Patent Application
20240318880
The field of the disclosure relates generally to refrigeration systems, and more particularly, to providing cooling to a compressor within a refrigeration system using a refrigerant drawn from a high pressure side of the refrigeration system.
Dynamic compressors, including centrifugal compressors, are commonly used in process industries and in heating, ventilation, and air conditioning (HVAC) systems. The compressor is typically connected to a motor via a shaft that supports multiple compression stages. A drive controls the motor to rotate the compression stages at a rotational speed and loading condition selected to compress a refrigerant to a specified demand. The motor speed and load may be controlled to operate the compressor under a wide range of operating conditions.
During operation, the drive, motor, and compressor bearings may reach high temperatures that, if left unaddressed, may increase the risk of mechanical failure due to overheating. Existing cooling systems may divert relatively low temperature refrigerant from the main refrigeration circuit for use as a coolant for cooling components of the compressor. The coolant is channeled through a housing of the compressor where it provides cooling to the components of the compressor. The coolant is then channeled towards a low pressure side of the compressor where the coolant mixes with low pressure refrigerant entering the compressor via a suction line of the main refrigeration circuit. The low pressure refrigerant and the coolant are channeled through the compression stages and simultaneously compressed.
In some known systems, the coolant is diverted from a high pressure side of the main refrigeration circuit (e.g., from a portion between a condenser and an expansion valve). Using refrigerant drawn from the high pressure side of the main refrigeration circuit as the coolant creates the opportunity for disturbing the flow of low pressure refrigerant that enters the low pressure side of the compressor via the main refrigeration circuit. This may degrade the performance, efficiency, and/or longevity of the compressor. Thus, there is a need for a compressor system that facilitates using coolant drawn from a high pressure side of a refrigeration system for cooling the compressor while also facilitating reducing or eliminating the opportunity for the coolant to disturb the flow of refrigerant at the low pressure side of the compressor.
This section is intended to introduce the reader to various aspects of art that may be related to various aspects of the disclosure, which are described and/or claimed below. This discussion is believed to be helpful in providing the reader with background information to facilitate a better understanding of the various aspects of the present disclosure. Accordingly, it should be understood that these statements are to be read in this light, and not as admissions of prior art.
One aspect is a refrigeration system that includes a compressor, an evaporator, a condenser, an expansion device, and a cooling circuit. The compressor includes a housing, a shaft rotatably supported in the housing, an impeller connected to the shaft, and a motor operably connected to the shaft. The evaporator is connected to a low pressure line of the compressor. The cooling circuit includes at least one coolant supply line to channel a coolant from one of the condenser and a refrigerant line connected between the condenser and the expansion device towards the housing, at least one coolant flow channel defined by the housing that receives the coolant from the at least one coolant supply line and channels the coolant towards the motor, a coolant return line to channel the coolant from the at least one coolant flow channel towards the low pressure line of the compressor, and a damping chamber located between the coolant return line and the low pressure line of the compressor. The damping chamber includes a damping chamber inlet connected to the coolant return line to allow the coolant to enter a damping chamber volume from the coolant return line, and damping chamber outlets connected to the low pressure line of the compressor to allow the coolant in the damping chamber volume to enter the low pressure line of the compressor.
Another aspect is a compressor system that includes a compressor and a cooling circuit. The compressor includes a housing defining a compressor inlet, a shaft rotatably supported in the housing, an impeller connected to the shaft, and a motor operably connected to the shaft. The housing has a passage extending between the compressor inlet and the impeller. The cooling circuit includes at least one coolant flow channel defined by the housing to receive a coolant and channel the coolant towards the motor, a coolant return line to channel the coolant from the at least one coolant flow channel towards the passage, and a damping chamber located between the coolant return line and the passage. The damping chamber includes a damping chamber inlet connected to the coolant return line to allow the coolant to enter a damping chamber volume from the coolant return line, and damping chamber outlets connected to the passage to allow the coolant in the damping chamber volume to enter the passage at discrete angular flow directions.
Another aspect is a method of operating a refrigeration system. The refrigeration system includes a compressor, an evaporator, a condenser, and an expansion device. The compressor includes a housing, a shaft rotatably supported in the housing, an impeller connected to the shaft, and a motor operably connected to the shaft. The method includes compressing a refrigerant using the compressor to produce compressed refrigerant, condensing the compressed refrigerant using the condenser to produce compressed, condensed refrigerant, expanding a first portion of the compressed, condensed refrigerant using the expansion device to produce uncompressed, condensed refrigerant, vaporizing the uncompressed, condensed refrigerant using the evaporator to produce uncompressed, vapor refrigerant, and channeling the uncompressed, vapor refrigerant towards a low pressure line of the compressor. The method also includes diverting a second portion of the compressed, condensed refrigerant towards the housing of the compressor to provide cooling to the motor, channeling the second portion of the compressed, condensed refrigerant towards the low pressure line of the compressor, and mixing the second portion of the compressed, condensed refrigerant with the uncompressed, vapor refrigerant within the low pressure line of the compressor. Mixing the second portion of the compressed, condensed refrigerant and the uncompressed, vapor refrigerant within the low pressure line of the compressor includes intersecting the uncompressed, vapor refrigerant with the second portion of the compressed, condensed refrigerant at discrete angular flow directions within the low pressure line.
Various refinements exist of the features noted in relation to the above-mentioned aspects of the present disclosure. Further features may also be incorporated in the above-mentioned aspects of the present disclosure as well. These refinements and additional features may exist individually or in any combination. For instance, various features discussed below in relation to any of the illustrated embodiments of the present disclosure may be incorporated into any of the above-described aspects of the present disclosure, alone or in any combination.
The following figures illustrate various aspects of the disclosure.
Corresponding reference characters indicate corresponding parts throughout the drawings.
Examples are described with respect to a centrifugal compressor but may be applicable to other types of compressors. The bearings, motor, and drive of a dynamic compressor may be cooled using a coolant. The coolant is drawn from a high pressure side of a main refrigeration circuit (e.g., a refrigeration loop used in a heating, ventilation, and air conditioning (HVAC) system). The coolant is channeled from the high pressure side of the main refrigeration circuit towards and through a housing of the compressor to provide cooling to components housed therein. The coolant is then channeled into a damping chamber prior to entering a low pressure line of the compressor. The damping chamber includes a damping chamber inlet that allows the coolant to enter a damping chamber volume and damping chamber outlets connected to the low pressure line to allow the coolant in the damping chamber volume to enter the low pressure line. Flow of the coolant into the low pressure line is distributed across the damping chamber outlets which are suitably configured (e.g., sized, shaped, and positioned) such that the coolant enters the low pressure line at multiple (i.e., two or more) discrete angular flow directions. Distributing the flow of the coolant into the low pressure line across the damping chamber outlets facilitates reducing or eliminating the ability of the coolant, which intersects the main refrigerant flowing through the low pressure line, to disturb the main refrigerant flow (e.g., to create a turbulent flow within the low pressure line). This facilitates improving the performance, efficiency, and longevity of the compressor.
In operation, the compressor 102 receives a working fluid, such as a refrigerant, as a low pressure gas through a suction line 110. The compressor 102 compresses the low pressure refrigerant gas, thereby raising the temperature and pressure of the refrigerant. The compressed, high temperature refrigerant exiting the compressor 102 is channeled towards and passes through the condenser 104, where the refrigerant is condensed to a high pressure liquid or a high pressure liquid-gas mixture. The compressed, condensed refrigerant exiting the condenser 104 is channeled towards and passes through the expansion device 106 that expands the refrigerant, thereby reducing the pressure of the refrigerant. The expanded (or “uncompressed”) refrigerant exiting the expansion device 106 may be a gas or a mixture of gas and liquid after passing through the expansion device 106. The uncompressed refrigerant exiting the expansion device 106 is channeled towards and passes through the evaporator 108. The evaporator 108 may include a heat exchanger, with a relatively high temperature fluid circulating therethrough that is cooled by the uncompressed refrigerant fluid. The uncompressed refrigerant fluid evaporates to a gas in the evaporator 108. The uncompressed refrigerant gas exiting the evaporator 108 is channeled back towards the compressor 102 via the suction line 110, where the working fluid is again compressed and the process repeats.
The example refrigeration system 100 includes a compressor cooling system 112 that draws working fluid (e.g., refrigerant) from part of the main refrigeration circuit (i.e., the refrigeration loop in which the working fluid is compressed using the compressor 102, condensed using the condenser 104, expanded using the expansion device 106, and evaporated using the evaporator 108). The working fluid used in the cooling system 112 is diverted from the main refrigeration circuit and channeled through a coolant supply line 116 towards the compressor 102 to cool components of the compressor 102, such as a motor and bearings of the compressor 102. The working fluid used in the cooling system 112 may also be referred to herein as “coolant.” The coolant is returned to the refrigeration circuit by a coolant return line 114 that channels the coolant towards a low pressure line 120 of the compressor 102. As used herein, “low pressure line” of a compressor (e.g., the compressor 102) refers to a refrigerant flow channel within the compressor or the main refrigeration circuit of which the compressor 102 is a part that precedes and channels refrigerant towards one or more impellers in the compression stages of the compressor (e.g., a first stage impeller of the compressor). The low pressure line 120 of the compressor 102 may include, for example and without limitation, a passage extending between an inlet of a first stage of the compressor 102 and a first stage impeller, the first stage inlet of the compressor 102, and the suction line 110 (e.g., the suction line 110) connected to the first stage inlet of the compressor 102.
The coolant used in the cooling system 112 is suitably drawn from a low temperature, high pressure side of the main refrigeration circuit downstream from the condenser 104 and upstream from the expansion device 106 (i.e., from a refrigerant line 122 connected between the condenser 104 and the expansion device 106), or, alternatively, from the condenser 104. Drawing the coolant from the main refrigeration circuit at this stage provides several advantages. The pressure differential across the cooling circuit 204 of the cooling system 112, i.e., the pressure differential between the high pressure refrigerant exiting the condenser 104 and the low pressure refrigerant entering the compressor 102 via the suction line 110, facilitates driving the coolant through the compressor 102, and back into the refrigeration circuit. The relatively low temperature refrigerant exiting the condenser 104, compared to a temperature of the refrigerant at downstream stages of the main refrigeration circuit (e.g., exiting the evaporator 108 and/or the expansion device 106), facilitates increasing the cooling capacity of the cooling system 112.
Using refrigerant from the high pressure side of the main refrigeration circuit as the coolant may create the opportunity to disturb the flow of the low pressure refrigerant of the main refrigeration circuit entering the compressor 102 via the suction line 110. Conventionally, the coolant enters the low pressure line 120 of the compressor 202 via a single outlet connecting the coolant return line 114 and the low pressure line 120. The coolant is drawn into the low pressure line 120 by a pressure differential between the coolant return line 114 and the low pressure line 120, and/or by a suction between the coolant return line 114 and the low pressure line 120 from the low pressure refrigerant flowing through the low pressure line 120. The coolant entering the low pressure line 120 via the single outlet intersects the low pressure refrigerant flowing through the low pressure line 120 at a single angular flow direction. The coolant intersecting the low pressure refrigerant at the single angular flow direction disturbs the flow of the low pressure refrigerant entering the compressor 102 and, thus, the flow of the refrigerant through the compressor 102. The performance, efficiency, and longevity of the compressor 102 may be substantially degraded by disturbances in the flow of the refrigerant through the compressor 102. For example, disturbances in the refrigerant flow may negatively impact a direction of the refrigerant flow contacting an impeller of the compressor 102. The direction of refrigerant flow may be controlled using inlet guide vanes positioned within the compressor 102 upstream from the impeller, however, the disturbances caused by the coolant intersecting the low pressure refrigerant at the single angular flow direction may substantially reduce the effectiveness of the guide vanes, particularly where the coolant enters the compressor 102 downstream from the inlet guide vanes.
Accordingly, still referring to
The compressor 202 in the example shown in
The compressor 202 includes a housing 216, a shaft 218 rotatably supported in the housing 216. The shaft 218 may be supported in the housing 216 by bearings 220, 222, 224. Alternatively, the shaft 218 may be supported without the use of the bearings 220, 222, and/or 224. The compressor 202 also includes a first stage impeller 226 connected to a first end 228 of the shaft 218, a second stage impeller 230 connected to a second end 232 of the shaft 218, and a motor 234 operably connected to the shaft 218 to drive rotation thereof. The compressor 202 may include components in addition to those shown in
The housing 216 encloses components of the compressor 202 within one or more sealed (e.g., hermetically or semi-hermitically) cavities. In some embodiments, for example, the housing 216 includes end caps at each stage of the compressor 202 that define volutes in which the first and second stage impellers 226, 230 are positioned. In some embodiments, the housing 216 is formed from cast pieces that are assembled using suitable fasteners (e.g., screws, bolts, etc.).
The bearings 220, 222, 224 may rotatably support the shaft 218 within the housing 216. In the example shown in
The motor 234 is operably connected to the shaft 218 to drive rotation thereof during operation of the compressor 202. The motor 234 may include any suitable motor that enables the compressor 202 to function as described herein. In the illustrated embodiment, the motor 234 is an electric motor and includes suitable components (e.g., a stator and a rotor) to impart rotational motion to the shaft 218 during operation of the compressor 202.
The housing 216 has coolant flow channels 236, 238, 240, 242 defined therein that channel coolant towards the bearings 220, 222, 224 and the motor 234. The coolant flow channels 236, 238, 240, 242 may be arranged and/or defined within the compressor housing 216 in any manner that enables the compressor system 200 to function as described herein. For example, the coolant flow channels 236, 238, 240, 242 may be formed as passages in components (e.g., cast components, as by machining, for example) of the compressor housing 216, as passages defined between two or more components of the compressor 202 (e.g., between the motor 234 and the compressor housing 216), and combinations thereof.
The example compressor 202 includes a first coolant flow channel 236, a second coolant flow channel 238, a third coolant flow channel 240, and a fourth coolant flow channel 242. The first coolant flow channel 236 delivers coolant to the thrust bearing 224, the second coolant flow channel 238 delivers coolant to the first radial bearing 220, the third coolant flow channel 240 delivers coolant to the second radial bearing 222, and the fourth coolant flow channel 242 delivers coolant to the motor 234. In some embodiments, the coolant flow channels 236, 238, 240, 242 may share common or overlapping portions. For example, as shown in
Each of coolant flow channels 236, 238, 240, 242 has a corresponding coolant inlet port 244 that connects to the cooling circuit 204 in the example embodiment. That is, the compressor housing 216 includes four external inlet connections for respectively connecting the coolant flow channels 236, 238, 240, 242 with coolant supply lines 248, 250, 252, 254. The compressor housing 216 may alternatively have fewer external inlet connections. For example, two or more of the coolant flow channels 236, 238, 240, 242 may share a common, single coolant inlet port (and a common connection point to one or more coolant supply lines) that provides coolant to multiple of the coolant flow channels 236, 238, 240, 242. In such examples, coolant flow delivered to the common coolant inlet port may be separated, divided, or otherwise routed within the compressor housing 216 to deliver coolant to two or more of the coolant flow channels 236, 238, 240, 242. In some embodiments, for example, the bearing coolant flow channels (i.e., the first, second, and third coolant flow channels 236, 238, 240) may have a common coolant inlet port, and the coolant flow may be routed to the separate flow channels internally within the compressor housing 216.
The compressor housing 216 also defines a common coolant outlet port 246. The common coolant outlet port 246 receives coolant from each of the coolant flow channels 236, 238, 240, 242. Alternatively stated, all the coolant channeled towards the compressor housing 216 and through the coolant flow channels 236, 238, 240, 242 is returned to the common coolant outlet port 246. In some embodiments, at least one of the coolant flow channels 236, 238, 240 is arranged such that coolant flows through at least one coolant flow channel, in series, across at least one of the bearings 220, 222, 224, through the motor 234, and to the common coolant outlet port 246. In this way, coolant flowing through the at least one coolant flow channel absorbs heat from both the motor 234 and one of the bearings 220, 222, 224. Coolant may flow through the motor 234, for example, by flowing between a stator and a rotor of the motor 234, through a portion of the shaft 218 around which the motor 234 is positioned, and/or through flow channels or holes defined in the rotor of the motor 234.
The cooling circuit 204 channels coolant towards the compressor housing 216 and the coolant flow channels 236, 238, 240, 242 via the coolant supply lines 248, 250, 252, 254. The coolant supply lines 248, 250, 252, 254 are connected in fluid communication with a coolant source 262 and are connected to the compressor housing 216 via the inlets 244 to deliver coolant to the coolant flow channels 236, 238, 240, 242. The coolant supply lines 248, 250, 252, 254 may include any suitable fluid conduit (rigid and/or flexible) that facilitates channeling the coolant to the compressor housing 216 including, for example and without limitation, pipes, hoses, tubes, and combinations thereof. In some embodiments, the coolant supply lines 248, 250, 252, 254 are constructed of metal tubing, such as copper tubing. The example cooling circuit 204 includes four coolant supply lines 248, 250, 252, 254, one for each of the coolant flow channels 236, 238, 240, 242 defined within the compressor housing 216. More specifically, the example cooling circuit 204 includes bearing coolant supply lines 248, 250, 252 and a motor coolant supply line 254. Each of the bearing coolant supply lines 248, 250, 252 is connected to one of the first, second, and third coolant flow channels 236, 238, 240 to channel or deliver coolant to at least one of compressor bearings 220, 222, 224. The motor coolant supply line 254 is connected to the fourth coolant flow channel 242 to deliver coolant to the motor 234.
The example coolant source 262 is suitably part of a main refrigeration circuit of which the compressor 202 is a part (e.g., the main refrigeration circuit of the refrigeration system 100 shown in
Suitably, the coolant that is drawn from the coolant source 262 is driven through the cooling circuit 204 using a pressure differential between the coolant source 262 and a low pressure line upstream from the first stage impeller 226 of the compressor 202 (e.g., the first stage inlet 210, or the passage P extending between the first stage inlet 210 and the first stage impeller 226). The coolant may be driven by the pressure differential without the need for auxiliary equipment (e.g., a pump). In other examples, the coolant may be directed through the cooling circuit 204 using auxiliary equipment (e.g., a pump).
At least one of the coolant supply lines 248, 250, 252, 254 may include a coolant control valve 264 to control coolant flow through the corresponding coolant supply line. The control valve 264 may include an electrically-actuatable valve that is controllable by a controller 260 to vary or otherwise control the flow rate of coolant through the corresponding supply line. Suitable valves include, for example and without limitation, solenoid valves, electronic expansion valves, and modulating control valves. For example, the motor coolant supply line 254 includes the coolant control valve 264. Additionally and/or alternatively, one or more of the bearing coolant supply lines 248, 250, 252 may include a coolant control valve 264. For example, the motor coolant supply line 254 and one or more of the bearing coolant supply lines 248, 250, 252 may include a coolant control valve 264.
In the example shown in
The cooling circuit 204 also includes a main shutoff valve 274 on the main coolant supply line (i.e., the motor coolant supply line 254) to enable coolant flow to the entire cooling circuit 204 to be shut off in order to isolate the compressor 202 (e.g., for servicing the compressor 202). The main shutoff valve 274 may alternatively be omitted.
The bearing coolant supply lines 248, 250, 252 may be free of individual shutoff valves or other devices that would individually cut the supply of coolant through the bearing coolant supply lines 248, 250, 252, as shown in
The cooling circuit 204 also returns coolant from the coolant flow channels 236, 238, 240, 242 to the main refrigeration circuit (e.g., the main refrigeration circuit of the refrigeration system 100 shown in
The coolant return line 256 may include any suitable fluid conduit (rigid and/or flexible) that facilitates channeling coolant between the coolant flow channels 236, 238, 240, 242 towards the lower pressure side of the compressor 202. Suitable conduits include, for example and without limitation, pipes, hoses, tubes, and combinations thereof. For example, the coolant return line 256 may be a conduit that is constructed of metal tubing, such as copper tubing, or the coolant return line 256 may be a conduit that is constructed of other materials.
In the example shown in
An inlet 276 of the coolant return line 256 is connected to the common coolant outlet port 246, and an outlet 278 of the coolant return line 256 is connected to an inlet 284 of the damping chamber 205. The coolant return line 256 receives, via the inlet 276, coolant from each of the coolant flow channels 236, 238, 240, 242 after the coolant absorbs heat from the motor 234 and/or the bearings 220, 222, 224. As noted above, at least one of the coolant flow channels 236, 238, 240, 242 may be arranged such that coolant flows through the at least one coolant flow channel, in series, across at least one of the bearings 220, 222, 224, through the motor 234, and to the common coolant outlet port 246. For example, as shown in
The cooling circuit 204 may also include a temperature sensor 258 connected to the coolant return line 256 to detect at least one of a temperature of the coolant return line 256 and a temperature of coolant within the coolant return line 256. The temperature sensor 258 may include any suitable temperature sensor that enables the cooling circuit 204 to function as described herein, including, for example and without limitation, thermistors (e.g., a negative temperature coefficient thermistor), thermocouples, resistance temperature detectors (RTDs), thermal switches, and combinations thereof.
The temperature sensor 258 of the example shown in
The controller 260 is connected to the temperature sensor 258 and the coolant control valve 264 and is configured to control operation of the coolant control valve 264 (e.g., by opening, closing, or varying a position of the coolant control valve 264). In some embodiments, for example, the controller 260 is configured to control the coolant control valve 264 based on the temperature detected by the temperature sensor 258 to control the supply of coolant to the compressor housing 216. For example, the controller 260 may receive a signal from the temperature sensor 258 indicative of a temperature detected by the temperature sensor 258, compare the detected temperature to one or more temperature set points, and control the coolant control valve 264 based on the detected temperature. More specifically, based on the comparison, the controller 260 may be configured to open the coolant control valve 264, thereby permitting additional coolant flow through the motor coolant supply line 254 and to the motor 234, or close the coolant control valve 264, thereby reducing coolant flow through the motor coolant supply line 254 and to the motor 234. “Opening” and “closing” the coolant control valve 264 may refer to absolute opening and closing (i.e., completely opening and closing of the valve), or relative opening and closing of the valve (e.g., opening the valve more than it already is, or closing the valve more than it already is).
The controller 260 generally includes any suitable computer and/or other processing unit, including any suitable combination of computers, processing units and/or the like that may be communicatively connected to one another and that may be operated independently or in connection within one another (e.g., controller 260 may form all or part of a controller network). Controller 260 may include one or more modules or devices, one or more of which is enclosed within the compressor 202, or may be located remote from the compressor 202. The controller 260 may include one or more processor(s) 280 and associated memory device(s) 282 configured to perform a variety of computer-implemented functions (e.g., performing the calculations, determinations, and functions disclosed herein). As used herein, the term “processor” refers not only to integrated circuits, but also refers to a controller, a microcontroller, a microcomputer, a programmable logic controller (PLC), an application specific integrated circuit, and other programmable circuits. Additionally, memory device(s) 282 of controller 260 may generally be or include memory element(s) including, but not limited to, computer readable medium (e.g., random access memory (RAM)), computer readable non-volatile medium (e.g., a flash memory), a floppy disk, a compact disc-read only memory (CD-ROM), a magneto-optical disk (MOD), a digital versatile disc (DVD) and/or other suitable memory elements. Such memory device(s) 282 may generally be configured to store suitable computer-readable instructions that, when implemented by the processor(s), configure or cause controller 260 to perform various functions described herein including, but not limited to, controlling the coolant control valve 264 and/or various other suitable computer-implemented functions.
The controller 260 and/or components of the controller 260 may be integrated or incorporated within other components of the cooling circuit 204 and/or a refrigeration system within which the cooling circuit 204 is incorporated. For example, the controller 260 may be incorporated within the coolant control valve 264 and/or a system controller that controls other functions and operations of the compressor 202 and the refrigeration system.
The damping chamber 205 is located between the coolant return line 256 and the low pressure line (e.g., the passage P) of the compressor 202. The damping chamber 205 includes a damping chamber inlet 284 that is connected to the coolant return line outlet 278. The damping chamber 205 receives, via the damping chamber inlet 284, coolant from the coolant return line 256 that enters an interior volume V of the damping chamber 205. The damping chamber 205 also includes damping chamber outlets 286 connected to the low pressure line of the compressor 202 (e.g., the passage P). The coolant within the interior volume V of the damping chamber 205 exits the damping chamber 205 and enters the low pressure line (e.g., the passage P) of the compressor 202 via the damping chamber outlets 286.
In the example shown in
The damping chamber outlets 286 connect the damping chamber volume V with the passage P and are located at discrete angular positions spaced in a circumferential-direction around the passage P. The damping chamber outlets 286 facilitate distributing flow of the coolant entering the passage P such that the coolant intersects the low pressure refrigerant in the passage P at multiple (i.e., two or more) angular flow directions. The damping chamber outlets 286 may include two or more outlets 286, such as three, four, five, six, or greater than six outlets 286.
The damping chamber outlets 286 may each have the same shape and/or size, or a shape and/or size of the damping chamber outlets 286 may vary. For example, the damping chamber outlets 286 may have the same cross-sectional size and/or shape, or the damping chamber outlets 286 may have different cross-sectional sizes and/or shapes. Additionally and/or alternatively, the damping chamber outlets 286 may have the same or different geometrical shape. The damping chamber outlets 286 may have any suitable geometric shape, such as, for example, prismatic (e.g., cylindrical), bell-shaped, conical, parabolic, and other shapes. Additionally and/or alternatively, the damping chamber outlets 286 may have the same orientation and/or a different orientation relative to a central axis of the passage P (and/or relative to a flow direction of the low pressure refrigerant in the passage P). In some examples, as shown in
The damping chamber outlets 286 may be arranged in a staggered circumferential arrangement around the passage P, or the damping chamber outlets 286 may be aligned in a substantially circular circumferential arrangement around the passage P. The damping chamber outlets 286 may be arranged in any suitable formation to enable the damping chamber 205 to function as described herein. The damping chamber outlets 286 may be located in substantial axial alignment with the damping chamber inlet 284, or the damping chamber outlets 286 may be axially offset from the damping chamber inlet 284. For example, some or all the damping chamber outlets 286 may be located axially in closer proximity to the first stage inlet 210 than the damping chamber inlet 284, and/or some or all the damping chamber outlets 286 may be located axially in closer proximity to the first stage impeller 226 than the damping chamber inlet 284.
The damping chamber inlet 284 and the damping chamber outlets 286 may be formed as through-holes in components of the housing 216 that are spaced radially from one another and define the damping chamber volume V. Suitably, the damping chamber outlets 286 together define a cross-sectional area through which the coolant enters the passage P that is greater than or equal to a cross-sectional area defined by the damping chamber inlet 284 through which the coolant enters the damping chamber volume V. Thereby, back pressure to the coolant accumulating within the damping chamber volume V may be reduced or eliminated to enable the coolant to be driven into the passage P as described herein.
The coolant enters the volume V of the damping chamber 205 via the damping chamber inlet 284 and accumulates within the damping chamber volume V. The coolant within the damping chamber volume V is driven through the damping chamber outlets 286 and into the passage P by a pressure differential between the coolant and the low pressure refrigerant flowing through the passage P and/or by a suction at the damping chamber outlets 286 from the low pressure refrigerant flowing through the passage P. The damping chamber inlet 284 and the damping chamber outlets 286 are suitably sized to reduce or eliminate back pressure to the coolant accumulating in the damping chamber V such that the coolant is enabled to be driven into the passage P by the pressure differential and/or the suction. The coolant entering the passage P is distributed by the damping chamber outlets 286 to intersect the low pressure refrigerant flowing through the passage P at multiple discrete angular flow directions. Thereby, disturbances to the refrigerant flow through the passage P caused by the intersecting coolant are reduced or eliminated, which facilitates improving the performance, efficiency, and longevity of the compressor 202.
The compressor 300 includes a compressor housing 302 forming at least one sealed cavity within which each stage of refrigerant compression is accomplished. The compressor 300 includes a first refrigerant inlet 304 defined by the housing 302. The first refrigerant inlet 304 receives working fluid (e.g., low pressure refrigerant vapor) from a suction line 306 (e.g., the suction line 110 shown in
The compressor housing 302 includes a first housing end portion or cap 320 enclosing the first compression stage 308, and a second housing end portion or cap 322 enclosing the second compression stage 314. The first compression stage 308 and the second compression stage 314 are positioned at opposite ends of the compressor 300. The first and second compression stages 308, 314 may alternatively be located at the same end of the compressor 300. The first compression stage 308 includes a first impeller 324 configured to add kinetic energy to refrigerant entering via the first refrigerant inlet 304. The kinetic energy imparted to the refrigerant by the first impeller 324 is converted to increased refrigerant pressure (i.e., compression) as the refrigerant velocity is slowed upon transfer to a sealed cavity (e.g., a diffuser). The second compression stage 314 includes a second impeller 326 configured to add kinetic energy to refrigerant transferred from the first compression stage 308 entering via the second refrigerant inlet 316. The kinetic energy imparted to the refrigerant by the second impeller 326 is converted to increased refrigerant pressure (i.e., compression) as the refrigerant velocity is slowed upon transfer to a sealed cavity (e.g., a diffuser). Compressed refrigerant exits the second compression stage 314 via the second refrigerant exit 318.
The first impeller 324 and second impeller 326 are coupled at opposite ends of a driveshaft 328. The driveshaft 328 is operatively coupled to a motor 330 positioned within the housing 302 between the first impeller 324 and second impeller 326. The motor 330 operates to rotate the driveshaft 328 such that first impeller 324 and second impeller 326 are rotated at a rotation speed selected to compress the refrigerant to a pre-selected target (e.g., mass flow) exiting the second refrigerant exit 318. Any suitable motor may be incorporated into the compressor 300 including, but not limited to, an electrical motor. The example compressor 300 includes an electrical motor having a stator 332 connected to the compressor housing 302, and a rotor 334 connected to the driveshaft 328. An air gap (not labeled in
As shown in
The first coolant flow channel 342 extends radially inward through the housing 302 near the first housing end cap 320, around the thrust bearing 340, and axially along the driveshaft 328 towards the common coolant outlet port 350. The second coolant flow channel 344 extends radially inward through the housing 302 towards the first radial bearing 336, and axially along the first radial bearing 336 and the driveshaft 328 towards the common coolant outlet port 350. The third coolant flow channel 346 extends radially inward through the housing 302 to the second radial bearing 338, and axially along the second radial bearing 338 and the driveshaft 328 towards the common coolant outlet port 350. The fourth coolant flow channel 348 extends helically around the stator 332 through a spiral groove (not shown in
As shown in
A coolant return line 354 (shown schematically in dotted lines
The low pressure refrigerant vapor flowing through the low pressure line of the compressor 300 (e.g., the suction line 306, the first refrigerant inlet 304, and/or the passage P) is at a lower pressure than the coolant delivered to the compressor housing 302. Suitably, the coolant is sourced from a relatively high pressure side of a refrigeration system (e.g., the refrigeration system 100 shown in
The damping chamber 358 is located between the coolant return line 354 and the low pressure line of the compressor 300 (e.g., the suction line 306, the first refrigerant inlet 304, and/or the passage P). The damping chamber 358 includes the damping chamber inlet 360 that is connected to the coolant return line outlet 356. The damping chamber 358 receives, via the damping chamber inlet 360, coolant from the coolant return line 354 that enters an interior volume V of the damping chamber 358. The damping chamber 358 also includes damping chamber outlets 362 connected to the low pressure line. In the example compressor 300, the damping chamber outlets 362 are connected to the passage P. The coolant within the interior volume V of the damping chamber 358 exits the damping chamber 358 and enters the passage P via the damping chamber outlets 362.
In the example compressor 300, as shown in
The inner tube 368 surrounds and at least partially defines the passage P and includes the damping chamber outlets 362 formed therein. The damping chamber outlets 362 are connected with the passage P such that coolant exiting the damping chamber 358 via the outlets 362 enters the passage P. The damping chamber outlets 362 are located at discrete angular positions spaced in a circumferential-direction along the inner tube 368. The damping chamber outlets 362 facilitate distributing flow of the coolant entering the passage P such that the coolant intersects the low pressure refrigerant in the passage P at multiple (i.e., two or more) angular flow directions. The damping chamber outlets 362 may include two or more outlets 362, such as three, four, five, six, or greater than six outlets 362. For example, the damping chamber outlets 362 may be formed as an annular or semi-annular array of through-holes that extends circumferentially along the inner tube 368. As shown in
The damping chamber outlets 362 may each have the same shape and/or size, or a shape and/or size of the damping chamber outlets 362 may vary. For example, the damping chamber outlets 362 may have the same cross-sectional size and/or shape, or the damping chamber outlets 362 may have different cross-sectional sizes and/or shapes. Additionally and/or alternatively, the damping chamber outlets 362 may have the same or different geometrical shape. The damping chamber outlets 362 may have any suitable geometric shape, such as, for example, prismatic (e.g., cylindrical), bell-shaped, conical, parabolic, and other shapes. Additionally and/or alternatively, the damping chamber outlets 362 may have the same orientation and/or a different orientation relative to a central axis of the passage P (and/or relative to a flow direction of the low pressure refrigerant in the passage P). In some examples, as shown in
The outer tube 370 surrounds the interior volume V and the inner tube 368 and includes the damping chamber inlet 360 formed therein. In the example compressor 300, the damping chamber 358 includes a single damping chamber inlet 360. The damping chamber inlet 360 may alternatively include more than one inlet 360. The damping chamber inlet 360 may be formed as a through-hole in the outer tube 370. The damping chamber inlet 360 may be formed at any suitable location to facilitate connection with the outlet 356 of the coolant return line 354. In the example shown, the damping chamber inlet 360 is formed in the outer tube 370 to facilitate connection with the coolant return line 354 that extends at least partially external to the housing 302. In other examples, where the coolant return line 354 is defined by and extends within the housing 302, the damping chamber inlet 360 may be formed at another suitable location to facilitate connection with the outlet of the coolant return line 354. For example, the damping chamber inlet 360 may be formed in the inner flange 366.
Suitably, the damping chamber outlets 362 together define a cross-sectional area through which the coolant enters the passage P that is greater than or equal to a cross-sectional area defined by the damping chamber inlet 360 through which the coolant enters the damping chamber volume V. Thereby, back pressure to the coolant accumulating within the damping chamber volume V may be reduced or eliminated to enable the coolant to be driven into the passage P as described herein.
The damping chamber outlets 362 may be located in substantial axial alignment with the damping chamber inlet 360, or the damping chamber outlets 362 may be axially offset from the damping chamber inlet 360. For example, as shown in
The coolant enters the volume V of the damping chamber 358 via the damping chamber inlet 360 and accumulates within the damping chamber volume V. The coolant within the damping chamber volume V is driven through the damping chamber outlets 362 and into the passage P by a pressure differential between the coolant and the low pressure refrigerant flowing through the passage P and/or by a suction at the damping chamber outlets 362 from the low pressure refrigerant flowing through the passage P. The damping chamber inlet 360 and the damping chamber outlets 362 are suitably sized to reduce or eliminate back pressure to the coolant accumulating in the damping chamber V such that the coolant is enabled to be driven into the passage P by the pressure differential and/or the suction. The coolant entering the passage P is distributed by the damping chamber outlets 362 to intersect the low pressure refrigerant flowing through the passage P at multiple discrete angular flow directions. Thereby, disturbances to the refrigerant flow through the passage P caused by the intersecting coolant are reduced or eliminated, which facilitates improving the performance, efficiency, and longevity of the compressor 300.
As shown in
Referring now to
The compressor 400 includes a damping chamber 404 defined by a first housing end cap 402. The first housing end cap 402 is included with the compressor housing 302 and connected to a main body 374 thereof. The damping chamber also defines the first refrigerant inlet 304 of the compressor 400. The damping chamber 404 surrounds the passage P extending between the inlet 304 and the first impeller 324. In this example, the damping chamber 404 is defined axially downstream from the inlet 304. In addition, the first housing end cap 402 defines a portion of an inlet guide vane apparatus 500 (shown in
The first housing end cap 402 includes an annular flange 406 that defines a radially outermost portion of the end cap 402. The annular flange 406 is connected to the main body 374 of the compressor housing 302. The annular flange 406 includes holes 407 formed therein that align with corresponding holes 376 formed in the main housing body 374. The aligned end cap holes 407 and corresponding main body holes 376 receive fasteners 378 to connect the first housing end cap 402 with the main housing body 374.
The annular flange 406 extends radially outwardly from an annular sidewall 408 of the first housing end cap 402. The annular sidewall 408 extends axially from a shoulder 410 of the end cap 402. The end cap 402 is open at the end of the annular sidewall 408 opposite the shoulder 410. A recessed surface 416 that faces the main housing body 374 is defined by the shoulder 410 and extends radially between the annular sidewall 408 and an interior wall 422. The damping chamber volume V is defined by an interior surface 414 of the annular sidewall 408, the recessed surface 416, and an outer surface 426 of the interior wall 422. The shoulder 410 also defines an exterior surface 418 opposite the recessed surface 416. The end cap 402 also includes a neck portion 420 extending axially from the shoulder 410. The neck portion 420 has a smaller outer diameter than the annular sidewall 408. The shoulder 410 extends radially between and joins the neck portion 420 and the annular sidewall 408.
The end cap 402 includes the interior wall 422 that extends axially outwardly from the recessed surface 416. The interior wall 422 is spaced radially from the annular sidewall 408 to define the damping chamber volume V. The interior wall 422 also forms a portion of the inlet guide 500 that is defined by and made integral with the end cap 402. In particular, the interior wall 422 forms a second housing portion of the inlet guide 500 that is made integral with the end cap 402. The interior wall 422 may be made integral with the end cap 402 by manufacturing techniques including, but not limited to, casting, molding, powder metal manufacturing, additive manufacturing or 3D printing, and machining (e.g., computer numerical control machining). The end cap 402 and the interior wall 422 may be made from any suitable material including, for example, cast iron, aluminum, steel, and alloys thereof, as well as plastic, and any combination of these materials. The end cap 402 and the interior wall 422 may also be made from graphite or another suitable self-lubricating material that may be added to a casting or molding, for example. Making the end cap 402 and the interior wall 422 from a self-lubricating material may negate the need for a bearing in the inlet guide 500 (shown in
The end cap 402 also includes a central bore 430 that is defined by the neck portion 420 and the interior wall 422. The central bore 430 extends axially through the cap 402 and defines the first refrigerant inlet 304 of the compressor 400 and a boundary of the passage P. The interior wall 422 surrounds a portion of the passage P. As shown in
The inlet guide 500 is mounted in proximity to the refrigerant inlet 304 of the compressor 400. Low pressure refrigerant vapor is channeled towards the inlet guide 500 through the passage P and exits the inlet guide 500 with a suitable flow direction. The refrigerant is then channeled towards the first compression stage 308 (shown in
Additional features and elements of the inlet guide 500 will now be described with reference to
In addition to the housing portion 502 and the interior wall 422, the inlet guide 500 includes a ring gear 504 and guide vanes 506. The ring gear 504 is rotatably connected to the housing portion 502 and/or to the interior wall 422 and may be rotatably supported within the inlet guide 500 by a bearing 508. Each guide vane 506 is rotatable relative to the vane housing assembly of the inlet guide 500 and is operably connected to the ring gear 504 such that rotation of the ring gear 504 causes each of the guide vanes 506 to rotate in unison. Each of the guide vanes 506 is rotatable relative to the vane housing assembly of the inlet guide 500 such that the orientation of the guide vanes 506 within the passage P, defined by the housing portion 502 and the interior wall 422, is selectively adjustable. In some embodiments, the guide vanes 506 are rotatable relative to the vane housing assembly of the inlet guide 500 in unison. The inlet guide 500 may also include one or more motors 510 operably connected to one or more of the guide vanes 506 to selectively rotate the guide vanes 506.
The housing portion 502 includes an annular wall 512 having a first inner surface 514 and a first outer surface 516. The interior wall 422 has a second inner surface 424 and a second outer surface 426. The first inner surface 514 and the second inner surface 424 define the boundary of the passage P extending through the vane housing assembly. The housing portion 502 defines an exit or outlet 518 of the inlet guide 500. Refrigerant being channeled through the passage P enters the vane housing assembly of the inlet guide 500, contacts the guide vanes 506, exits the vane housing assembly via the outlet 518, and is channeled towards the first impeller 324 (shown in
The vane housing assembly of the inlet guide 500 includes an exterior area 520 surrounding the first outer surface 516 and the second outer surface 426 and located radially outward from the vane housing assembly. At least a portion of each of the guide vanes 506 is positioned between the housing portion 502 and the interior wall 422, and at least a portion of the guide vanes 506 and the ring gear 504 are arranged in the exterior area 520. Accordingly, the ring gear 504 and at least a portion of the guide vanes 506 are accessible (e.g., to an operator or technician) for inspection and/or repairs without requiring inlet guide 500 to be disassembled. By way of example, an operator or technician may access the ring gear 504 and a portion of the guide vanes 506 without first disconnecting the housing portion 502 from the end cap 402. The annular sidewall 408 may include a cut out 432 formed in the sidewall 408. The cut out 432 renders the sidewall 408 discontinuous along a circumferential extent and provides clearance to enable access to the ring gear 504 and a portion of the guide vanes 506 without disassembling the vane housing assembly. The cut out 432 may additionally, and/or alternatively, provide clearance for connecting the one or more motors 510 to one or more of the guide vanes 506.
The interior wall 422 includes a downstream surface 428 that is generally annular in shape. The interior wall 422 may have a width extending between the second outer surface 426 and the second inner surface 424 that is similar to a width of the annular wall 512 of the housing portion 502 extending between the first inner surface 514 and the first outer surface 516. An axial length of a portion of the passage P extending through the vane housing assembly is defined by an axial length of the interior wall 422 and the annular wall 512. A diameter of the passage P extending through the vane housing assembly is defined by a diameter of the second inner surface 424 and the first inner surface 514. The dimensions of the vane housing assembly, e.g., diameter and length, may be scaled to the size of the compressor 400 and the aerodynamic needs of the compressor 400 to define suitable dimensions of the passage P extending through the vane housing assembly.
The downstream surface 428 of the interior wall 422 includes second channels 434 arranged in a radially symmetric pattern about the downstream surface 428. An upstream surface 522 of the housing portion 502 includes first channels 524 arranged in a radially symmetric pattern about the upstream surface 522. The upstream surface 522 includes the same number of the first channels 524 as the number of second channels 434 included in the downstream surface 428. Each of the first and second channels 524, 434 may be identical, having the same size and shape. In the example inlet guide 500, the first and second channels 524, 434 are in the shape of a segment of a cylinder. When the inlet guide 500 is assembled, each of the first channels 524 aligns with one of the second channels 434 to cooperatively form guide vane channels extending radially through the vane housing assembly. The guide vane channels so formed are sized and shaped to receive at least a portion of the guide vanes 506 therein.
The guide vanes 506 are received by the guide vane channels formed by aligning first and second channels 524, 434 and are arranged in a radially symmetric pattern mirroring the radially symmetric pattern of the first and second channels 524, 434. The number of guide vanes 506 corresponds to the number of the first and second channels 524, 434. In the example inlet guide 500, there are ten guide vanes 506 corresponding to ten first channels 524 and ten second channels 434. The inlet guide 500 may include any suitable number of guide vanes 506 that enables the inlet guide 500 to function as described herein. For example, the inlet guide 500 may include six guide vanes 506, seven guide vanes 506, eight guide vanes 506, nine guide vanes 506, or more than ten guide vanes 506.
Each of the guide vanes 506 received by one of the guide vane channels are at least partially positioned in the portion of the passage P that extends through the vane housing assembly. The guide vanes 506 have any shape or size enabling the inlet guide 500 to function as describe herein. Additionally, the shape and size of the guide vanes 506 may be selected based upon the intended application of the inlet guide 500. For example, the size, shape, and angle of the guide vanes 506 may be selected based on the type and configuration of the compressor 400, the operating conditions, and/or the fluid type used with the compressor 400. Each of the guide vanes 506 is rotatable relative to the vane housing assembly of the inlet guide 500 such that the orientation of the each of the guide vanes 506 within the passage P is selectively adjustable.
The ring gear 504 is rotatably connected to the housing portion 502 and/or the interior wall 422 and rotatable about a central axis A defined by the inlet guide 500. The ring gear 504 includes gear teeth 526 that are sized and shaped to mate with vane gear teeth 528 of each of the guide vanes 506. Rotation of the ring gear 504 is transmitted to the vane gear teeth 528, causing rotation of the guide vanes 506 within the guide vane channels of the inlet guide 500.
The ring gear 504 further includes a feature 530 on a surface opposite the gear teeth 526. The feature 530 engages with the bearing 508, preventing the bearing 508 from translating axially relative to the ring gear 504.
The ring gear 504, and the vane gear teeth 528, are arranged in the exterior area 520 of the inlet guide 500, enabling an operator to inspect and/or repair the ring gear 504 without disconnecting the housing portion 502 and the interior wall 422. At least one of the guide vanes 506 may be a drive guide vane 532 that is operably connected to motor 510 that drives rotation of the drive guide vane 532. Rotation of the drive guide vane 532 causes rotation of the ring gear 504, which transmits rotation to the rest of the guide vanes 506, also referred to as follower guide vanes. Accordingly, all the guide vanes 506 rotate in unison. The motor 510 may be a stepper motor. The motor may communicatively be connected to a controller (e.g., the controller 260) and the controller transmits one or more instructions to the motor causing the motor to rotate the drive guide vane 532 in order to arrange the guide vanes 506 in a suitable orientation within the passage P. Simultaneous rotation of the guide vanes 506 changes the orientations of the guide vanes 506 relative to refrigerant flow through the vane housing assembly. The guide vanes 506 may be rotated, in unison, to arrange the inlet guide 500 to any suitable position, for example, to a fully open or neutral position, relative to the refrigerant flow, based on the operational needs of the compressor 400. For example, the position of the guide vanes 506 may be selected to increase the operating range of the compressor 400, including both surge and choke.
The inlet guide 500 may include the bearing 508 arranged between the housing portion 502 and the ring gear 504. The bearing 508 facilitates rotation of the ring gear 504 relative to the housing portion 502. The bearing 508 may be connected to the ring gear 504, e.g., the bearing 508 is press fit into frictional engagement with the feature 530. Accordingly, the ring gear 504 and the bearing 508 rotate relative to the housing portion 502. Alternatively, the bearing 508 may be press fit onto housing portion 502 such that the bearing 508 and the housing portion 502 are frictionally engaged and the ring gear 504 rotates relative to the bearing 508 and the housing portion 502. The bearing 508 may be a non-lubricating bearing or a self-lubricating bearing, and the bearing 508 may include any suitable type of bearing 508 that enables the inlet guide 500 to function as described herein. The bearing 508 may also be omitted and the ring gear 504 may rotate relative to the housing portion 502, without the use of a bearing. For example, the housing portion 502 and/or the interior wall 422 may be made from a self-lubricating material (e.g., graphite) that may negate the need for a bearing.
Referring again to
The damping chamber 404 also includes damping chamber outlets 438 connected to the passage P. The coolant within the damping chamber volume V exits the damping chamber 404 and enters the passage P of the compressor 400 via the damping chamber outlets 438. The damper chamber outlets 438 are formed in the interior wall 422 axially upstream from the second channels 434 formed in the downstream surface 428. Thus, the damping chamber outlets 438 are connected with the passage P upstream from the guide vanes 506 such that coolant exiting the damping chamber 404 via the outlets 438 enters the passage P and mixes with the low pressure refrigerant vapor upstream from the guide vanes 506.
The damping chamber outlets 438 are located at discrete angular positions spaced in a circumferential-direction along the interior wall 422. The damping chamber outlets 438 facilitate distributing flow of the coolant entering the passage P such that the coolant intersects the low pressure refrigerant in the passage P at multiple (i.e., two or more) angular flow directions. The damping chamber outlets 438 may include two or more outlets 438, such as three, four, five, six, or greater than six outlets 438. For example, the damping chamber outlets 438 may be formed in the interior wall 422 as an annular or semi-annular array of through-holes that extends circumferentially along the interior wall 422. In some examples, the damping chamber outlets 438 may be formed in a staggered circumferential arrangement along the interior wall 422. In other examples, the damping chamber outlets 438 may be aligned in a substantially circular circumferential arrangement along the interior wall 422. The damping chamber outlets 438 may be formed in any suitable formation to enable the damping chamber 404 to function as described herein.
The damping chamber outlets 438 may each have the same shape and/or size, or a shape and/or size of the damping chamber outlets 438 may vary. For example, the damping chamber outlets 438 may have the same cross-sectional size and/or shape, or the damping chamber outlets 438 may have different cross-sectional sizes and/or shapes. Additionally and/or alternatively, the damping chamber outlets 438 may have the same or different geometrical shape. The damping chamber outlets 438 may have any suitable geometric shape, such as, for example, prismatic (e.g., cylindrical), bell-shaped, conical, parabolic, and other shapes. Additionally and/or alternatively, the damping chamber outlets 438 may have the same orientation and/or a different orientation relative to a central axis of the passage P (and/or relative to a flow direction of the low pressure refrigerant in the passage P). In some examples, as shown in
Suitably, the damping chamber outlets 438 together define a cross-sectional area through which the coolant enters the passage P that is greater than or equal to a cross-sectional area defined by the damping chamber inlet 436 through which the coolant enters the damping chamber volume V. Thereby, back pressure to the coolant accumulating within the damping chamber volume V may be reduced or eliminated to enable the coolant to be driven into the passage P as described herein.
The coolant enters the volume V of the damping chamber 404 via the damping chamber inlet 436 and accumulates within the damping chamber volume V. The coolant within the damping chamber volume V is driven through the damping chamber outlets 438 and into the passage P by a pressure differential between the coolant and the low pressure refrigerant flowing through the passage P and/or by a suction at the damping chamber outlets 438 from the low pressure refrigerant flowing through the passage P. The damping chamber inlet 436 and the damping chamber outlets 438 are suitably sized to reduce or eliminate back pressure to the coolant accumulating in the damping chamber V such that the coolant is enabled to be driven into the passage P by the pressure differential and/or the suction. The coolant entering the passage P is distributed by the damping chamber outlets 438 to intersect the low pressure refrigerant flowing through the passage P at multiple discrete angular flow directions. Thereby, disturbances to the refrigerant flow through the passage P caused by the intersecting coolant are reduced or eliminated, which facilitates improving the performance, efficiency, and longevity of the compressor 400.
Example embodiments of compressor systems and methods, such as refrigerant compressors, are described above in detail. The systems and methods are not limited to the specific embodiments described herein, but rather, components of the system and methods may be used independently and separately from other components described herein. For example, the cooling circuits described herein may be used in compressors other than centrifugal compressors, including, for example and without limitation, scroll compressors, rotary compressors, and reciprocating compressors.
As used herein, the terms “about,” “substantially,” “essentially” and “approximately” when used in conjunction with ranges of dimensions, concentrations, temperatures or other physical or chemical properties or characteristics is meant to cover variations that may exist in the upper and/or lower limits of the ranges of the properties or characteristics, including, for example, variations resulting from rounding, measurement methodology or other statistical variation.
When introducing elements of the present disclosure or the embodiment(s) thereof, the articles “a,” “an,” “the,” and “said” are intended to mean that there are one or more of the elements. The terms “comprising,” “including,” “containing,” and “having” are intended to be inclusive and mean that there may be additional elements other than the listed elements. The use of terms indicating a particular orientation (e.g., “top,” “bottom,” “side,” etc.) is for convenience of description and does not require any particular orientation of the item described.
As various changes could be made in the above constructions and methods without departing from the scope of the disclosure, it is intended that all matter contained in the above description and shown in the accompanying drawing[s] shall be interpreted as illustrative and not in a limiting sense.
