assembly 130.
  • the first oil supply assembly 130 is connected to the air supply port 111 and the first oil supply assembly 130 of the oil supply hole 122, and is configured to transmit the lubricating oil in the oil separator 120 to the compressor 110 through the air supply port 111.
  • the lubricating oil separated by the oil separator 120 flows out through the oil supply hole 122, passes through the first oil supply assembly 130, and enters the supplementary air port 111 of the compressor 110, and is mixed with the compressed refrigerant gas in the compressor 110.
  • the internal structure is lubricated. Since the lubricating oil enters the compressor 110 from the supplementary air port 111, the temperature difference between the lubricant and the refrigerant at the supplemental air port 111 is not much different. At this time, the lubricant does not heat the refrigerant, thereby reducing the specific volume of the refrigerant.
  • the compression oil supply device 100 of the present application supplies oil to the compressor 110 from the air supply port 111 of the compressor 110 to reduce the specific volume of the refrigerant and effectively solve the current refrigerant caused by the heating of the refrigerant by the lubricating oil at the suction port.
  • the problem of large suction specific volume reduces the suction temperature of the compressor 110, thereby lowering the discharge temperature, improving the reliability of the compressor 110 operation, and increasing the mass flow of the refrigerant cycle to improve the performance of the air conditioning system. .
  • the first oil supply assembly 130 includes a first oil supply line 131 and a first valve 132.
  • the first oil supply line 131 is connected to the oil supply hole 122 and the air supply port 111.
  • the first oil supply line 131 is used for transporting lubricating oil.
  • One end of the first oil supply pipe 131 extends into the oil supply hole 122 of the oil separator 120, and the other end extends into the air supply port 111 of the compressor 110 to connect the compressor 110 and the oil separator 120.
  • the lubricating oil of the oil separator 120 enters the first oil supply line 131 through the oil supply hole 122, and is delivered from the first oil supply line 131 to the compressor 110 through the air supply port 111.
  • the first valve 132 is disposed on the first oil supply line 131 and is used to control the on-off of the first oil supply line 131.
  • the first valve 132 can control whether the first oil supply line 131 can deliver lubricating oil into the compressor 110.
  • the first valve 132 is opened, and the first oil supply line 131 communicates with the oil separator 120 and the compressor 110 to establish a lubricating oil flow path.
  • the first valve 132 is closed, the lubricating oil flow path is disconnected, and the lubricating oil cannot enter the compressor 110.
  • the first valve 132 is a solenoid valve.
  • the first valve 132 may be a valve that can be switched on and off, such as a butterfly valve.
  • the first oil supply assembly 130 further includes a first throttle member 133.
  • the first throttle member 133 is disposed on the first oil supply line 131 and is used to limit the flow of the lubricant oil in the first oil supply line 131.
  • the first throttle member 133 can restrict the flow of the lubricating oil in the first oil supply line 131, so as to avoid an excessive amount of lubricating oil in the compressor 110. It is ensured that the compressor 110 runs smoothly.
  • the first throttle member 133 includes a throttle orifice plate, and the throttle orifice plate is disposed in the first oil supply pipe 131.
  • the orifice plate is arranged in a plate shape, and a plurality of oil passing holes are arranged on the orifice plate.
  • the lubricating oil in the first oil supply line 131 flows into the compressor 110 through the oil hole. This can limit the flow rate of the lubricating oil in the first oil supply line 131.
  • the first throttling member 133 includes a throttling pipe, and the diameter of the throttling pipe is 0.1 to 0.8 times the diameter of the first oil supply pipe 131. Both ends of the throttle pipe are respectively connected to the first oil supply pipe 131. That is, the throttle pipe is a small-diameter pipe, and the small-diameter pipe is used to restrict the flow of lubricating oil. In this way, the purpose of limiting the lubricating oil flow in the first oil supply line 131 can also be achieved.
  • the throttle pipe is disposed in the first oil supply pipe 131.
  • the inner wall of the throttle pipe and the outer wall of the first oil supply pipe 131 may form an annular flow passage for the lubricating oil to flow through, or the throttle pipe may be installed in the first oil supply pipe 131 in an interference manner to restrict the flow.
  • the inner hole of the tube allows the lubricant to flow through. In this way, the purpose of limiting the lubricating oil flow in the first oil supply line 131 can also be achieved.
  • the first throttle component 133 includes an electronic expansion valve, a capillary tube, or a throttle valve.
  • the first throttle member 133 includes a capillary tube
  • both ends of the capillary tube are connected to the first oil supply pipe 131 to limit the flow of the lubricating oil in the first oil supply pipe 131.
  • the throttle valve is disposed on the first fuel supply pipe 131, and the flow rate of the lubricating oil in the first fuel supply pipe 131 can be adjusted by adjusting the opening degree of the throttle valve.
  • the throttle valve may be an electronic expansion valve.
  • the first throttling member 133 may also adopt other structures that can limit the refrigerant flow rate.
  • the first throttle member 133 is a capillary.
  • the compression oil supply device 100 further includes a second oil supply assembly 140.
  • the second oil supply assembly 140 is connected to the air inlet 113 and the oil supply hole 122. That is, the first oil supply module 130 may be used to supply oil to the compressor 110, or the first oil supply module 130 and the second oil supply module 140 may be used to supply oil to the compressor 110 at the same time. It can be understood that when only the first oil supply component 130 is used to supply oil to the compressor 110, the oil supply amount of the lubricating oil can ensure the normal operation of the compressor 110. When the first oil supply assembly 130 and the second oil supply assembly 140 are used to supply oil to the compressor 110 at the same time, the oil supply amount of the lubricating oil can be increased to meet the operating requirements of the compressor 110 under special circumstances.
  • the first oil supply line 131 and The second oil supply assembly 140 supplies oil to the air-supplying port 111 and the air-intake port 113 of the compressor 110 to increase the amount of lubricating oil to ensure effective lubrication and cooling inside the compressor 110. This can ensure that the compressor 110 operates reliably.
  • the second oil supply assembly 140 stops supplying oil to the compressor 110, and at this time, only the first oil supply line 131 is used to deliver lubricant to the compressor 110. In this way, the energy consumption of the compressor 110 can be reduced, and the user's comfort during use can be improved.
  • the second fuel supply assembly 140 includes a second fuel supply line 141 and a second valve 142.
  • the second oil supply line 141 connects the oil supply hole 122 and the air inlet 113.
  • the second oil supply line 141 is used for transporting lubricating oil.
  • One end of the second oil supply pipe 141 extends into the oil supply hole 122 of the oil separator 120, and the other end extends into the suction port 113 of the compressor 110 to connect the compressor 110 and the oil separator 120.
  • the lubricating oil of the oil separator 120 enters the second oil supply line 141 through the oil supply hole 122, and is delivered from the second oil supply line 141 to the compressor 110 through the suction port 113.
  • the second valve 142 is disposed on the second oil supply line 141 and is used to control the on-off of the second oil supply line 141.
  • the second valve 142 can control whether the second oil supply line 141 can deliver lubricating oil into the compressor 110.
  • the second valve 142 is opened, and the second oil supply line 141 communicates with the oil separator 120 and the compressor 110 to establish a lubricating oil flow path.
  • the second valve 142 is closed, the lubricating oil flow path is disconnected, and the lubricating oil cannot enter the compressor 110.
  • the second valve 142 is a solenoid valve.
  • the second valve 142 may be a valve that can be switched on and off, such as a butterfly valve.
  • the second oil supply assembly 140 in order to limit the flow of lubricating oil in the second oil supply line 141, the second oil supply assembly 140 further includes a second throttle member 143.
  • the second throttling member 143 is disposed on the second oil supply line 141 and is used to limit the flow rate of the lubricating oil in the second oil supply line 141.
  • the second throttling member 143 can restrict the flow of the lubricating oil in the second oil supply line 141, so as to avoid an excessive amount of lubricating oil in the compressor 110. It is ensured that the compressor 110 runs smoothly.
  • the second throttle component 143 includes, but is not limited to, an electronic expansion valve, an orifice plate, a throttle tube, a capillary tube, or a throttle valve, etc., and may also have other structures that can restrict the flow of lubricating oil. It can be understood that the structures of the orifice plate, the throttle tube, the capillary tube, and the throttle valve are the same as those of the first throttle component 133 described above, and are not described in detail here. It can be understood that the first throttling member 133 and the second throttling member 143 may use the same throttling element, or may use different throttling elements. In this embodiment, the second throttle member 143 is a capillary.
  • the present application also provides a control method of a compression oil supply device, including the following steps:
  • the first valve 132 of the compressor 110 is opened, the second valve 142 is closed, and the oil supply port 111 of the compressor 110 returns oil;
  • the first valve 132 and the second valve 142 of the compressor 110 are opened at the same time, and the air supply port 111 and the suction port 113 of the compressor 110 return to the oil at the same time.
  • the amount of lubricant required when the compressor 110 is running is whether the compressor 110 is short of oil. Based on the amount of lubricant required during normal operation of the compressor 110.
  • the normal operation of the compressor 11 means that the compressor 110 runs for a period of time and enters a steady state after starting. If the amount of lubricant required by the compressor 110 is large, that is, the actual demand of the compressor 110 is higher than the demand of the compressor 110 during normal operation. At this time, the oil discharge rate of the compressor 110 is much higher than the oil discharge rate of the compressor 110 during normal operation, and a large amount of lubricating oil needs to be added to the compressor 110 to ensure that the compressor 110 runs smoothly.
  • the actual demand of the compressor 110 lubricating oil is compatible with the demand of the compressor 110 during normal operation. That is, the actual demand for the compressor 110's lubricating oil is not much different from the demand during the normal operation of the compressor 110, which is slightly higher or lower than the demand during the normal operation of the compressor 110. At this time, the oil discharge rate of the compressor 110 is not much different from the oil discharge rate during the normal operation of the compressor 110, and it is not necessary to add a large amount of lubricant to the compressor 110 to ensure the smooth operation of the compressor 110.
  • the first valve 132 and the second valve 142 of the compression oil supply device 100 are opened at the same time, and the compressor 110 is supplied with oil by the air supply port 111 and the air suction port 113 to ensure the reliability of the compressor 110 operation. If the actual demand for the lubricant of the compressor 110 is normal, the first valve 132 is opened and the second valve 142 is closed, and only the oil supply port 111 is used to return the oil to ensure the lubricant demand of the compressor 110. At this time, the amount of return oil of the lubricating oil can be reduced to ensure the performance of the compressor 110.
  • the operating conditions where the actual demand is higher than the compressor 110 during normal operation include at least frequency-increasing operating conditions and / or low-temperature operating conditions.
  • the frequency-increasing operating conditions include, but are not limited to, a compressor starting operation condition and / or an operating condition of an increased system load.
  • the increase in system load may refer to a case where multiple connections are enabled.
  • Low-temperature conditions refer to the conditions under which the compressor operates in a low-temperature environment. Exemplarily, operating in an environment below -7 ° C. It can be understood that the low temperature working condition will increase the viscosity of the lubricating oil, resulting in difficulty in returning the lubricating oil. Therefore, the demand for the lubricating oil needs to be increased to ensure the smooth operation of the compressor 110.
  • the operating conditions may also include other abnormal operating conditions.
  • the first oil supply pipe 131 and the second oil supply assembly 140 can be used to supply oil to the air supply port 111 and the air suction port 113 of the compressor 110 to increase the supply of lubricating oil.
  • the amount of oil This can ensure that the compressor 110 operates reliably.
  • the lubrication demand is small, that is, the actual demand for the lubricant of the compressor 110 is not much different from the demand during the normal operation of the compressor 110, and the second oil supply assembly 140 stops The compressor 110 supplies oil. At this time, only the first oil supply line 131 is used to deliver the lubricant to the compressor 110. In this way, the energy consumption of the compressor 110 can be reduced, and the user's comfort during use can be improved.
  • the present application also provides an air conditioning system including a heat exchanger and the compression oil supply device 100 in the above embodiment.
  • the heat exchanger is connected to the air outlet 123 of the oil separator 120 and is used for heat exchange treatment of the refrigerant.
  • the compressor 110 can be reliably operated, thereby ensuring the air-conditioning system to operate reliably and improving the performance of the air-conditioning system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
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  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

一种空调系统、压缩供油装置及其控制方法。压缩供油装置包括：具有补气口（111）的压缩机（110）；具有供油孔（112）的油分离器（120）；以及连接补气口（111）与供油孔（112）的第一供油组件（130），用于将油分离器（120）中的润滑油经补气口（111）输送至压缩机（110）。润滑油经压缩机（110）的补气口（111）进入压缩机（110），润滑油的温度与补气口（111）处制冷剂的温度相差不大，不存在加热制冷剂的问题。由此减小制冷剂的比容，降低压缩机的吸气温度，进而降低排气温度，提高压缩机运行的可靠性，同时还增加了制冷剂循环的质量流量，提高空调系统的性能。

Description

空调系统、压缩供油装置及其控制方法
相关申请
本申请要求2018年08月31日申请的，申请号为201811013671.6，名称为“空调系统、压缩供油装置及其控制方法”的中国专利申请的优先权，在此将其全文引入作为参考。
技术领域
本申请涉及空调设备技术领域，特别是涉及一种空调系统、压缩供油装置及其控制方法。
背景技术
随着空调热泵产品的普及和应用范围的拓宽，越来越多的补气增焓空调产品出现。对于大多数的空调产品而言，其压缩机的供油方式还是从压缩机吸气口供油。由于供给的冷冻油是高温的，被压缩机吸气口吸入的高温的冷冻油与压缩机吸入的制冷剂气体混合后，冷冻油加热制冷剂气体使制冷剂气体温度升高，导致制冷剂吸气比容增大，一方面降低了制冷剂循环的质量流量，影响空调器的性能，另一方面增加吸气温度，进而提高了排气温度，影响压缩机的性能和可靠性。
发明内容
基于此，有必要针对目前因吸气口处的润滑油加热制冷剂导致的制冷剂吸气比容大的问题，提供一种降低制冷剂吸气比容的压缩供油装置，同时还提供一种应用于上述压缩供油装置的控制方法，以及提供一种包括上述压缩供油装置的空调系统。
上述目的通过下述技术方案实现：
一种压缩供油装置，包括：
具有补气口的压缩机；
具有供油孔的油分离器；以及
连接所述补气口与所述供油孔的第一供油组件，所述第一供油组件用于将所述油分离器中的润滑油经所述补气口输送至所述压缩机。
在其中一个实施例中，所述第一供油组件包括：
连接所述供油孔与所述补气口的第一供油管路；以及
设置于所述第一供油管路的第一阀门，所述第一阀门用于控制所述第一供油管路的通断。
在其中一个实施例中，所述第一供油组件还包括第一节流部件，所述第一节流部件设置于所述第一供油管路，用于限制所述第一供油管路中润滑油的流量。
在其中一个实施例中，所述第一节流部件包括电子膨胀阀、节流孔板、毛细管或节流阀。
在其中一个实施例中，所述第一节流部件包括节流管，所述节流管的管径大小为所述第一供油管路管径大小的0.1～0.8倍；
所述节流管的两端分别与所述第一供油管路连接，或者，所述节流管设置于所述第一供油管路内。
在其中一个实施例中，所述压缩机还具有吸气口，所述压缩供油装置还包括第二供油组件，所述第二供油组件连接所述吸气口与所述供油孔。
在其中一个实施例中，所述第二供油组件包括：
连接所述供油孔与所述吸气口的第二供油管路；以及
设置于所述第二供油管路的第二阀门，用于控制所述第二供油管路的通断。
在其中一个实施例中，所述第二供油组件还包括第二节流部件，所述第二节流部件设置于所述第二供油管路，用于限制所述第二供油管路中润滑油的流量。
在其中一个实施例中，所述第二节流部件包括电子膨胀阀、节流孔板、节流管、毛细管或节流阀。
在其中一个实施例中，所述第二节流部件包括节流管，所述节流管的管径大小为所述第二供油管路的管径大小的0.1～0.8倍；
所述节流管的两端分别与所述第二供油管路连接，或者，所述节流管设置于所述第二供油管路内。
一种压缩供油装置的控制方法，应用于上述任一技术特征所述的压缩供油装置，包括如下步骤：
根据压缩机的运行工况判断所述压缩机润滑油的实际需求量；
若所述实际需求量与所述压缩机正常运行时的需求量相适应，所述压缩机的第一阀门打开，第二阀门关闭，所述压缩机的补气口回油；
若所述实际需求量高于所述压缩机正常运行时的需求量，所述压缩机的第一阀门与第二阀门同时打开，所述压缩机的补气口与吸气口同时回油。
在其中一个实施例中，所述实际需求量高于所述压缩机正常运行时需求量的运行工况 至少包括升频运行工况和/或低温工况。
一种空调系统，包括换热器及如上述任一技术特征所述的压缩供油装置；
所述换热器与所述油分离器的出气口连接，用于对制冷剂进行换热处理。
采用上述技术方案后，本申请至少具有如下技术效果：
本申请的空调系统、压缩供油装置及其控制方法，第一供油组件将油分离器的润滑油经补气口送入压缩机，以满足压缩机运行时的润滑需求。而且，润滑油经压缩机的补气口进入压缩机，润滑油的温度与补气口处制冷剂的温度相差不大，不存在加热制冷剂的问题。有效的解决目前因吸气口处的润滑油加热制冷剂导致的制冷剂吸气比容大的问题。这样可以减小制冷剂的比容，降低压缩机的吸气温度，进而降低排气温度，提高压缩机运行的可靠性，同时还增加了制冷剂循环的质量流量，以提高空调系统的性能。
附图说明
图1为本申请一实施例中的压缩供油装置的示意图。
其中：
100-压缩供油装置；
110-压缩机；
111-补气口；
112-排气口；
113-吸气口；
120-油分离器；
121-进气口；
122-供油孔；
123-出气口；
130-第一供油组件；
131-第一供油管路；
132-第一阀门；
133-第一节流部件；
140-第二供油组件；
141-第二供油管路；
142-第二阀门；
143-第二节流部件。
具体实施方式
为了使本申请的目的、技术方案及优点更加清楚明白，以下通过实施例，并结合附图，对本申请的空调系统、压缩供油装置及其控制方法进行进一步详细说明。应当理解，此处所描述的具体实施例仅用以解释本申请，并不用于限定本申请。
本文中为部件所编序号本身，例如“第一”、“第二”等，仅用于区分所描述的对象，不具有任何顺序或技术含义。而本申请所说“连接”、“联接”，如无特别说明，均包括直接和间接连接(联接)。在本申请的描述中，需要理解的是，术语“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请的限制。
在本申请中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
参见图1，本申请提供一种压缩供油装置100。该压缩供油装置100应用于空调系统中，实现压缩机110的供油。本申请的压缩供油装置100可以减小制冷剂的比容，提高压缩机110的性能和运行可靠性，并提高空调系统的性能。
在一实施例中，压缩供油装置100包括压缩机110、油分离器120及第一供油组件130。压缩机110具有补气口111与排气口112。压缩机110用于压缩制冷剂气体。压缩机110还具有吸气口113。制冷剂从吸气口113吸入压缩机110后进行压缩，并从排气口112排出。压缩机110还通过补气口111补入制冷剂，以保证压缩机110的性能。
油分离器120具有进气口121和供油孔122。压缩机110的排气口112与油分离器120的进气口121连通。压缩机110压缩制冷剂时，制冷剂会与润滑油混合在一起，经压缩机110的排气口112输送至油分离器120中。油分离器120用于分离润滑油与制冷剂。油分离器120分离出来的润滑油可继续输送至压缩机110内，保证压缩机110的润滑性能，同时还能实现润滑油的循环流动，减少润滑油的注入量，节省成本。油分离器120还具有出气口123，用于排出分离后的制冷剂。油分离器120分离出来的制冷剂则经换热器如冷凝器、蒸发器处理后，再由吸气口113或补气口111吸回压缩机110进行压缩，实现制冷剂 的循环流动。
可以理解的，压缩机110、油分离器120及换热器之间通过流通管路连接，用于实现制冷剂的循环输送。并且，本申请的压缩供油装置100通过第一供油组件130连接压缩机110与油分离器120。具体的，第一供油组件130连接补气口111与供油孔122的第一供油组件130，用于将油分离器120中的润滑油经补气口111输送至压缩机110。
油分离器120分离出来的润滑油经供油孔122流出，经过第一供油组件130进入到压缩机110的补气口111，与压缩机110内被压缩的制冷剂气体混合，对压缩机110的内部结构进行润滑。由于润滑油从补气口111进入压缩机110，其与补气口111处制冷剂的温差相差不大。此时，润滑油不会对制冷剂进行加热，进而降低制冷剂的比容。
本申请的压缩供油装置100从压缩机110的补气口111向压缩机110供油，以降低制冷剂的比容，有效的解决目前因吸气口处的润滑油加热制冷剂导致的制冷剂吸气比容大的问题，进而降低压缩机110的吸气温度，进而降低排气温度，提高压缩机110运行的可靠性，同时还增加了制冷剂循环的质量流量，以提高空调系统的性能。
在一实施例中，第一供油组件130包括第一供油管路131以及第一阀门132。第一供油管路131连接供油孔122与补气口111。第一供油管路131用于输送润滑油。第一供油管路131的一端伸入油分离器120的供油孔122，另一端伸入压缩机110的补气口111，以连接压缩机110与油分离器120。油分离器120的润滑油经供油孔122进入第一供油管路131，并由第一供油管路131经补气口111输送至压缩机110内。
第一阀门132设置于第一供油管路131，用于控制第一供油管路131的通断。第一阀门132可以控制第一供油管路131是否可以向压缩机110内输送润滑油。压缩机110运行时，第一阀门132打开，第一供油管路131连通油分离器120与压缩机110，建立润滑油流路。压缩机110停止运行时，第一阀门132关断，润滑油流路断开，润滑油无法进入压缩机110。示例的，第一阀门132为电磁阀。当然，在本申请的其他实施方式中，第一阀门132也可为蝶阀等可实现通断的阀门。
在一实施例中，为了限制第一供油管路131中润滑油的流量，第一供油组件130还包括第一节流部件133。第一节流部件133设置于第一供油管路131，用于限制第一供油管路131中润滑油的流量。润滑油经第一供油管路131向压缩机110输送时，第一节流部件133可以限制第一供油管路131的润滑油流量，避免压缩机110内出现润滑油量过剩的情况，保证压缩机110平稳运行。
可选的，第一节流部件133包括节流孔板，节流孔板设置于第一供油管路131内。节流孔板呈板状设置，其上设置多个过油孔。第一供油管路131内的润滑油经过油孔流动至 压缩机110内。这样可以限制第一供油管路131中润滑油的流量。
可选的，第一节流部件133包括节流管，节流管的管径大小为第一供油管路131的管径大小的0.1～0.8倍。节流管的两端分别与第一供油管路131连接。也就是说，节流管为小管径的管路，采用小管径的管路限制润滑油的流动。这样也可以达到限制第一供油管路131中润滑油流量的目的。
当然，节流管设置于第一供油管路131内。可以理解的，可以节流管的内壁与第一供油管路131的外壁形成环形流道供润滑油流过，也可以节流管过盈安装于第一供油管路131内，节流管的内孔供润滑油流过。这样也可以达到限制第一供油管路131中润滑油流量的目的。
可选的，第一节流部件133包括电子膨胀阀、毛细管或节流阀。当第一节流部件133包括毛细管时，毛细管的两端与第一供油管路131连接，以限制第一供油管路131中润滑油的流量。当第一节流部件133包括节流阀时，节流阀设置于第一供油管路131上，通过调节节流阀的开度可以调节第一供油管路131中润滑油的流量。示例的，节流阀可以为电子膨胀阀。当然，在本申请的其他实施方式中，第一节流部件133还可采用其他可以限制制冷剂流量的结构。本实施例中，第一节流部件133为毛细管。
在一实施例中，压缩供油装置100还包括第二供油组件140，第二供油组件140连接吸气口113与供油孔122。也就是说，可以采用第一供油组件130向压缩机110供油，也可以采用第一供油组件130与第二供油组件140同时向压缩机110供油。可以理解的，只采用第一供油组件130向压缩机110供油时，润滑油的供油量可以保证压缩机110的正常运行。当采用第一供油组件130与第二供油组件140同时向压缩机110供油时，可以提高润滑油的供油量，以满足压缩机110特殊情况下的运行需求。
当压缩机110润滑油需求量较大时，例如，压缩机110刚启动升频速度较快时，低温环境下润滑油粘度大回油困难等时间段，可以采用第一供油管路131与第二供油组件140分别向压缩机110的补气口111与吸气口113供油，提高润滑油的供油量，保证压缩机110内部的有效润滑与冷却。这样可以保证压缩机110可靠运行。
当压缩机110润滑需求量较小时，第二供油组件140停止向压缩机110供油，此时只采用第一供油管路131向压缩机110内输送润滑油。这样可以降低压缩机110的能耗，提高用户使用时的舒适度。
在一实施例中，第二供油组件140包括第二供油管路141以及第二阀门142。第二供油管路141连接供油孔122与吸气口113。第二供油管路141用于输送润滑油。第二供油管路141的一端伸入油分离器120的供油孔122，另一端伸入压缩机110的吸气口113，以 连接压缩机110与油分离器120。油分离器120的润滑油经供油孔122进入第二供油管路141，并由第二供油管路141经吸气口113输送至压缩机110内。
第二阀门142设置于第二供油管路141，用于控制第二供油管路141的通断。第二阀门142可以控制第二供油管路141是否可以向压缩机110内输送润滑油。压缩机110运行时，第二阀门142打开，第二供油管路141连通油分离器120与压缩机110，建立润滑油流路。压缩机110停止运行时，第二阀门142关断，润滑油流路断开，润滑油无法进入压缩机110。示例的，第二阀门142为电磁阀。当然，在本申请的其他实施方式中，第二阀门142也可为蝶阀等可实现通断的阀门。
在一实施例中，为了限制第二供油管路141中润滑油的流量，第二供油组件140还包括第二节流部件143。第二节流部件143设置于第二供油管路141，用于限制第二供油管路141中润滑油的流量。润滑油经第二供油管路141向压缩机110输送时，第二节流部件143可以限制第二供油管路141的润滑油流量，避免压缩机110内出现润滑油量过剩的情况，保证压缩机110平稳运行。
在一实施例中，第二节流部件143包括但不限于电子膨胀阀、节流孔板、节流管、毛细管或节流阀等，还可为其他可限制润滑油流量的结构。可以理解的，节流孔板、节流管、毛细管、节流阀的结构与上述第一节流部件133的结构相同，在此不一一赘述。可以理解的，第一节流部件133与第二节流部件143可以采用相同的节流元件，也可采用不同的节流元件。本实施例中，第二节流部件143为毛细管。
本申请还提供一种压缩供油装置的控制方法，包括如下步骤：
根据压缩机110的运行工况判断压缩机110润滑油的实际需求量；
若实际需求量与压缩机110正常运行时的需求量相适应，压缩机110的第一阀门132打开，第二阀门142关闭，压缩机110的补气口111回油；
若实际需求量高于压缩机110正常运行时的需求量，压缩机110的第一阀门132与第二阀门142同时打开，压缩机110的补气口111与吸气口113同时回油。
可以理解的，压缩机110运行时润滑油的需求量大小即为压缩机110是否缺油。以压缩机110正常运行时的润滑油需求量为基准。压缩机11正常运行是指压缩机110启动后运行一段时间并进入平稳状态。若压缩机110润滑油需求量较大时，即压缩机110的实际需求量高于压缩机110正常运行时的需求量。此时，压缩机110的排油率远高于压缩机110正常运行时的排油率，需要向压缩机110内补充大量的润滑油，以保证压缩机110平稳运行。若压缩机润滑油需求量正常，即压缩机110润滑油的实际需求量与压缩机110正常运行时的需求量相适应。也就是说，压缩机110润滑油的实际需求量与压缩机110正常运行 时的需求量相差不大，略高于或略低于压缩机110正常运行时的需求量。此时，压缩机110的排油率与压缩机110正常运行时的排油率相差不大，无需向压缩机110内补充大量的润滑油，即可保证压缩机110平稳运行。
因此，当压缩机110的润滑油实际需求量较高，高于压缩机110正常运行时的需求量时。压缩供油装置100的第一阀门132与第二阀门142同时打开，采用补气口111与吸气口113同时向压缩机110供油，以保证压缩机110运行的可靠性。若压缩机110润滑油的实际需求量正常时，第一阀门132打开，第二阀门142关闭，仅采用补气口111回油，即可保证压缩机110的润滑油需求量。此时，可以减少润滑油的回油量，保证压缩机110的性能。
在一实施例中，实际需求量高于压缩机110正常运行时需求量的运行工况至少包括升频运行工况和/或低温工况。示例的，升频运行工况包括但不限于压缩机启动运行的情况和/或系统负荷增加的工况等。其中，系统负荷增加可以指开启多联机的情况等。低温工况指压缩机在低温环境运行的情况。示例的，在低于-7℃环境中运行。可以理解的，低温工况会增加润滑油的粘稠度，导致润滑油回油困难，因此需要增加润滑油的需求量，以保证压缩机110运行平稳。当然，运行工况还可包括其他非正常工况。
当压缩机110润滑油需求量较大时，即压缩机110润滑油的实际需求量高于压缩机110正常运行时的需求量，例如，压缩机110刚启动升频速度较快时，低温环境下润滑油粘度大回油困难等时间段，可以采用第一供油管路131与第二供油组件140分别向压缩机110的补气口111与吸气口113供油，提高润滑油的供油量。这样可以保证压缩机110可靠运行。
当压缩机110在正常工况下运行时，润滑需求量较小，即压缩机110润滑油的实际需求量与压缩机110正常运行时的需求量相差不大，第二供油组件140停止向压缩机110供油，此时只采用第一供油管路131向压缩机110内输送润滑油。这样可以降低压缩机110的能耗，提高用户使用时的舒适度。
本申请还提供一种空调系统，包括换热器及上述实施例中的压缩供油装置100。换热器与油分离器120的出气口123连接，用于对制冷剂进行换热处理。本申请的空调系统采用上述的压缩供油装置100后，可以保证压缩机110可靠运行，进而保证空调系统可靠运行，提高空调系统的性能。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书的记载范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对本申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。

Claims (13)

  1. 一种压缩供油装置，其特征在于，包括：
    具有补气口(111)的压缩机(110)；
    具有供油孔(122)的油分离器(120)；以及
    连接所述补气口(111)与所述供油孔(122)的第一供油组件(130)，所述第一供油组件(130)用于将所述油分离器(120)中的润滑油经所述补气口(111)输送至所述压缩机(110)。
  2. 根据权利要求1所述的压缩供油装置，其特征在于，所述第一供油组件(130)包括：
    连接所述供油孔(122)与所述补气口(111)的第一供油管路(131)；以及
    设置于所述第一供油管路(131)的第一阀门(132)，所述第一阀门(132)用于控制所述第一供油管路(131)的通断。
  3. 根据权利要求2所述的压缩供油装置，其特征在于，所述第一供油组件(130)还包括第一节流部件(133)，所述第一节流部件(133)设置于所述第一供油管路(131)，用于限制所述第一供油管路(131)中润滑油的流量。
  4. 根据权利要求3所述的压缩供油装置，其特征在于，所述第一节流部件(133)包括电子膨胀阀、节流孔板、毛细管或节流阀。
  5. 根据权利要求3所述的压缩供油装置，其特征在于，所述第一节流部件(133)包括节流管，所述节流管的管径大小为所述第一供油管路(131)的管径大小的0.1～0.8倍；
    所述节流管的两端分别与所述第一供油管路(131)连接，或者，所述节流管设置于所述第一供油管路(131)内。
  6. 根据权利要求1至5任一项所述的压缩供油装置，其特征在于，所述压缩机(110)还具有吸气口(113)，所述压缩供油装置还包括第二供油组件(140)，所述第二供油组件(140)连接所述吸气口(113)与所述供油孔(122)。
  7. 根据权利要求6所述的压缩供油装置，其特征在于，所述第二供油组件(140)包括：
    连接所述供油孔(122)与所述吸气口(113)的第二供油管路(141)；以及
    设置于所述第二供油管路(141)的第二阀门(142)，所述第二阀门(142)用于控制所述第二供油管路(141)的通断。
  8. 根据权利要求7所述的压缩供油装置，其特征在于，所述第二供油组件(140)还包括第二节流部件(143)，所述第二节流部件(143)设置于所述第二供油管路(141)，用于限制所述第二供油管路(141)中润滑油的流量。
  9. 根据权利要求8所述的压缩供油装置，其特征在于，所述第二节流部件(143)包括电子膨胀阀、节流孔板、节流管、毛细管或节流阀。
  10. 根据权利要求8所述的压缩供油装置，其特征在于，所述第二节流部件(143)包括节流管，所述节流管的管径大小为所述第二供油管路(141)的管径大小的0.1～0.8倍；
    所述节流管的两端分别与所述第二供油管路(141)连接，或者，所述节流管设置于所述第二供油管路(141)内。
  11. 一种压缩供油装置的控制方法，其特征在于，应用于如权利要求1至10任一项所述的压缩供油装置，包括如下步骤：
    根据压缩机(110)的运行工况判断所述压缩机(110)润滑油的实际需求量；
    若所述实际需求量与所述压缩机(110)正常运行时的需求量相适应，所述压缩机(110)的第一阀门(132)打开，第二阀门(142)关闭，所述压缩机(110)的补气口(111)回油；
    若所述实际需求量高于所述压缩机(110)正常运行时的需求量，所述压缩机(110)的第一阀门(132)与第二阀门(142)同时打开，所述压缩机(110)的补气口(111)与吸气口(113)同时回油。
  12. 根据权利要求11所述的压缩供油装置的控制方法，其特征在于，所述实际需求量高于所述压缩机(110)正常运行时需求量的运行工况至少包括升频运行工况和/或低温工况。
  13. 一种空调系统，其特征在于，包括换热器及如权利要求1至10任一项所述的压缩供油装置(100)；
    所述换热器与所述油分离器(120)的出气口(123)连接，用于对制冷剂进行换热处理。
PCT/CN2018/122223 2018-08-31 2018-12-20 空调系统、压缩供油装置及其控制方法 Ceased WO2020042457A1 (zh)

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