Compressor oil supply system and heat pump unit

Abstract

The utility model discloses a compressor oil supply system and heat pump unit, compressor oil supply system includes: the high oil tank of oil supply to compressor, and the main oil tank of receiving the lubricating oil of compressor outflow, and the main oil tank is connected high oil tank through oil pump to form the oil supply circuit, and the main oil tank is connected evaporator and condenser to form the oil return branch of injection, the control valve of independent work is installed respectively to oil supply circuit and injection oil return branch, and the main oil tank is equipped with the first liquid level sensor for detecting oil quantity, and the control valve is electrically connected with the first liquid level sensor, the utility model discloses through real -time monitoring oil quantity dynamic control oil supply circuit and injection oil return branch's working condition, can avoid the additional energy consumption of the oil return of sustained injection, guarantee system energy efficiency, can eliminate the oil pressure difference shortage problem caused by oil return delay, and avoid the risk of fault shutdown.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to compressor oil supply systems and heat pump units. Background Technology

[0002] In large-scale air conditioning equipment and high-temperature heat pump systems, the lubrication system of centrifugal compressors is crucial for maintaining refrigeration efficiency and long-term stable operation. Lubricating oil not only performs the core functions of lubricating the moving parts inside the compressor and reducing mechanical friction, but also provides critical cooling for the motor and bearings through its circulation, preventing material fatigue and performance degradation caused by overheating during operation. To ensure that the lubricating oil is always in optimal working condition, current mainstream designs employ a closed-loop temperature control scheme: after being pressurized and output from the oil tank by the oil pump, the lubricating oil first flows through a plate heat exchanger to exchange heat with the refrigerant for precise cooling, then is transported to a high-level oil tank for storage, and finally distributed to critical components such as the motor and bearings. This process, through strict control of oil temperature and flow rate, significantly improves the compressor's operating efficiency and service life.

[0003] However, in large-capacity, high-temperature heat pump centrifugal chillers, the stability of the lubrication system faces even more severe challenges. Besides temperature control, lubrication leakage poses a significant threat to the unit's performance, reliability, and safety. Due to aging of the sealing structure or fluctuations in operating conditions, lubricating oil can easily leak from the oil supply system into the refrigeration cycle, mixing with the refrigerant to form an oil-refrigerant mixture. This leakage not only disrupts the working fluid balance within the system but can also lead to compressor instability or even unexpected shutdown. More seriously, continuous leakage will cause oil pressure fluctuations and insufficient oil pressure differential, resulting in a sharp reduction in the amount of lubricating oil delivered to the compressor bearings. When lubrication and cooling requirements cannot be met, problems such as accelerated bearing wear and abnormal component wear arise, ultimately threatening the overall safety of the equipment.

[0004] To address leakage issues, traditional solutions typically involve continuously operating the ejector oil return device to force oil return. However, this strategy has two drawbacks: firstly, the continuous operation of the ejector oil return consumes additional energy, reducing the overall energy efficiency of the unit; secondly, the ejector oil return has a response lag, failing to compensate for oil loss immediately after a leak occurs. Even when the oil pressure differential drops below the safety threshold, the unit will still trigger a protective shutdown. Furthermore, existing systems lack real-time monitoring capabilities for oil volume in the supply circuit, making it difficult to detect oil imbalances caused by leaks in a timely manner. Fluctuations in oil supply and increased oil temperature may further lead to overheating of the motor bearings, causing irreversible damage to the unit.

[0005] Therefore, how to improve the oil supply accuracy and stability of the compressor oil supply system is a technical problem that the industry urgently needs to address. Utility Model Content

[0006] To overcome the problem of insufficient oil supply stability in existing technologies, this utility model provides a compressor oil supply system and a heat pump unit. The system adds a liquid level sensor to the main oil tank, dynamically adjusting the working status of the oil supply circuit and the ejector oil return branch by real-time monitoring of the oil quantity. This avoids the additional energy consumption caused by continuous ejector oil return, ensuring system energy efficiency, and eliminates the problem of insufficient oil pressure difference caused by delayed oil return, thus mitigating the risk of downtime due to malfunction.

[0007] The technical solution adopted in this utility model is to design a compressor oil supply system, including: a high-level oil tank that supplies oil to the compressor, and a main oil tank that receives the lubricating oil flowing out of the compressor. The main oil tank is connected to the high-level oil tank through an oil pump to form an oil supply circuit. The main oil tank is connected to the evaporator and the condenser to form an ejector return oil branch. The oil supply circuit and the ejector return oil branch are each equipped with an independently operating control valve. The main oil tank is equipped with a first liquid level sensor for detecting the oil quantity. The control valve is electrically connected to the first liquid level sensor.

[0008] Furthermore, the compressor's oil return chamber is connected to the main oil tank, and the compressor's oil return chamber is equipped with at least one second liquid level sensor for detecting the oil level. The control valve is electrically connected to the second liquid level sensor.

[0009] In some embodiments of this utility model, the ejector return oil branch is connected to the main oil tank via the front vane cavity of the compressor.

[0010] Furthermore, the ejector return oil branch includes: an oil inlet ejector pipe connected between the evaporator and the condenser, an oil inlet branch pipe connected between the compressor's front vane cavity and the evaporator, an oil outlet ejector pipe connected between the compressor's front vane cavity and the condenser, and an oil outlet branch pipe connected between the compressor's front vane cavity and the main oil tank; wherein, the oil inlet ejector pipe and the oil outlet ejector pipe are equipped with valves to prevent fluid from entering the condenser.

[0011] Furthermore, the oil inlet branch pipe is connected to the upper part of the evaporator, and the oil outlet branch pipe is connected to the lower part of the front vane cavity of the compressor.

[0012] Furthermore, the compressor's oil return chamber is connected to the main oil tank via an oil return pipe, which is located at the bottom of the compressor's oil return chamber.

[0013] Furthermore, a temperature sensor is installed on the return oil pipe.

[0014] Furthermore, the main oil tank is connected to the high-level oil tank via an oil supply pipe, and the oil supply pipe is equipped with an oil temperature heat exchanger for regulating the oil temperature.

[0015] This utility model also proposes a heat pump unit, including the aforementioned compressor oil supply system.

[0016] In some embodiments of this utility model, the compressor is a centrifugal compressor.

[0017] Compared with the prior art, the present invention has at least one of the following technical effects:

[0018] 1. A first liquid level sensor is added to the main oil tank. By monitoring the oil quantity in real time, the working status of the oil supply circuit and the ejector return oil branch is dynamically adjusted to achieve dual optimization goals: first, to avoid the extra energy consumption caused by continuous ejector return oil and ensure system energy efficiency; second, to eliminate the problem of insufficient oil pressure difference caused by return oil delay and avoid the risk of failure and downtime.

[0019] 2. A second liquid level sensor is added to the oil return chamber of the compressor. By monitoring the oil volume in the chamber in real time, the oil supply status can be accurately determined, which strengthens the fine monitoring of the total oil volume of the system and improves the stability of the compressor oil supply system control.

[0020] 3. The ejector return oil branch connects to the main oil tank through the compressor's front vane cavity. The ejector lubricating oil is directly supplied to the front vane cavity, and the lubricating oil directly covers key moving parts such as the impeller front bearing, eliminating lubrication delay and reducing friction loss. The lubricating oil deposited at the bottom of the front vane cavity is ejected back to the main oil tank through the same branch, maintaining the dynamic balance of oil quantity. This design can not only improve the compressor's lubrication efficiency and optimize the compressor's operating state, but also supply oil back to the main oil tank to replenish the oil quantity in the main oil tank. Attached Figure Description

[0021] The present invention will now be described in detail with reference to the embodiments and accompanying drawings, wherein:

[0022] Figure 1 This is a connection diagram of the compressor oil supply system of this utility model;

[0023] Figure 2 This is a schematic diagram of the flow direction of the oil supply circuit when the present invention is working;

[0024] Figure 3 This is a schematic diagram of the flow direction of the ejector return oil branch when it is working.

[0025] Figure 4 This is a schematic diagram of the flow direction when both the oil supply circuit and the ejector return branch of this utility model are working;

[0026] Figure 5 This is a schematic diagram of the liquid level control process according to an embodiment of the present invention;

[0027] Figure 6 This is a schematic diagram of the liquid level control process according to another embodiment of the present invention;

[0028] Figure 7 This is a schematic diagram of the liquid level control process in another embodiment of the present invention; Attached image description:

[0030] 1. Compressor; 101. Oil return chamber; 102. Front vane chamber; 2. Evaporator; 3. Condenser; 4. Main oil tank; 5. High-level oil tank; 6. Oil pump; 7. First liquid level sensor; 8. Second liquid level sensor; 9. Oil return pipe; 10. Oil supply pipe; 11. First oil supply valve; 12. Second oil supply valve; 13. First ejector oil return valve; 14. Second ejector oil return valve; 15. Oil inlet ejector pipe; 16. Oil inlet branch pipe; 17. Oil outlet ejector pipe; 18. Oil outlet branch pipe; 19. Temperature sensor; 20. Oil temperature heat exchanger. Detailed Implementation

[0031] To make the technical problem to be solved, the technical solution, and the beneficial effects of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this utility model and are not intended to limit this utility model.

[0032] like Figures 1 to 4 As shown, the compressor oil supply system proposed in this utility model is applicable to heat pump units, especially heat pump units using centrifugal compressors. Specifically, the compressor oil supply system includes: a high-level oil tank 5 that supplies oil to the compressor 1, and a main oil tank 4 that receives the lubricating oil flowing out of the compressor 1. The main oil tank 4 is connected to the high-level oil tank 5 through an oil pump 6 to form an oil supply circuit. The main oil tank 4 is connected to the evaporator 2 and the condenser 3 to form an ejector return oil branch. The oil supply circuit and the ejector return oil branch are each equipped with an independently operating control valve. The main oil tank 4 is equipped with a first liquid level sensor 7 for detecting the oil level.

[0033] For ease of distinction, the control valve of the oil supply circuit is called the oil supply valve, and the control valve of the ejector return branch is called the ejector return valve. The oil supply valve and the ejector return valve are electrically connected to the first liquid level sensor 7, and the output terminal of the first liquid level sensor 7 is directly or indirectly connected to the drive terminals of the oil supply valve and the ejector return valve to form an electrical signal path.

[0034] For example, such as Figure 4 As shown, in some feasible embodiments of this utility model, the first liquid level sensor 7 monitors the liquid level of the main oil tank 4 as D, and the normal range is D≥D1, where D1 is the set oil level.

[0035] When D≥D1, it indicates that the oil level in the main oil tank 4 is normal and the ejector return valve is closed.

[0036] When D < D1, it indicates that the oil level in the main oil tank 4 is insufficient, the ejector return valve opens, and the ejector return branch returns oil to the main oil tank 4.

[0037] This design adds a first liquid level sensor 7 inside the main oil tank 4. By monitoring the oil quantity in real time, it dynamically adjusts the working status of the oil supply circuit and the ejector return oil branch, thereby achieving a dual optimization goal: first, to avoid the extra energy consumption caused by continuous ejector return oil and ensure system energy efficiency; second, to eliminate the problem of insufficient oil pressure difference caused by return oil delay and avoid the risk of failure and shutdown.

[0038] The oil return chamber 101 of the compressor 1 is connected to the main oil tank 4. The oil return chamber 101 of the compressor 1 is provided with at least one second liquid level sensor 8 for detecting the oil quantity. The oil supply valve and the ejector oil return valve are electrically connected to the second liquid level sensor 8 respectively. The output end of the second liquid level sensor 8 is directly or indirectly connected to the drive terminals of the oil supply valve and the ejector oil return valve to form an electrical signal path.

[0039] In practical applications, the first liquid level sensor 7, the second liquid level sensor 8, the oil supply valve, and the ejector return valve are all electrically connected to the controller. The controller receives the detection signals from the first liquid level sensor 7 and the second liquid level sensor 8, and outputs drive signals to the oil supply valve and the ejector return valve, thereby adjusting the opening degree of the oil supply valve and the ejector return valve.

[0040] For example, such as Figure 6 As shown, in some feasible embodiments of this utility model, the first liquid level sensor 7 monitors the liquid level of the main oil tank 4 as D, the normal range is D≥D1, D1 is the first set oil level, and the second liquid level sensor 8 monitors the liquid level of the return oil chamber 101 as Dy, the normal range is Dy≥Dy1, Dy1 is the second set oil level.

[0041] When D≥D1, it indicates that the oil level in the main oil tank 4 is normal, the ejector return valve is closed, and the oil level in the main oil tank 4 is monitored again.

[0042] When D < D1, it indicates that the oil level in the main oil tank 4 is insufficient. The ejector return valve opens, and the ejector return branch returns oil to the main oil tank 4. The oil supply situation is judged according to the value of Dy. When Dy < Dy1, it indicates that the oil level in the return chamber of compressor 1 is insufficient. The ejector return valve opens wider, and the flow rate of lubricating oil ejected to the main oil tank 4 increases. The oil supply valve opens wider, and the flow rate of lubricating oil supplied to the high-level oil tank 5 increases. When Dy < Dy1, it indicates that the oil level in the return chamber 101 of compressor 1 is normal. The monitoring of the oil level in the main oil tank 4 continues.

[0043] For example, such as Figure 7 As shown, in some other feasible embodiments of this utility model, the first liquid level sensor 7 monitors the liquid level of the main oil tank 4 as D, the normal range is D≥D1, D1 is the first set oil level, the second liquid level sensor 8 monitors the liquid level of the return oil chamber 101 as Dy, the set liquid level drop rate is Vx1, and the set liquid level rise rate is Vs1.

[0044] When D≥D1, it indicates that the oil level in the main oil tank 4 is normal. The change in the value of Dy indicates whether the oil level has risen or fallen.

[0045] If the liquid level drops, calculate the rate of drop Vx. If Vx ≥ Vx1, it indicates that compressor 1 is leaking oil into the refrigeration cycle and the leakage is significant. The ejector return valve opens wide, and the ejector return branch returns oil to the main oil tank 4. If Vx < Vx1, it indicates that the oil return is normal, and the opening of the oil supply valve and the ejector return valve remains unchanged.

[0046] If the liquid level rises, it indicates that the oil return is normal and the opening of the oil supply valve and the ejector return valve remains unchanged.

[0047] When D < D1, it indicates that the oil level in the main oil tank 4 is insufficient. The change in the value of Dy indicates whether the oil level is rising or falling.

[0048] If the liquid level rises, calculate the rate of rise and fall of the liquid level Vs. When Vs≥Vs1, it indicates that the oil return is normal and the opening of the oil supply valve and the ejector oil return valve remains unchanged. When Vs<Vs1, it indicates that the compressor 1 is leaking oil into the refrigeration cycle, the oil return is slow, the ejector oil return valve opens wider, and the oil return volume of the ejector oil return branch increases.

[0049] If the liquid level drops, calculate the rate of drop Vx. If Vx ≥ Vx1, it indicates that compressor 1 is leaking oil into the refrigeration cycle and the leakage is relatively fast. The ejector return valve opens wider, and the return oil volume of the ejector return branch increases. If Vx < Vx1, it indicates that the oil supply system is fluctuating normally. The oil supply valve opens wider, and the flow rate of lubricating oil supplied to the high-level oil tank 5 increases.

[0050] This design adds a second level sensor 8 to the oil return chamber 101 of the compressor. By monitoring the oil level in the chamber in real time, it accurately determines the oil supply status and enhances the precise monitoring of the total oil volume of the system. Based on the dual level monitoring of the main oil tank 4 and the oil return chamber 101, the first level sensor 7 and the second level sensor 8 monitor the oil levels in the main oil tank 4 and the oil return chamber 101 in real time, dynamically controlling the start and stop of the ejector oil return branch to reduce ineffective energy consumption, and synchronously adjusting the opening of the oil supply valve to achieve precise flow matching. This design significantly improves the control accuracy and operational stability of the oil supply system and eliminates the risk of downtime caused by oil supply fluctuations.

[0051] like Figure 1 , 3As shown, in a preferred embodiment of this invention, the ejector return oil branch is connected to the main oil tank 4 via the front vane cavity 102 of the compressor 1. The front vane cavity 102 of the compressor 1 is a transition cavity located before the impeller inlet. Lubricating oil is directly supplied to the front vane cavity 102 of the compressor 1 via the ejector return oil branch. The lubricating oil directly covers key moving parts such as the impeller front bearing, eliminating lubrication delay and reducing friction loss. The lubricating oil deposited at the bottom of the front vane cavity 102 is ejected back to the main oil tank 4 via the same branch, maintaining a dynamic balance of oil volume. This design not only improves the lubrication efficiency of the compressor 1 and optimizes its operating state, but also provides return oil to the main oil tank 4, replenishing its oil volume.

[0052] Based on the above embodiment, the ejector oil return branch includes an oil inlet ejector pipe 15, an oil inlet branch pipe 16, an oil outlet ejector pipe 17, and an oil outlet branch pipe 18. The oil inlet ejector pipe 15 is connected between the evaporator 2 and the condenser 3. The oil inlet branch pipe 16 is connected between the front vane cavity 102 of the compressor 1 and the evaporator 2. The oil outlet ejector pipe 17 is connected between the front vane cavity 102 of the compressor 1 and the condenser 3. The oil outlet branch pipe 18 is connected between the front vane cavity 102 of the compressor 1 and the main oil tank 4. The oil inlet branch pipe 16 is equipped with a first ejector oil return valve 13 to control the flow rate of the oil and refrigerant mixture ejected from the evaporator 2. The oil outlet branch pipe 18 is equipped with a second ejector oil return valve 14 to control the return oil flow rate from the front vane cavity 102. The operation of the ejector oil return valves mentioned above is executed by the first ejector oil return valve 13 and the second ejector oil return valve 14. To prevent lubricating oil from entering the condenser, the oil inlet ejector pipe 15 and the oil outlet ejector pipe 17 are equipped with valves to prevent fluid from entering the condenser 3. The valves can be check valves or the like.

[0053] The oil return branch is driven by pressure difference to achieve automatic circulation and recovery of lubricating oil. Its core working principle is to use the inherent pressure difference of the system as a power source: First, the oil inlet ejector pipe uses the high pressure difference between the condenser 3 and the evaporator 2 to efficiently draw out the oil-refrigerant mixture from the upper layer of the evaporator 2. The check valve equipped in this pipeline ensures unidirectional fluid flow and completely blocks the risk of backflow of the mixture contaminating the condenser 3. Then, the mixture is transported to the front vane cavity 102 of the compressor 1 through the oil inlet branch pipe 16, where gas-liquid separation is completed. The liquid oil directly lubricates and cools key components such as the impeller bearing, while the gaseous refrigerant returns to the main circulation. Next, the oil outlet ejector pipe 17 uses the secondary pressure difference between the condenser 3 and the front vane cavity 102 to extract the waste oil deposited at the bottom of the cavity. This pipeline is also equipped with a check valve, forming a double insurance against lubricating oil entering the condenser. Finally, the recovered lubricating oil returns to the main oil tank 4 through the oil outlet branch pipe 18, forming a complete closed-loop oil circuit.

[0054] This design achieves three core advantages through the precise coordination of multiple pipelines and the protection of valve components: First, by replacing the traditional mechanical pump with pressure differential drive, the system energy efficiency is greatly improved while achieving zero additional energy consumption; Second, the direct lubrication and immediate recovery of lubricating oil in the front vane cavity 102 significantly improves cooling efficiency and eliminates the problem of fluidity reduction caused by oil accumulation; Third, the double check valve design on the oil inlet ejector pipe 15 and the oil outlet ejector pipe 17 constitutes a reliable hard-seal isolation barrier, fundamentally eliminating the possibility of lubricating oil contaminating the condenser and ensuring the stability and reliability of the system's long-term operation.

[0055] like Figure 1 , 3 As shown, based on this, the preferred solution is that the oil inlet branch pipe 16 is connected to the upper part of the evaporator 2, and the oil outlet branch pipe 18 is connected to the lower part of the front vane cavity 102 of the compressor 1. This design can efficiently extract the oil-refrigerant mixture that naturally accumulates in the upper layer of the evaporator 2 due to density differences through the oil inlet branch pipe 16, ensuring that the source medium of the ejected oil return branch has a high lubricating oil concentration, thereby significantly improving the ejection efficiency and the oil cleaning effect on the evaporator 2. At the same time, after lubrication circulation, the lubricating oil that has completed heat exchange and the small amount of liquid refrigerant that may precipitate due to temperature changes will naturally deposit at the bottom of the front vane cavity 102 under the action of gravity. The oil outlet branch pipe 18 can be used to eject and recover the deposited oil at the bottom of the front vane cavity 102, which can most thoroughly remove the deposited oil, effectively preventing excessive accumulation that could lead to abnormal oil level rise or re-stirring by the high-speed rotating impeller, thereby eliminating potential operational risks such as liquid slugging and oil contamination.

[0056] like Figure 1 , 2 As shown, in a preferred embodiment, the oil return chamber 101 of the compressor 1 is connected to the main oil tank 4 via an oil return pipe 9, which is located at the lower part of the oil return chamber 101 of the compressor 1. During the operation of the compressor 1, the lubricating oil that has completed its lubrication function, as well as the liquid refrigerant that may precipitate at low temperatures, will naturally accumulate and deposit at the bottom of the chamber under the influence of gravity. Connecting the oil return pipe 9 to the lower part of the oil return chamber 101 effectively draws out the deposited oil and returns it to the main oil tank 4, avoiding the problem of oil accumulation at the bottom not being able to drain due to the oil return port being too high. This prevents the risk of decreased lubrication performance or even sludge blockage of the system due to long-term oil deposition, oxidation, and deterioration.

[0057] In addition, a temperature sensor 19 is installed on the oil return pipe 9. Since the viscosity of lubricating oil is highly dependent on temperature, and viscosity directly affects the lubrication effect and flow resistance, the system can sense the real temperature of the lubricating oil returning from the compressor 1 in real time by monitoring the return oil temperature of the oil return pipe 9, thereby determining the internal working condition of the compressor 1 and the cooling effect of the lubricating oil.

[0058] like Figure 1 ,2 As shown, in some embodiments of this utility model, the main oil tank 4 is connected to the high-level oil tank 5 via an oil supply pipe 10. A first oil supply valve 11 is provided at one end of the oil supply pipe 10 near the main oil tank 4, and a second oil supply valve 12 is provided at the other end of the oil supply pipe 10 near the high-level oil tank 5. The operation of the oil supply valves mentioned above is performed by the first oil supply valve 11 and the second oil supply valve 12. The oil supply pipe 10 is also provided with an oil temperature heat exchanger 20 for regulating the oil temperature. The oil temperature heat exchanger 20 includes, but is not limited to, a plate heat exchanger. Taking a plate heat exchanger as an example, one set of heat exchange tubes in the plate heat exchanger is used to circulate lubricating oil, and another set of heat exchange tubes is used to circulate the heat exchange medium. The lubricating oil in the oil supply pipe 10 flows through the heat exchange tubes of the plate heat exchanger, and the heat exchange medium exchanges heat with the lubricating oil to regulate the oil temperature. The lubricating oil after heat exchange then flows to the high-level oil tank 5 via the oil supply pipe.

[0059] In practical applications, the system can dynamically adjust the heat exchange medium flow rate of the plate heat exchanger according to the return oil temperature, so as to stabilize the return oil temperature within the ideal range, thereby maximizing the system's operating efficiency while ensuring equipment safety.

[0060] For ease of understanding, the valves mentioned in this article can be selected according to specific application requirements. For example, the first oil supply valve 11, the first ejector return valve 13, and the second ejector return valve 14 mentioned above can all be shut-off valves, while the second oil supply valve 12 can be a ball valve. To ensure that the oil supply circuit and the ejector return branch can operate stably for a long time, the preferred solution is to design filters in the oil supply circuit and the ejector return branch.

[0061] This utility model also proposes a heat pump unit, including the above-mentioned compressor oil supply system. The system adds a liquid level sensor in the main oil tank and dynamically adjusts the working status of the oil supply circuit and the ejector oil return branch by monitoring the oil quantity in real time. This can not only avoid the extra energy consumption caused by continuous ejector oil return and ensure system energy efficiency, but also eliminate the problem of insufficient oil pressure difference caused by oil return delay and avoid the risk of failure and shutdown.

[0062] In some embodiments of this utility model, the compressor is a centrifugal compressor. As a high-speed rotating device, the centrifugal compressor has stringent requirements for the stability of the lubrication system, cooling efficiency, and oil quantity control accuracy. This is highly compatible with the precise oil supply capability of this oil supply system, ensuring the stability and reliability of the centrifugal heat pump unit.

[0063] It should be noted that the terminology used above is for describing specific embodiments only and is not intended to limit the exemplary embodiments according to this utility model. When the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof. The order of execution of actions, steps, etc., in the apparatus and methods shown in the specification and drawings can be implemented in any order unless a specific express order is specified, and as long as the output of the preceding process is not used in the subsequent process. Similar sequential terms used for ease of description do not imply that such an order must be followed.

[0064] Techniques, methods, and apparatus known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and apparatus should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0065] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A compressor oil supply system, characterized in that, include: The system includes a high-level oil tank that supplies oil to the compressor and a main oil tank that receives the lubricating oil flowing out of the compressor. The main oil tank is connected to the high-level oil tank via an oil pump to form an oil supply circuit. The main oil tank is also connected to the evaporator and the condenser to form an ejector return oil branch. The oil supply circuit and the ejector return branch are each equipped with an independently operating control valve, the main oil tank is equipped with a first liquid level sensor for detecting the oil quantity, and the control valve is electrically connected to the first liquid level sensor.

2. The compressor oil supply system according to claim 1, characterized in that, The compressor's oil return chamber is connected to the main oil tank. The compressor's oil return chamber is also equipped with at least one second liquid level sensor for detecting the oil level. The control valve is electrically connected to the second liquid level sensor.

3. The compressor oil supply system according to claim 1, characterized in that, The ejector return oil branch is connected to the main oil tank via the front vane cavity of the compressor.

4. The compressor oil supply system according to claim 3, characterized in that, The ejector return oil branch includes: an oil inlet ejector pipe connected between the evaporator and the condenser, an oil inlet branch pipe connected between the front vane cavity of the compressor and the evaporator, an oil outlet ejector pipe connected between the front vane cavity of the compressor and the condenser, and an oil outlet branch pipe connected between the front vane cavity of the compressor and the main oil tank. The oil inlet ejector and the oil outlet ejector are equipped with valves to prevent fluid from entering the condenser.

5. The compressor oil supply system according to claim 4, characterized in that, The oil inlet branch pipe is connected to the upper part of the evaporator, and the oil outlet branch pipe is connected to the lower part of the front vane cavity of the compressor.

6. The compressor oil supply system according to claim 1, characterized in that, The oil return chamber of the compressor is connected to the main oil tank via an oil return pipe, which is located at the lower part of the oil return chamber of the compressor.

7. The compressor oil supply system according to claim 6, characterized in that, The return oil pipe is equipped with a temperature sensor.

8. The compressor oil supply system according to claim 1, characterized in that, The main oil tank is connected to the high-level oil tank via an oil supply pipe, and the oil supply pipe is equipped with an oil temperature heat exchanger for regulating the oil temperature.

9. A heat pump unit, characterized in that, The heat pump unit includes the compressor oil supply system as described in any one of claims 1 to 8.

10. The heat pump unit according to claim 9, characterized in that, The compressor is a centrifugal compressor.

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