Compressor with multiple lubricant tanks

Abstract

This invention provides a compressor comprising a compressor housing having a discharge chamber and an intermediate pressure chamber, a first lubricant tank and a second lubricant tank, an inlet, a discharge port, a compression mechanism, an intermediate injection port, a lubricant supply channel, and a lubricant tank valve. The first lubricant tank is disposed in the discharge chamber. The second lubricant tank is disposed in the intermediate pressure chamber. The compression mechanism draws in working fluid from the inlet and discharges the working fluid into the discharge chamber. The intermediate injection port is fluidly connected to the intermediate pressure chamber. The lubricant supply channel connects the discharge chamber and the intermediate pressure chamber. The lubricant tank valve controls the flow of lubricant through the lubricant supply channel from the first lubricant tank to the second lubricant tank. The lubricant in the second lubricant tank is supplied at least to the compression mechanism.

Description

Technical Field

[0001] This disclosure generally relates to a compressor. More specifically, this disclosure relates to supplying lubricant within a compressor of a heating, ventilation, air conditioning, and refrigeration (HVACR) system. Background Technology

[0002] Heating, ventilation, air conditioning, and refrigeration (HVACR) systems typically include compressors for compressing working fluids. Compressors can be, for example (but not limited to), scroll compressors, rotary compressors, centrifugal compressors, reciprocating compressors, or other suitable types of compressors for compressing working fluids including refrigerants (e.g., a single refrigerant or a mixture of multiple refrigerants). Such compressors include moving parts such as drive shafts, compression mechanisms (e.g., scroll plates, rotors, impellers, etc.), and one or more bearings for supporting the moving parts. Lubricant is provided to the moving parts, including the bearings, to inhibit wear and prevent damage to the compressor.

[0003] In some embodiments, the HVACR system may be a transport climate control system (TCCS), which includes, for example, a transport refrigeration system (TRS) and / or a heating, ventilation, and air conditioning (HVAC) system. TRS is typically used to control environmental conditions (e.g., temperature, humidity, air quality, etc.) within the cargo space of a transport unit (e.g., trucks, containers (such as containers on flatbeds, intermodal containers, etc.), box trucks, semi-trailers, public transport vehicles, or other similar transport units). TRS can maintain the environmental conditions of the cargo space to preserve goods (e.g., products, frozen foods, pharmaceuticals, etc.). In some embodiments, the transport unit may include an HVAC system to control the climate within the passenger space of the vehicle. The HVACR system may include a climate control unit attached to the transport unit for housing HVACR components, such as, for example, a compressor, at least a portion of a working fluid circuit, one or more fans, etc. Summary of the Invention

[0004] This disclosure generally relates to heating, ventilation, air conditioning, and refrigeration (HVACR) systems. More specifically, this disclosure relates to providing lubrication to compressors in HVACR systems.

[0005] The embodiments described herein can minimize total lubricant tank capacity and lubricant carryover over a wide mass flow range. In other words, the embodiments described herein can prevent significant lubricant carryover in compressors operating within a large operating envelope and a wide speed range. In some embodiments, the compressor of the HVACR system may be a horizontal compressor to allow the compressor to be mounted on a rooftop climate control unit, for example, for transportation applications.

[0006] Horizontal compressors in transportation applications can provide increased flexibility in climate control unit architecture, particularly for top-mounted climate control units. Using horizontal compressors also allows for separate climate control units on the transportation unit itself (e.g., for articulated buses, double-decker buses, multi-zone transportation refrigeration systems for truck or trailer applications, etc.). Therefore, the embodiments described herein avoid long suction lines and limit refrigerant charge, which is important for flammable refrigerants (such as, but not limited to, A2L, A2, A3, B2L, B2, and B3 refrigerants).

[0007] In transportation applications, HVACR systems may need to operate at many different latitudes, and climate control within the climate-controlled space may need to provide a variety of climatic conditions (e.g., deep-freezing conditions (e.g., about -20°F), freezing conditions (e.g., about 0°F), and fresh conditions (e.g., 35°F)). Therefore, refrigerant capacity requirements may vary significantly to meet these conditions. The embodiments described herein allow HVACR systems to operate under these diverse conditions while providing low lubricant carry-over and using small reservoirs. In particular, the compressor of the HVACR system can be a variable-speed compressor capable of providing different refrigerant capacities.

[0008] The embodiments described herein can provide a lubricant reservoir located on the intermediate-pressure side of the compressor. An advantage of these embodiments is the use of low-volume refrigerant dissolved in the lubricant and low viscosity (e.g., 20-120 cSt). Another advantage of these embodiments is that heat from the electric motor does not affect the compressor's intake gas flow. Furthermore, the lubricant in the reservoir can be cooled with an optional lubricant cooler to reduce high discharge temperatures and prevent thermal degradation of the lubricant. An active lubricant separator (e.g., a coalescing lubricant separator) can be added to the lubricant reservoir. After passing through the optional lubricant cooler, the lubricant can be introduced at high pressure to the intermediate-pressure lubricant reservoir valve. In this way, degassing of the lubricant can be largely prevented from affecting the compressor's intake gas flow. By reducing lubricant carryover, the amount of lubricant that needs to be recirculated during low-speed periods in the suction line and / or remote evaporator can be reduced.

[0009] Therefore, many of the internal components used in vertical scroll compressors with suction slots can also be used in horizontal compressors.

[0010] In one embodiment, the compressor includes a compressor housing, a first lubricant tank, a second lubricant tank, a compression mechanism, and a lubricant supply passage. A discharge chamber having the first lubricant tank and an intermediate-pressure chamber having the second lubricant tank are each disposed within the compressor housing. An inlet and an outlet are formed in the compressor housing. The compression mechanism is disposed within the compressor housing and configured to draw in working fluid from the inlet and discharge the working fluid into the discharge chamber. An intermediate injection port formed in the compression mechanism is fluidly connected to the intermediate-pressure chamber. The lubricant supply passage extends from the discharge chamber to the intermediate-pressure chamber, and a lubricant tank valve is configured to control the flow of lubricant through the lubricant supply passage from the first lubricant tank in the discharge chamber to the second lubricant tank in the intermediate-pressure chamber. Lubricant in the second lubricant tank is supplied at least to the compression mechanism.

[0011] In one embodiment, the heating, ventilation, air conditioning, and refrigeration (HVACR) system includes a working fluid loop. The working fluid loop includes a compressor, condenser, expander, and evaporator in fluid connection, through which the working fluid flows.

[0012] The compressor in an HVACR system may include a compressor housing, a first lubricant reservoir, a second lubricant reservoir, a compression mechanism, and a lubricant supply passage. A discharge chamber with the first lubricant reservoir and an intermediate-pressure chamber with the second lubricant reservoir are each disposed within the compressor housing. An inlet and an outlet are formed within the compressor housing. The compression mechanism is disposed within the compressor housing and configured to draw in working fluid from the inlet and discharge the working fluid into the discharge chamber. An intermediate injection port formed in the compression mechanism is fluidly connected to the intermediate-pressure chamber. The lubricant supply passage extends from the discharge chamber to the intermediate-pressure chamber, and a lubricant reservoir valve is configured to control the flow of lubricant through the lubricant supply passage from the first lubricant reservoir in the discharge chamber to the second lubricant reservoir in the intermediate-pressure chamber. Lubricant in the second lubricant reservoir is supplied at least to the compression mechanism.

[0013] In one embodiment, a method of operating a compressor is provided. The compressor includes a compressor housing, a first lubricant tank, a second lubricant tank, a compression mechanism, and a lubricant supply passage. A discharge chamber having the first lubricant tank and an intermediate-pressure chamber having the second lubricant tank are each disposed within the compressor housing. An inlet and an outlet are formed in the compressor housing. The compression mechanism is disposed within the compressor housing and configured to draw in working fluid from the inlet and discharge the working fluid into the discharge chamber. An intermediate injection port formed in the compression mechanism is fluidly connected to the intermediate-pressure chamber. The lubricant supply passage extends from the discharge chamber to the intermediate-pressure chamber, and a lubricant tank valve is configured to control the flow of lubricant through the lubricant supply passage from the first lubricant tank in the discharge chamber to the second lubricant tank in the intermediate-pressure chamber. Lubricant in the second lubricant tank is supplied at least to the compression mechanism. The method includes detecting the lubricant condition in the second lubricant tank, such as level, temperature, pressure, and viscosity, via a second lubricant tank level sensor, and operating the lubricant tank valve to adjust the lubricant level in the second lubricant tank. Attached Figure Description

[0014] Referring to the accompanying drawings, which form a part of this disclosure, embodiments of the systems and methods described herein can be practiced.

[0015] Figure 1 This is a schematic diagram of a working fluid circuit according to one embodiment.

[0016] Figure 2 This is a schematic diagram of a compressor according to one embodiment.

[0017] Figure 3 This is a flowchart of a method for operating a compressor according to one embodiment.

[0018] Figure 4 This is a flowchart of a method for controlling the lubricant level in a compressor according to an embodiment.

[0019] Similar reference numerals throughout the accompanying drawings indicate similar parts. Detailed Implementation

[0020] This disclosure generally relates to heating, ventilation, air conditioning, and refrigeration (HVACR) systems. More specifically, this disclosure relates to supplying lubricant within the compressor of an HVACR system. HVACR systems can operate at any ambient temperature globally, and the space regulated by the HVACR system can be frozen, refrigerated, or heated. The regulated space can be, but is not limited to, insulated or enclosed spaces, such as vehicle or train carriages.

[0021] For example, the lubricant can be oil. In one example of a horizontal scroll compressor, a lubricant reservoir is provided in the lower portion of the compressor housing, with a defined level to supply a certain amount of lubricant to the compressor. However, the availability of lubricant for lubricating the various components of a scroll compressor may vary depending on different operating conditions. For example, during the start-up phase of a scroll compressor, the moving parts of the compressor, such as the moving scroll, counterweight, etc., and / or bearings, such as the upper bearing, lower bearing, moving bearing, thrust bearing, etc., are initially lubricated. After overcoming certain forces (e.g., gravity, surface tension, etc.), most of the lubricant returns from the moving parts to the lubricant reservoir. The return flow of lubricant to the reservoir can vary depending on the configuration of the specific compressor (e.g., the size / shape of the lubricated parts, the size of the compressor, the location of the lubricant separator, the type of lubricant, the type of working fluid (e.g., refrigerant), the flow path through the compressor, the motor location, etc.). The compressor speed can also alter the supply / utilization of lubricant. Therefore, during startup (e.g., until a balanced level of lubricant is established in the compressor) or when the compressor is operated at various speeds, the amount of lubricant available in the lubricant tank can vary as the lubricant is discharged downwards along the scroll compressor.

[0022] During different operating conditions of the compressor (e.g., operating at higher speeds versus operating at lower speeds), the amount of lubricant available in the lubricant reservoir may vary, and in some cases, the reservoir may not contain enough lubricant to maintain the desired flow of lubricant for adequately lubricating the compressor's moving parts, which could lead to compressor damage. For example, a compressor operates at low speeds using a lower flow of lubricant, and a larger amount of lubricant is required to maintain adequate lubrication of the moving parts during the transition from low to high speed operation.

[0023] This document discloses embodiments of a compressor, an HVACR system having the compressor, and methods of operating the compressor, which provide multiple lubricant tanks in the compressor to provide a buffer capacity for lubricant supply to the compressor.

[0024] Figure 1 This is a schematic diagram of the working fluid loop 10 (also referred to as the heat transfer loop) of an HVACR system 1 according to an embodiment. The working fluid loop 10 includes a compressor 12, a condenser 14, an expander 16, and an evaporator 18. These components of the working fluid loop 10 are fluidly connected.

[0025] Figure 1The working fluid loop 10 is an example, and modifications may be made in other embodiments to include additional components. For example, in one embodiment, the working fluid loop 10 may include other components, such as, but not limited to, one or more flow control devices, additional expansion devices, receiver tanks, dryers, wicking heat exchangers, filters, etc. In one embodiment, the working fluid loop 10 may include an optional valve 20.

[0026] HVACR system 1 is used to control environmental conditions (e.g., temperature, humidity, air quality, etc.) in a space (often referred to as a conditioned space). Examples of conditioned spaces include, but are not limited to, enclosed spaces within residential buildings (e.g., residences), commercial buildings (e.g., office buildings), vehicles (e.g., public transport vehicles, trucks, vans, etc.), and transport units (e.g., containers (such as flatbed containers, intermodal containers, ocean shipping containers, etc.), box trucks, or other similar transport units).

[0027] For example, in one embodiment, the HVACR system 1 can be used in a transport climate control system configured to regulate the enclosed space of a transport unit. The HVACR system 1 can be used for a single temperature application or multiple temperature applications for the transport unit, such as multiple climate control zones. For example, in one embodiment, the HVACR system can be used as a residential or commercial HVACR configured to regulate the interior space of a building.

[0028] The compressor 12, condenser 14, expander 16, evaporator 18, and economizer 20 are fluidly connected via working fluid lines 24, 26, 28, 30 (30a and 30b) and 32, and optionally working fluid lines 34 and 36. In one embodiment, the working fluid lines 24, 26, 28, 30 (30a and 30b), 32, 34, and 36 may alternatively be referred to as working fluid conduits 24, 26, 28, 30 (30b and 30a), 32, 34, and 36, etc.

[0029] In one embodiment, the working fluid loop 10 can be configured as a cooling system (e.g., an air conditioning system, a refrigeration system, a fluid cooling unit of an HVACR system, etc.) capable of operating in a cooling mode. In one embodiment, the working fluid loop 10 can be configured as a heat pump system capable of operating in both a cooling mode and a heating / defrosting mode. The HVACR system 1 can be configured to operate in heating mode, cooling mode, dehumidification mode, defrosting mode, etc.

[0030] The working fluid circuit 10 can operate according to generally known principles. The working fluid circuit 10 can be configured to heat or cool a process fluid (e.g., water, air, etc.). In one embodiment, the working fluid circuit 10 can represent a cooling unit or the like that that cools a process fluid (e.g., water, an aqueous ethanol solution, etc.), and the process fluid is used to cool air supplied to a regulated space. In one embodiment, the working fluid circuit 10 can represent an air conditioner or a heat pump that regulates a process fluid such as air.

[0031] During exemplary operation of the working fluid circuit 10, the working fluid flows into the compressor 12 in a gaseous state from the evaporator 18 at a relatively low pressure. The working fluid flows into the compressor 12 through the suction port 13A. The compressor 12 compresses the gas from a relatively low pressure (e.g., suction pressure (P...)). S Compression to relatively high pressures (e.g., exhaust pressure (P)) D This also heats the gas. In one embodiment, compressor 12 is a positive displacement compressor (e.g., screw compressor, scroll compressor, reciprocating compressor, etc.). The relatively high-pressure working fluid is discharged from the outlet 13B of compressor 12.

[0032] After compression, the relatively high-pressure and relatively high-temperature gas discharged from compressor 12 flows from compressor 12 to condenser 14 through working fluid line 24. In addition to the working fluid flowing through condenser 14, a first process fluid PF1 (e.g., external air, external water, hot water to be heated, etc.) also flows through condenser 14. The working fluid flows through condenser 14 and dissipates heat to the first process fluid (e.g., water, air, etc.), which cools and condenses the working fluid.

[0033] The cooled working fluid (now in liquid form) flows to the expander 16 (e.g., via working fluid line 26). The expander 16 allows the working fluid to expand and reduce its pressure. In one embodiment, the expander 16 may be an expansion valve, expansion plate, expansion vessel, orifice, or other such type of expansion mechanism. It should be understood that the expander can be any type of expander used in the art for expanding a working fluid to reduce its temperature. The expander 16 is referred to herein as an "expander". The gaseous / liquid working fluid has a lower temperature after being expanded by the expander 16.

[0034] The working fluid may be a mixture of liquid and gas, flowing from expander 16 to evaporator 18 (e.g., via working fluid line 28) and then to compressor 12 (e.g., via working fluid line 32). For example, a first portion (e.g., the main / largest portion) of the working fluid flows from expander 16 to evaporator 18, and a second portion flows from expander 16 to compressor 12. The second portion of the working fluid flows into intermediate inlet 13C of compressor 12. This second portion of the working fluid may be referred to as intermediate-pressure working fluid. The intermediate-pressure working fluid is injected into the compression mechanism at an intermediate location. In one embodiment, working fluid circuit 10 may include an economizer (not shown) configured to use a different portion of the working fluid (e.g., utilizing the first portion of the working fluid) to cool the intermediate-pressure working fluid.

[0035] In addition to the working fluid flowing through the evaporator 18, a second process fluid PF2 (e.g., air, water, cooling unit water, cooling unit medium, etc.) also flows through the evaporator 18. The working fluid flowing through the evaporator 18 absorbs heat from the second process fluid (e.g., water, air, etc.), which heats and cools the working fluid. The heating of the working fluid converts it into a gaseous form. The gaseous working fluid then returns to the compressor 12 (via working fluid lines 30 (30a and 30b)). The above process continues when the working fluid circuit 10 is operating, for example, in cooling mode (e.g., when the compressor 12 is activated).

[0036] In one embodiment, the working fluid circuit 10 may include an intermediate pressure regulating valve 20. The regulating valve 20 can be used to redirect a portion of the intermediate-pressure working fluid from the intermediate inlet 13C to the suction inlet 13A of the compressor 10. The amount of working fluid flowing into the optional working fluid line 36 is controlled by the regulating valve 20. The working fluid in working fluid line 30a is mixed with the working fluid in working fluid line 36 and supplied to the compressor 12 via working fluid line 30b. The gaseous portion of the working fluid flowing to the compressor 12 via working fluid line 30b is at an intermediate pressure (e.g., between the discharge pressure and the suction pressure) between the relatively low pressure of the working fluid and the relatively high pressure of the working liquid.

[0037] Figure 2 This is a schematic diagram of a compressor 100 according to one embodiment. For example, in one embodiment, the compressor 100 may be... Figure 1 The compressor 12 in the working fluid circuit 10.

[0038] The compressor 100 shown is a single-stage compressor. More specifically, the compressor 100 shown is a single-stage horizontal compressor with a horizontal or near-horizontal drive shaft. It should be understood that the principles described in this specification are not limited to single-stage horizontal compressors or horizontal compressors, and in other embodiments, the features discussed herein with respect to compressor 100 can be applied to multi-stage compressors with two or more compression stages, or to vertical compressors with a vertical or near-vertical drive shaft.

[0039] Compressor 100 includes a compressor housing 102. Components of compressor 100 are disposed within compressor housing 102. Compressor 100 includes a discharge chamber 104 and an intermediate pressure chamber 106 disposed within compressor housing 102. Discharge chamber 104 and intermediate pressure chamber 106 are not directly connected. Figure 2 As shown, the discharge chamber 104 and the intermediate pressure chamber 106 are separated by a partition 108 that is impermeable to the working fluid and lubricant. The discharge chamber 104 has a first lubricant tank 110, and the intermediate pressure chamber 106 has a second lubricant tank 112.

[0040] The compressor 100 includes a suction inlet 114, an intermediate inlet 116, and a working fluid outlet 118. The specific positions of the suction inlet 114, intermediate inlet 116, and outlet 118 relative to the compressor housing 102 are not particularly limited to the illustrated embodiment and may differ in other embodiments. For example, in one embodiment, the suction inlet 114, intermediate inlet 116, and working fluid outlet 118 may be… Figure 1 The compressor 12 has a suction port 13A, an intermediate inlet 13C, and a discharge port 13B.

[0041] The suction inlet 114, intermediate vapor inlet 116, and working fluid outlet 118 are configured to be fluidly connected to an external pipeline, a suction inlet pipeline 114E, an intermediate vapor inlet pipeline 116E, and a working fluid outlet pipeline 118E, respectively. The suction inlet pipeline 114E, intermediate vapor inlet pipeline 116E, and working fluid outlet pipeline 118E can be part of a refrigeration circuit. For example, the suction inlet pipeline 114E can be... Figure 1 The working fluid lines 30 (30a and 30b) and the intermediate steam inlet line 116E can be... Figure 1 The working fluid line 32 and the working fluid outlet line 118E can be Figure 1 Working fluid pipeline 24 in the middle.

[0042] The compressor 100 includes a compression mechanism 120 disposed within the compressor housing 102. The compression mechanism 120 may be suitable for compressing a working fluid circuit (e.g., Figure 1The working fluid circuit 10 in the compressor can be any type of positive displacement compression mechanism for the gaseous working fluid (e.g., gaseous refrigerant). For example, in one embodiment, the compression mechanism can be, but is not limited to, a pair of meshing scroll discs (e.g., for a scroll compressor), meshing screws (e.g., for a rotary compressor), impellers (e.g., for a centrifugal compressor), etc.

[0043] In the example shown, the compression mechanism 120 has an intake port 122, an intermediate injection port 124, and a discharge port 126. The compression mechanism 120 is configured to draw in working fluid from the intake port 114 via the intake port 122 and discharge the working fluid into the discharge chamber 104 via the discharge port 126. The intermediate injection port 124 is fluidly connected to the intermediate pressure chamber 106 and is configured to supply working fluid from the intermediate pressure chamber 108 to the compression mechanism 120. In one embodiment, the discharge port 126 may be fitted with a valve 128 (e.g., a valve plate, a dynamic non-reversing valve, a check valve) to ensure that the working fluid flows into the discharge chamber 104 via the discharge port 126, rather than flowing backward from the normal flow direction.

[0044] During operation, the compression mechanism 120 draws in a relatively low pressure (e.g., at a suction pressure P) from the suction port 114. S The working fluid (under the first pressure) is compressed and will be discharged at a relatively high pressure (e.g., at the discharge pressure P). D The compressed working fluid (under a second pressure) is discharged into the discharge chamber 104. The compressed working fluid is discharged through the discharge port 118 via the discharge chamber 104, as discussed in more detail below. At medium pressure P... I Below (e.g., at inhalation pressure P) S With discharge pressure P D Under pressure between the first and second pressures, the working fluid flows from the intermediate pressure chamber 106 into the compression mechanism 120. The intermediate pressure working fluid is drawn in through the intermediate pressure chamber 106 from the intermediate inlet 116. The intermediate pressure working fluid mixes with the partially compressed intake fluid, and the mixture is further compressed and discharged as compressed working fluid into the discharge chamber 104.

[0045] The compressor 100 includes a motor 140 and a drive shaft 142 that drives the compression mechanism 120 to compress the working fluid. For example, the drive shaft 142 may be connected to a moving part of the compression mechanism (e.g., a scroll plate, a rotating rotor, a rotating screw, etc.), and rotation of the drive shaft 142 causes the compression mechanism to compress the working fluid. The drive shaft 142 is supported by one or more bearings 143.

[0046] In the illustrated embodiment, motor 140 is an electric motor operating according to well-known principles. For example, motor 140 includes a stator 146 and a rotor 148 that is magnetically rotated by the stator 146. A drive shaft 142 is attached to the rotor 148 such that the drive shaft 142 rotates as the rotor 148 rotates. The drive shaft 142 may be fixed to the rotor 148, for example, via an interference fit. In other embodiments, motor 140 may be an external electric motor, an internal combustion engine (e.g., a diesel engine or a gasoline engine), etc. It should be understood that in such embodiments, electric motor 140, stator 146, and rotor 148 will not be present in compressor 100.

[0047] A compressor lubricant pump 144 may be attached to a drive shaft 142 at an end not connected to the compression mechanism 120, and may be configured to pump lubricant into the compression mechanism 120 via the drive shaft 142. The compressor lubricant pump 144 may be mechanically or electrically driven. The drive shaft 142 includes a lubricant passage 145 through which lubricant is supplied to the compression mechanism 120. In one embodiment, the lubricant pump 144 may be formed by an opening in the drive shaft 142, wherein the inclination of the lubricant passage 145 (e.g., at an angle relative to the axis of the drive shaft 142) causes the rotating drive shaft 142 to generate centrifugal force, thereby providing lubricant into and through the lubricant passage 145 via a pumping action.

[0048] The compressor 100 has a lubricant supply passage 150 extending from the discharge chamber 104 to the intermediate pressure chamber 106. The lubricant supply passage 150 fluidly connects a first lubricant reservoir 110 of the discharge chamber 104 to a second lubricant reservoir 112 of the intermediate pressure chamber 106. The lubricant supply passage 150 is configured to guide lubricant from the first lubricant reservoir 110 into the intermediate pressure chamber 106. Figure 2 The diagram shows a channel formed outside the compressor housing 102. However, it should be understood that in other embodiments, the lubricant supply channel 150 may be formed inside the compressor housing 102 and / or as part of the compressor housing 102.

[0049] Lubricant supply passage 150 includes a lubricant reservoir valve 152 configured to control the flow of lubricant from a first lubricant reservoir 110 in discharge chamber 104 through the lubricant reservoir valve 152 to a second lubricant reservoir 112 in intermediate pressure chamber 106. For example, opening the lubricant reservoir valve 152 increases the flow rate of lubricant from the first lubricant reservoir 110 to the second lubricant reservoir 112 (through lubricant supply passage 150). For example, closing the lubricant reservoir valve 152 reduces the flow rate of lubricant from the first lubricant reservoir 110 (through lubricant supply passage 150) to the second lubricant reservoir 112. It should be understood that the terms “open,” “opening,” “close,” “closing,” etc., used herein for the lubricant reservoir valve 152 generally refer to incremental changes in the valve’s position, rather than absolute positions (e.g., 0% open, at its maximum flow / size, etc.). For example, closing the valve means moving the valve position closer to a fully closed position, and opening the valve means moving the valve position closer to a fully open position.

[0050] In one embodiment, the lubricant supply passage 150 may include a lubricant cooler 154. The lubricant cooler 154 is configured to cool the lubricant flowing through the lubricant supply passage 150. The lubricant cooler 154 can cool the temperature of the lubricant from T4 to T5. T4 is equal to or lower than the temperature T1 of the first lubricant tank 110, and higher than T5. The lubricant cooler 154 may be controlled to maintain the lubricant temperature below a predetermined maximum temperature to prevent lubricant decomposition, or may be controlled to lower the lubricant temperature to achieve a desired viscosity. The lubricant cooler 154 may be a heat exchanger configured to cool the lubricant flowing through the lubricant supply passage 150. For example, in one embodiment, the lubricant cooler 154 may be configured to cool the lubricant using a portion of the cooler working fluid in a heat transfer circuit. For example, in another embodiment, the lubricant cooler 154 may be configured to cool the lubricant using a fluid different from the working fluid (e.g., a first process fluid, external water, etc.).

[0051] The compressor 100 includes one or more sensors. In the illustrated embodiment, the compressor 100 includes lubricant tank sensors (e.g., 160a, 160b, and 160c). Each lubricant tank sensor is configured to detect the lubricant level in its respective tank (e.g., detect the lubricant level in the respective lubricant tank). (First) Lubricant tank sensor 160a senses the lubricant level L1 in a first lubricant tank 110. (Second) Lubricant tank sensor 160b senses the lubricant level L2 in a second lubricant tank 112. (Third) Lubricant tank sensor 160c senses the lubricant level L3 in a third lubricant tank 170.

[0052] Lubricant tank sensors 160a, 160b, and 160c can be configured to detect additional lubricant conditions, such as, but not limited to, temperature, pressure, and viscosity. For example, in addition to the lubricant level L1, the (first) lubricant tank sensor 160a can also be configured to sense the temperature T1 of the first lubricant tank 110. In addition to the lubricant level L2, the (second) lubricant tank sensor 160b can also be configured to sense the temperature T2 of the second lubricant tank 112. In addition to the lubricant level L3, the (third) lubricant tank sensor 160c can also be configured to sense the temperature T3 of the third lubricant tank 170.

[0053] Compressor 100 includes a controller 161. Controller 161 controls the operation of compressor 100. Specifically, controller 161 controls lubricant tank valve 152. Controller 161 can also control the overall operation of compressor 100 (e.g., the speed of compressor 100, the speed of motor 140, etc.). For example, controller 161 can be configured to receive lubricant levels (L1, L2, and L3) in the reservoir detected by lubricant tank sensors 160a, 160b, and 160c. Controller can be further configured to compare the lubricant levels with predetermined values ​​and instruct lubricant tank valve 152 to open or close based on the comparison result. Controller can be further configured to receive other information, such as, but not limited to, the temperature, pressure, and viscosity of the lubricant, and control lubricant tank valve 152. Controller 161 described in the figures and below is described / shown as a single component. However, it should be understood that the “controller” shown in the figures and described herein can include multiple discrete or interconnected components, which in one embodiment include a memory (not shown) and a processor (not shown). In one embodiment, the controller 161 may be the HVACR system to which the compressor 100 is connected (e.g., Figure 1 The controller of the HVACR1 system.

[0054] Lubricant tank valve 152 is configured to operate based on lubricant levels L1, L2, L3 in one or more of the lubricant tanks 110, 112, 170. For example, as discussed above, lubricant tank valve 152 can be operated by controller 161. In one embodiment, lubricant tank valve 152 is controlled based on lubricant level L2 in second lubricant tank 112. Lubricant tank valve 152 can be configured to adjust flow such that lubricant level L2 in second lubricant tank 112 is at or above a minimum level (e.g., a predetermined minimum level).

[0055] For example, when controller 161 determines that the lubricant level L2 in the second lubricant tank 112 is below a predetermined minimum level, controller 161 may instruct lubricant tank valve 152 to open to increase the lubricant flow rate from the first lubricant tank 110 to the second lubricant tank 112. In another example, when the lubricant level in the second lubricant tank 112 is above a maximum level (e.g., a predetermined maximum level), lubricant tank sensor 160b detects a high lubricant level and sends the lubricant level information to controller 161, which then instructs lubricant tank valve 152 to close and reduce or stop the lubricant flow.

[0056] In one embodiment, controller 161 may be configured to receive information other than the lubricant level and control lubricant tank valve 152. For example, the additional information may be the temperatures T1, T2, and T3 of oil tanks 110, 112, and 170, respectively.

[0057] like Figure 2 As shown, the compressor 100 may have an optional third lubricant tank 170 disposed in the intermediate pressure chamber 106 above the second lubricant tank 112. The drive shaft 142 is connected to the lubricant in the third lubricant tank 170 via a lubricant pump 144, and can supply lubricant from the third lubricant tank 170 to the compression mechanism 120 via a lubricant passage 145 in the drive shaft 142. The lubricant passage 145 can also supply lubricant along the drive shaft 142 to other components (e.g., to bearings 143, etc.). For example, the lubricant pump 144 may be formed by an opening in the end of the drive shaft 142, wherein the lubricant passage 145 is angled relative to the axis of the drive shaft 142, causing the drive shaft 142 to rotate to draw in lubricant and pass it through the lubricant passage 145.

[0058] In one embodiment, the compressor 100 may include a lubricant pump 172. The lubricant pump 172 may be configured to deliver lubricant from a second lubricant tank 112 to a third lubricant tank 170. The lubricant pump 172 may be configured to maintain a minimum lubricant level L3 (e.g., a predetermined minimum level) in the third lubricant tank 170. For example, the lubricant pump 172 may be operated using a lubricant sensor 160c for the third lubricant tank 170.

[0059] It should be understood that in other embodiments, the drive shaft lubricant pump 144 may be configured to pump directly from the second lubricant reservoir 112. For example, in one embodiment, the drive shaft lubricant pump 144 may be formed by a hose, conduit, etc., directly connecting the end of the drive shaft 142 to the second lubricant reservoir 112. The rotational force of the drive shaft 142 then draws lubricant into the lubricant passage 145 of the drive shaft 142 through the hose, conduit, etc. The illustrated embodiment is a horizontal compressor. It should be understood that in one embodiment, the compressor 100 may be a vertical compressor, wherein the end of the drive shaft 142 is disposed in the second lubricant reservoir 112 and pumped directly from the second lubricant reservoir 112. In such embodiments, the compressor 100 does not include a third lubricant reservoir 170.

[0060] The compressor 100 may include a lubricant separator 176 in the discharge chamber 104. The lubricant separator 176 may divide the discharge chamber 104 into sub-chambers 104a and 104b. A working fluid outlet 118 is connected to sub-chamber 104a, and an outlet 126 of the compression mechanism 120 is connected to sub-chamber 104b. The material of the lubricant separator 176 is not particularly limited, as long as it is permeable and can capture lubricant contained in the working fluid discharged from the compression mechanism. In the illustrated embodiment, the lubricant separator 176 is disposed in the discharge chamber 104; however, it should be understood that the lubricant separator may be disposed outside the compressor housing. It should also be understood that the lubricant separator 176 may be formed in various forms, as long as it can remove lubricant from the working fluid discharged from the compression mechanism 120. For example, the lubricant separator 176 may be cup-shaped and attached to the interior of the opening to which the working fluid outlet 118 is attached. In another embodiment, the lubricant separator 176 may be a channel or labyrinth structure.

[0061] In the operation of the illustrated embodiment, compressed working fluid is discharged from compression mechanism 120 into sub-chamber 104b via discharge port 126, and reaches sub-chamber 104a via lubricant separator 176 before being discharged from working fluid discharge port 118. As the working fluid passes through lubricant separator 176, lubricant entrained in the warm working fluid is captured and returned to the first lubricant tank 110. It should be understood that this mechanism can reduce the amount of lubricant leaving from working fluid discharge port 118 and entering the refrigeration circuit. It should be further understood that the efficiency and reliability of the HVACR system can be improved because the amount of lubricant deposited in the refrigeration circuit that could impede the flow of working fluid and reduce heat exchange efficiency can be reduced.

[0062] exist Figure 2 In this circuit, working fluid lines 114E, 116E, and 118E are part of the refrigeration circuit attached to compressor 100. Suction line 114E can be... Figure 1The working fluid pipeline 30 and the intermediate steam inlet pipeline 116E can be... Figure 1 The working fluid line 32 and the working fluid outlet line 118E can be Figure 1 The working fluid line 24 is included. Optional valve 180 is a bypass valve connecting the suction inlet line 114E and the intermediate vapor inlet line 116E, and can be installed in the refrigeration circuit. This valve can be... Figure 1 The regulating valve 20 is located in the compressor housing 102. In one embodiment, the valve 180 is located outside the compressor housing 102.

[0063] In operation, for example, when determining the pressure (P) of the working fluid entering the compression unit 120 from the suction line 114E. S When the pressure is below a predetermined minimum, valve 180 can be operated to allow the working fluid in the intermediate steam inlet line 116E to flow into and mix with the working fluid in the suction line 114E, and to adjust the conditions (e.g., temperature, pressure) of the working fluid entering the compression unit 120. Alternatively, for example, when it is determined that the pressure of the working fluid entering the compression unit 120 from the suction line 114E is higher than a predetermined maximum pressure, valve 180 can be operated to reduce or stop the flow of working fluid from the intermediate steam inlet line 116E to the suction line 114E.

[0064] During operation, such as during changes in operating mode, such as changes in compressor speed, a large amount of lubricant is pumped into the compression mechanism 120, thereby lowering the lubricant level in the second lubricant tank 112. The second lubricant tank level sensor 160b detects the change in lubricant level and sends a signal L2 to control the lubricant tank valve 152 via the controller 161 to open the lubricant tank valve 152, allowing lubricant to be rapidly supplied from the first lubricant tank 110 to the second lubricant tank 112. The first lubricant tank 110 provides a buffer system that delivers lubricant to the second lubricant tank 112, preventing the second lubricant tank 112 from being emptied and avoiding damage to the compressor mechanism 120 due to insufficient lubrication. The first lubricant tank 110 also provides buffering capacity during compressor start-up when the compressor operates at higher speeds to reduce the temperature of the regulated space as quickly as possible, pumping / using more lubricant than is used during normal compressor operation.

[0065] It should be understood that the compressor with multiple reservoirs as described above provides a reliable compressor because the lubricant level in the second lubricant reservoir can be maintained at the desired level, and the risk of "dry operation" or operation without lubricant can be reduced. It should also be understood that because the first lubricant reservoir 110 is located inside the compressor housing 102, the compressor does not require a larger footprint than a compressor with a single lubricant reservoir and less lubricant buffering capacity. It should also be understood that this design allows the use of existing compressor mechanisms in either a vertical or horizontal orientation, and the compressor can be a vertical compressor where the discharge chamber and intermediate pressure chamber are arranged vertically side-by-side, or a horizontal compressor where the discharge chamber and intermediate pressure chamber are arranged horizontally side-by-side.

[0066] In one embodiment, the lubricant passing through the lubricant supply channel 150 can be cooled to regulate its temperature. The lubricant at the compressor discharge side is warm, and the amount of working fluid dissolved in it is higher. By cooling the lubricant passing through the lubricant supply channel, the working fluid dissolved in the lubricant can be released into the intermediate-pressure chamber, and both the working fluid and the lubricant can be reused in the compressor. It should be understood that such a cooling mechanism can improve compressor efficiency because the working fluid dissolved in the lubricant can be recovered and used for refrigeration. It should also be understood that the cooling mechanism allows the use of low-viscosity lubricants, such as, but not limited to, Solest 35, Solest 120, and Emkarate RL32H. This is because the lubricant in the second lubricant tank can remain relatively cool, resulting in less working fluid dissolving in the lubricant, and thus allowing the use of low-viscosity lubricants.

[0067] In one embodiment, the selected working fluid includes a refrigerant, such as R-134a, or a refrigerant having a relatively lower global warming potential (GWP) than R-134a, which can be used as an alternative to R-134a. In another embodiment, the selected working fluid may include refrigerants such as R1234ze(E), R-513A, R452A, R454A, R454B, R454C, R32, hydrocarbons, other refrigerant blends, etc.

[0068] Figure 3 This is a flowchart of a method 300 for operating a compressor having multiple lubricant tanks according to an embodiment. The following will discuss... Figure 2 The compressor 100 shown describes method 300. However, it should be understood that method 300 can be used to operate compressors with different configurations. In one embodiment, method 300 can be employed by compressor 12 in working fluid circuit 10. Method 300 begins at 310.

[0069] At 310, the compression mechanism 120 is driven by the motor 140. When the motor 140 operates, the working fluid is drawn into the compression mechanism 120. Then, method 300 proceeds in parallel to 320 and 330.

[0070] At 320, motor 140 drives compression mechanism 120 to draw working fluid into compressor 100 via suction port 114. Furthermore, at 330, intermediate-pressure working fluid is injected from intermediate-pressure chamber 106 into compression mechanism 120 via intermediate injection port 124; both the suction working fluid and the intermediate-pressure working fluid are compressed in compression mechanism 120. Then, method 300 proceeds to 340.

[0071] At 340, the inhaled working fluid and the injected medium-pressure working fluid are compressed into compressed working fluid by the compression mechanism 120. Then, method 300 proceeds to 350.

[0072] At 350, the compressed working fluid obtained by compressing the working fluid from the suction port 114 and the intermediate injection port 124 is discharged into the discharge chamber 104. Then, method 300 proceeds to 360.

[0073] At 360°, the compressed working fluid is discharged from outlet 118.

[0074] Therefore, method 300 can be a continuous process performed during the operation of compressor 100. It should be understood that multiple operations in 310 to 360 can be performed simultaneously, synchronously or interleaved in compressor 100, starting from different times.

[0075] Figure 4 This is a flowchart of a method 400 for controlling the lubricant level in a compressor having multiple lubricant tanks, according to one embodiment. The following is about... Figure 2 The compressor 100 shown describes method 400. However, it should be understood that method 400 can be used to operate compressors with different configurations. In one embodiment, method 400 can be employed by compressor 12 in working fluid circuit 10. Method 400 begins at 410.

[0076] At 410, compressor 100 has lubricant in lubricant tanks 110, 112, and 170, wherein lubricant tanks 110, 112, and 170 are part of a lubricant circuit for supplying lubricant to the moving parts of compressor 100. Compressor 100 is shut down or in a stable operating state, wherein the lubricant pumped into and returned from compression mechanism 120 is in equilibrium. The lubricant level in the second lubricant tank 112 is above a predetermined minimum lubricant threshold level L. 2min And the lubricant reservoir valve 152 in the lubricant supply channel 150 is closed. 2minAt least the minimum lubricant level in the second lubricant tank 112, which is the level required to maintain a sufficient supply of lubricant to the moving parts of the compressor during normal operation of the compressor, for example, an equalization level of lubricant based on, for example, lubricant entrained in the compressed fluid and / or lubricant discharged from the compressor parts and returned to the lubricant tank of the compressor.

[0077] In one embodiment, the second lubricant tank 112 has a lubricant level sensor 160b configured to send information about the lubricant level (L2) of the second lubricant tank to the controller 161. It should be understood that additional sensors 160a and 160c may be provided in the first lubricant tank 110 and the third lubricant tank 170 to detect information about the lubricant level (L1) of the first lubricant tank 110 or the lubricant level (L3) of the third lubricant tank 170 and send the information to the controller 161. Then, method 400 proceeds to 412.

[0078] At 412, compressor 100 may be started or its operating conditions may be changed, for example, from low speed to high speed. Then, method 400 proceeds to 414. Alternatively, method 400 may optionally proceed to 416 instead of 414 when a decrease in the lubricant level (L2) is expected due to the change in operating conditions.

[0079] At 414, controller 161 instructs lubricant reservoir valve 152 to remain closed. Then, method 400 proceeds to 418. Alternatively, at 416, controller 161 instructs lubricant reservoir valve 152 to open. Then, method 400 proceeds to 418.

[0080] For example, when the compressor speed in a scroll compressor changes from low to high, the centrifugal force of the drive shaft can alter the lubricant distribution within the compression mechanism, potentially creating a temporary low-lubricant condition in the compression mechanism 120. At least due to the increased pumping speed, a larger volume of lubricant can be pumped into the compressor, and the volume and L2 are expected to decrease until a new equilibrium is reached between the volume of lubricant pumped into the compression mechanism and the amount of lubricant returning from the compression mechanism. When L2 is expected to decrease, L2 reaches L... 2min Previously, the lubricant tank valve could be opened at 416, allowing lubricant in the first lubricant tank 110 to flow from the first lubricant tank 100 to the second lubricant tank 112 to compensate for the expected decrease. The first lubricant tank 110 is capable of supplying lubricant until the lubricant level in the second lubricant tank 112 reaches a predetermined desired level.

[0081] In another example, when the compressor operates at the second speed and then reduces the speed to the first speed, the compression mechanism draws a smaller volume of lubricant into the compression mechanism, and L2 is expected to increase. Therefore, the lubricant reservoir valve 152 can remain closed at 414 to prevent L2 from increasing to an undesirable high level.

[0082] At 418, sensor 160b in intermediate pressure chamber 106 detects lubricant level L2 and sends it to controller 161. Then, method 400 proceeds to 420.

[0083] At 420, controller 161 sets the lubricant level L2 and L... 2min A comparison is made. When controller 161 determines that L2 is higher than L... 2min When the controller 161 determines that L2 is equal to or lower than L, the process proceeds to step 422. 2min If so, the method proceeds to step 424.

[0084] At 422, controller 161 instructs lubricant reservoir valve 152 to maintain its previous state. If lubricant reservoir valve 152 is closed at 414, it is instructed to remain closed. If lubricant reservoir valve 152 is open at 416, it is instructed to remain open. Then, method 400 returns to 418.

[0085] At 424, controller 161 instructs lubricant reservoir valve 152 to open or remain open, allowing lubricant to flow from the first lubricant reservoir 110 to the second lubricant reservoir 112 through lubricant supply passage 150. If lubricant reservoir valve 152 is closed at 414, it is instructed to open. If lubricant reservoir valve 152 is open at 416, it is instructed to remain open. Lubricant will naturally flow from the first lubricant reservoir 110 to the second lubricant reservoir 112 due to the pressure (P) within discharge chamber 104. D The pressure is higher than that inside the intermediate pressure chamber 106 (P). I Then, method 400 proceeds to 426.

[0086] At 426, sensor 160b in intermediate pressure chamber 106 detects lubricant level L2 and sends it to controller 161. Then, method 400 proceeds to 428.

[0087] At 428, controller 161 sets the lubricant level L2 against a predetermined maximum lubricant level threshold L. 2max A comparison is made. When controller 161 determines that L2 is lower than L... 2max When the controller 161 determines that L2 is equal to or greater than L, the process proceeds to step 430. 2max If so, the method proceeds to step 432. In one embodiment, L 2maxThis is the liquid level at which the compressor can operate normally without damaging the compressor mechanism, for example, by flooding the internal mechanisms of the compressor with lubricant.

[0088] At 430, controller 161 instructs lubricant reservoir valve 152 to remain open. Then, method 400 returns to 426.

[0089] At 432, controller 161 instructs lubricant tank valve 152 to close, thereby stopping the flow of lubricant from the first lubricant tank 110 to the second lubricant tank 112. The method then proceeds to 418.

[0090] Method 400 can be performed continuously while the compressor is operating, and / or it can be performed for a predetermined period of time after the compressor is turned off. For example, when the compressor is turned off, method 400 can be performed to allow the reservoir to be balanced through valve 150.

[0091] It should be understood that method 400 is shown for illustrative purposes only, and the methods for controlling the flow rate of lubricant through lubricant supply passage 150 are not limited to these examples. It should be understood that the flow rate can be controlled according to various operating conditions of the compressor and the working fluid circuit used by compressor 100.

[0092] aspect

[0093] It should be noted that any one of aspects 1 to 9 may be combined with aspects 10 to 15, 16 to 18, or any one or more of both. Any one of aspects 10 to 15 may be combined with any one of aspects 16 to 18.

[0094] Aspect 1. A compressor, comprising: a compressor housing; a discharge chamber and an intermediate pressure chamber, each disposed within the compressor housing, the discharge chamber having a first lubricant reservoir and the intermediate pressure chamber having a second lubricant reservoir; an inlet and an outlet formed within the compressor housing; a compression mechanism disposed within the compressor housing, the compression mechanism being configured to draw in working fluid from the inlet and discharge the working fluid into the discharge chamber, the compression mechanism including an intermediate injection port fluidly connected to the intermediate pressure chamber; and a lubricant supply passage extending from the discharge chamber to the intermediate pressure chamber, the lubricant supply passage including a lubricant reservoir valve configured to control the flow of lubricant through the lubricant supply passage from the first lubricant reservoir in the discharge chamber to the second lubricant reservoir in the intermediate pressure chamber, wherein the lubricant in the second lubricant reservoir is supplied at least to the compression mechanism.

[0095] Aspect 2, the compressor according to aspect 1, wherein the lubricant supply passage includes a lubricant cooler configured to cool the lubricant flowing through the lubricant supply passage.

[0096] Aspect 3. The compressor according to any one of aspects 1 to 2, further comprising: a lubricant tank sensor and a controller, the lubricant tank sensor being configured to detect the lubricant level in the second lubricant tank, wherein the lubricant tank sensor is configured to send the lubricant level in the second lubricant tank to the controller, and the controller is configured to control the lubricant tank valve based on the lubricant level in the second lubricant tank to adjust the flow of the lubricant through the lubricant supply passage.

[0097] Aspect 4, the compressor according to any one of aspects 1 to 3, further includes a lubricant pump configured to deliver lubricant from the second lubricant tank to the compression mechanism.

[0098] Aspect 5: The compressor according to any one of aspects 1 to 4 further includes an intermediate steam injection inlet fluidly connected to the intermediate pressure chamber.

[0099] Aspect 6. The compressor according to any one of aspects 1 to 5, further comprising: a third lubricant tank disposed in the intermediate pressure chamber above the second lubricant tank; a second lubricant pump configured to deliver lubricant from the second lubricant tank to the third lubricant tank; and a drive shaft including a first end coupled to the compression mechanism, a second end disposed in the third lubricant tank, and a lubricant passage, wherein lubricant in the third lubricant tank is supplied to the compression mechanism via the lubricant passage by rotation of the drive shaft.

[0100] Aspect 7. The compressor according to any one of aspects 1 to 6 further includes a third lubricant tank sensor configured to detect the lubricant level in the third lubricant tank, wherein the second lubricant pump is configured to operate based on the lubricant level in the third lubricant tank in order to maintain the lubricant level in the third lubricant tank.

[0101] Aspect 8: The compressor according to any one of aspects 1 to 7, wherein the compressor is a horizontal compressor, and wherein the discharge chamber and the intermediate pressure chamber are arranged horizontally side by side.

[0102] Aspect 9. The compressor according to any one of aspects 1 to 7, wherein the compressor is a vertical compressor, and wherein the discharge chamber and the intermediate pressure chamber are arranged vertically side by side.

[0103] Aspect 10. A heating, ventilation, air conditioning, and refrigeration (HVACR) system, comprising: a working fluid circuit including: a compressor, a condenser, at least one expander, and an evaporator fluidly connected, wherein a working fluid flows through the compressor, the condenser, the at least one expander, and the evaporator, wherein the compressor includes: a compressor housing; a discharge chamber and an intermediate pressure chamber, each disposed within the compressor housing, the discharge chamber having a first lubricant reservoir and the intermediate pressure chamber having a second lubricant reservoir; an inlet and an outlet, the inlet and the outlet being formed within the compressor housing. The compressor includes a compression mechanism disposed within the compressor housing, the compression mechanism being configured to draw in working fluid from the suction port and discharge the working fluid into the discharge chamber, the compression mechanism including an intermediate injection port fluidly connected to the intermediate pressure chamber; and a lubricant supply passage extending from the discharge chamber to the intermediate pressure chamber, the lubricant supply passage including a lubricant reservoir valve configured to control the flow of lubricant through the lubricant supply passage from a first lubricant reservoir in the discharge chamber to a second lubricant reservoir in the intermediate pressure chamber, wherein the lubricant in the second lubricant reservoir is supplied at least to the compression mechanism.

[0104] Aspect 11. The system according to aspect 10, wherein the compressor further includes a lubricant cooler configured to cool the lubricant flowing through the lubricant supply passage.

[0105] Aspect 12. The system according to any one of aspects 10 to 11, wherein the compressor further comprises: a lubricant tank sensor and a controller, the lubricant tank sensor being configured to detect the lubricant level in the second lubricant tank, wherein the lubricant tank sensor is configured to send the lubricant level in the second lubricant tank to the controller, and the controller is configured to control the lubricant tank valve based on the lubricant level in the second lubricant tank to adjust the flow of lubricant through the lubricant supply channel.

[0106] Aspect 13. The system according to any one of aspects 10 to 12, wherein the system further includes an intermediate vapor injection line fluidly connected to the intermediate pressure chamber, and the compressor further includes an intermediate vapor injection inlet fluidly connected to the intermediate pressure chamber.

[0107] Aspect 14. The system according to any one of aspects 10 to 13, wherein the compressor is a horizontal compressor, and wherein the discharge chamber and the intermediate pressure chamber are arranged horizontally side by side.

[0108] Aspect 15. The system according to any one of aspects 10 to 13, wherein the compressor is a vertical compressor, and wherein the discharge chamber and the intermediate pressure chamber are arranged vertically side by side.

[0109] Aspect 16. A method of operating a compressor, comprising: using a motor to drive a compression mechanism to draw working fluid into the compressor via an inlet, compressing the working fluid into a compressed working fluid, and discharging the compressed working fluid from the compressor via an outlet, the compressor comprising a compressor housing having the inlet and the outlet, a discharge chamber having a first lubricant tank disposed within the compressor housing, and an intermediate pressure chamber having a second lubricant tank disposed within the compressor housing; injecting intermediate pressure working fluid from the intermediate pressure chamber into the compression mechanism, the intermediate pressure working fluid being compressed by the compression mechanism and discharged as part of the compressed working fluid; and guiding lubricant from the first lubricant tank in the discharge chamber to the second lubricant tank in the intermediate pressure chamber via a lubricant supply passage extending from the discharge chamber to the intermediate pressure chamber, including detecting a lubricant level in the second lubricant tank and controlling the flow rate of lubricant through the lubricant supply passage via a lubricant tank valve.

[0110] Aspect 17. The method according to aspect 16 further includes: operating the compressor at a first speed; and switching the speed from the first speed to a second speed that is faster than the first speed, wherein when operating at the second speed, the flow rate of lubricant through the lubricant supply passage increases relative to when operating at the first speed.

[0111] Aspect 18, the method according to any one of aspects 16 to 17, further comprising: using a lubricant heat exchanger to cool the lubricant in the lubricant supply channel flowing from the first lubricant tank to the second lubricant tank.

[0112] The terminology used in this specification is intended to describe particular embodiments and is not intended to be limiting. Unless expressly indicated otherwise, the terms “a,” “an,” and “the” also include the plural forms. When used in this specification, the terms “comprises” and / or “comprising” specify the presence of the stated features, integers, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, and / or components.

[0113] Regarding the foregoing description, it should be understood that detailed changes can be made without departing from the scope of this disclosure, particularly in terms of the construction materials used and the shape, size, and arrangement of components. This specification and the described embodiments are merely exemplary, and the true scope and spirit of this disclosure are indicated by the appended claims.

Claims

1. A compressor, comprising: Compressor housing; The compressor housing includes a discharge chamber and an intermediate pressure chamber, each disposed within the compressor housing. The discharge chamber has a first lubricant tank, and the intermediate pressure chamber has a second lubricant tank. An intake port and an outlet port are formed within the compressor housing; A compression mechanism disposed within the compressor housing is configured to draw in working fluid from the suction port and discharge the working fluid into the discharge chamber, the compression mechanism including an intermediate injection port fluidly connected to the intermediate pressure chamber; as well as A lubricant supply channel extends from the discharge chamber to the intermediate pressure chamber. The lubricant supply channel includes a lubricant reservoir valve configured to control the flow of lubricant through the lubricant supply channel from the first lubricant reservoir to the second lubricant reservoir. The lubricant in the second lubricant tank is supplied to at least the compression mechanism.

2. The compressor of claim 1, wherein, The lubricant supply channel includes a lubricant cooler configured to cool the lubricant flowing through the lubricant supply channel.

3. The compressor according to claim 1, further comprising: A lubricant tank sensor and controller, wherein the lubricant tank sensor is configured to detect the lubricant level in the second lubricant tank. The lubricant tank sensor is configured to send the lubricant level in the second lubricant tank to the controller, and the controller is configured to control the lubricant tank valve based on the lubricant level in the second lubricant tank in order to adjust the flow of lubricant through the lubricant supply channel.

4. The compressor according to claim 1, further comprising: A lubricant pump is configured to deliver lubricant from the second lubricant tank to the compression mechanism.

5. The compressor according to claim 1, further comprising an intermediate steam injection inlet fluidly connected to the intermediate pressure chamber.

6. The compressor according to claim 1, further comprising: The third lubricant tank is located in the medium-pressure chamber, above the second lubricant tank; A second lubricant pump is configured to deliver lubricant from the second lubricant tank to the third lubricant tank; as well as The drive shaft includes a first end connected to the compression mechanism, a second end disposed in the third lubricant tank, and a lubricant passage, wherein lubricant in the third lubricant tank is supplied to the compression mechanism through the lubricant passage by means of the rotation of the drive shaft.

7. The compressor of claim 6, further comprising a third lubricant tank sensor configured to detect the lubricant level in the third lubricant tank. wherein, The second lubricant pump is configured to operate based on the lubricant level in the third lubricant tank in order to maintain the lubricant level in the third lubricant tank.

8. The compressor according to any one of claims 1 to 7, wherein, The compressor is a horizontal compressor, wherein the discharge chamber and the intermediate pressure chamber are arranged horizontally side by side.

9. The compressor according to any one of claims 1 to 7, wherein, The compressor is a vertical compressor, wherein the discharge chamber and the intermediate pressure chamber are arranged vertically side by side.

10. A heating, ventilation, air conditioning and cooling (HVACR) system, comprising: The working fluid circuit includes: A compressor, a condenser, at least one expander, and an evaporator are fluidly connected, wherein a working fluid flows through the compressor, the condenser, the at least one expander, and the evaporator. The compressor includes: Compressor housing; The compressor housing includes a discharge chamber and an intermediate pressure chamber, each disposed within the compressor housing. The discharge chamber has a first lubricant tank, and the intermediate pressure chamber has a second lubricant tank. An intake port and an outlet port are formed within the compressor housing; A compression mechanism, disposed within the compressor housing, is configured to draw in working fluid from the suction inlet and discharge the working fluid into the discharge chamber. The compression mechanism includes an intermediate injection port fluidly connected to the intermediate pressure chamber. A lubricant supply channel extending from the discharge chamber to the intermediate pressure chamber includes a lubricant reservoir valve configured to control the flow of lubricant through the lubricant supply channel from a first lubricant reservoir in the discharge chamber to a second lubricant reservoir in the intermediate pressure chamber. The lubricant in the second lubricant tank is supplied to at least the compression mechanism.

11. The system according to claim 10, wherein, The compressor further includes a lubricant cooler configured to cool the lubricant flowing through the lubricant supply passage.

12. The system according to claim 10, wherein, The compressor further includes a lubricant tank sensor and a controller, the lubricant tank sensor being configured to detect the lubricant level in the second lubricant tank. The lubricant tank sensor is configured to send the lubricant level in the second lubricant tank to the controller, and the controller is configured to control the lubricant tank valve based on the lubricant level in the second lubricant tank in order to adjust the flow of lubricant through the lubricant supply channel.

13. The system according to claim 10, wherein, The system further includes an intermediate vapor injection line fluidly connected to the intermediate pressure chamber, and the compressor further includes an intermediate vapor injection inlet fluidly connected to the intermediate pressure chamber.

14. The system according to any one of claims 10 to 13, wherein, The compressor is a horizontal compressor, wherein the discharge chamber and the intermediate pressure chamber are arranged horizontally side by side.

15. The system according to any one of claims 10 to 13, wherein, The compressor is a vertical compressor, wherein the discharge chamber and the intermediate pressure chamber are arranged vertically side by side.

16. A method for operating a compressor, comprising: A motor drives a compression mechanism to draw working fluid into the compressor via an inlet, compress the working fluid into a compressed working fluid, and discharge the compressed working fluid from the compressor via an outlet. The compressor includes a compressor housing having the inlet and the outlet, a discharge chamber having a first lubricant tank disposed within the compressor housing, and an intermediate pressure chamber having a second lubricant tank disposed within the compressor housing. Medium-pressure working fluid is injected from the medium-pressure chamber into the compression mechanism, the medium-pressure working fluid is compressed by the compression mechanism and discharged as part of the compressed working fluid; and Lubricant is guided from the first lubricant tank in the discharge chamber to the second lubricant tank in the intermediate pressure chamber via a lubricant supply channel extending from the discharge chamber to the intermediate pressure chamber, including detecting the lubricant level in the second lubricant tank and controlling the flow rate of lubricant through the lubricant supply channel via a lubricant tank valve.

17. The method of claim 16, further comprising: The compressor is operated at a first speed; and Switch the speed from the first speed to a second speed that is faster than the first speed. Specifically, when the compressor is operated at the second speed, the flow rate of lubricant through the lubricant supply channel increases compared to when the compressor is operated at the first speed.

18. The method according to claim 16 or 17, further comprising: The lubricant in the lubricant supply channel flowing from the first lubricant tank to the second lubricant tank is cooled using a lubricant heat exchanger.

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